U.S. patent number 3,652,187 [Application Number 05/085,077] was granted by the patent office on 1972-03-28 for pump.
This patent grant is currently assigned to Amicon Corporation. Invention is credited to Sebastian B. Di Mauro, Herbert H. Loeffler.
United States Patent |
3,652,187 |
Loeffler , et al. |
March 28, 1972 |
**Please see images for:
( Certificate of Correction ) ** |
PUMP
Abstract
A reciprocating fluid operated diaphragm-type pump has a control
valve automatically movable at each end of the reciprocating stroke
of the pump between two alternate positions to reverse fluid flow
to the pump, and thereby cause the pump to reciprocate. A
connecting member between the diaphragms of the pump passes through
a passage in the control valve and has sealing members located to
alternately seal and exhaust the opposite ends of the control valve
to pressurized fluid flowing out of the valve passage to the ends
of the valve, so that control valve movement at the ends of the
pump stroke is positive and rapid.
Inventors: |
Loeffler; Herbert H.
(Arlington, MA), Di Mauro; Sebastian B. (Malden, MA) |
Assignee: |
Amicon Corporation (Lexington,
MA)
|
Family
ID: |
22189309 |
Appl.
No.: |
05/085,077 |
Filed: |
October 29, 1970 |
Current U.S.
Class: |
417/393 |
Current CPC
Class: |
F04B
43/0736 (20130101) |
Current International
Class: |
F04B
43/06 (20060101); F04B 43/073 (20060101); F04b
017/00 (); F04b 035/00 () |
Field of
Search: |
;417/393,395 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Walker; Robert M.
Claims
What is claimed is:
1. A pump comprising
a housing having two separate compartments,
a pumping member spanning and dividing each of said compartments
into inner and outer chambers,
material inlet means and outlet means for each said outer
chamber,
a valve assembly for controlling movement of said pumping members,
said valve assembly being located between said compartments and
comprising
a valve chamber including a port in communication with each said
inner chamber, a fluid inlet port for a motive fluid supply, at
least one exhaust port, and a pair of spaced apart valve seats,
and
a control valve in said valve chamber having opposed actuating
ends, an internal passage between said ends, and a motive fluid
inlet to said internal passage, said valve being movable in said
valve chamber between two positions in which either one or the
other of said actuating ends rests on the respective one or the
other of said valve seats, said control valve being constructed to
connect one of said inner compartments to said fluid inlet port and
the other of said inner compartments to said exhaust port through
said valve chamber in accordance with its position,
a connecting member between said pumping members, joining said
pumping members together for simultaneous movement in said
compartments in like directions in a reciprocating stroke, said
connecting member extending through said internal valve
passage,
at least two spaced apart sealing members, responsive to movement
of said connecting member, sized to form sliding seals in said
internal valve passage, one of said members being disposed on each
side of the said motive fluid inlet to said internal valve passage,
and so located that alternate ones of said sealing members are
carried out of said internal valve passage when said connecting
member reaches the alternate extremes of its said stroke so as to
admit motive fluid out of said internal valve passage, past the
respective end of said open valve, between that end and its seat,
and
sealing means responsive to movement of said connecting member to
alternate extremes of its stroke to seal that end of said control
valve from exhaust while opening the opposite end of said control
valve to exhaust, to allow movement of said control valve between
its positions in response to said admitted motive fluid.
2. The pump of claim 1 wherein said sealing members and said
sealing means are secured to said connecting member for movement
therewith.
3. The pump of claim 2 wherein said internal valve passage is of
cylindrical shape, said connecting member has a portion between
said sealing members of smaller cross-sectional area than the
cross-sectional area of said internal valve passage, defining with
said valve passage an annular region continually under fluid
pressure from said motive fluid inlet, and said sealing members are
located to expose the ends of said control valve to said pressure
region.
4. The pump of claim 1 including a partition between each said
compartment and said valve assembly, each said partition
including
an exhaust passage having an exhaust port, each said exhaust
passage being arranged concentric with said internal valve passage,
with said connecting member extending through said exhaust passage,
and
a surface at the interior end of each said passage defining one of
said valve seats,
said connecting member and said exhaust passages being sized to
allow fluid flow between the said actuating ends of the valve and
the respective passage, and said sealing means arranged to prevent
said fluid flow.
5. The pump of claim 4 wherein said sealing means comprises two
additional spaced apart sealing members, secured to said connecting
member for movement therewith, sized to form sliding seal in said
exhaust passages, and so located that one of said sealing members
is disposed in the respective one of said exhaust passages between
said exhaust port and the said actuating end of said valve at each
extreme of the said stroke of said connecting member.
6. The pump of claim 1 wherein said control valve chamber has two
exhaust ports for said inner chambers, and valve has an outer
surface comprising axially spaced peripheral seals defining
therebetween three axially spaced annular fluid flow spaces, the
opposite end spaces are in communication with said exhaust ports,
the intermediate space is in communication with the fluid inlet
port from said motive fluid supply, and said spaces are mutually
arranged with the valve chamber ports to said inner chambers so
that, at each alternate position of said control valve, one of said
end spaces is closed to one said inner chamber, the intermediate
space is open to that said inner chamber to admit motive fluid to
said chamber, and the other of said end spaces is open to the other
said inner chamber to exhaust motive fluid from that chamber.
7. The pump of claim 1 including baffle means between said exhaust
port and atmosphere.
8. The pump of claim 1 wherein each said pumping member comprises a
flexible diaphragm spanning its respective said compartment, and
centrally secured to said connecting member.
9. The pump of claim 8 including rigid reinforcing plates secured
to each side of said diaphragm, and wherein said connecting member
comprises a rigid rod extending through said plates.
10. The pump of claim 9 wherein each said compartment is
constructed in the form of opposed outer and inner frustro-conical
shapes joined at a common base.
11. The pump of claim 10 wherein said material inlet means
comprises an inlet conduit radially into the outer frustro-conical
shape along its truncated apical end wall, and said material outlet
means comprises an outlet conduit radially out of said outer
frustro-conical shape along its truncated apical end wall.
12. The pump of claim 11 wherein said material inlet means includes
a single tubular material inlet passage having an inlet opening
intermediate of its ends, and with each end arranged to
communicate, past a one-way valve means, with one of said inlet
conduits, and a single tubular material outlet passage, having an
outlet opening intermediate of its ends, and with each end arranged
in communication, past a one-way valve means, with one of said
outlet conduits.
Description
This invention relates to pumps.
Conventional fluid operated reciprocating pumps usually contain
self-acting control valves, which are actuated by the moving
pumping means (e.g., a piston or a diaphragm) of the pump, or some
structure responsive to movement of the pumping means, at each end
of the pump stroke, to reverse the flow of motive fluid (as air or
hydraulic fluid) to the pumping means. The movement of the pumping
means to one end of its stroke, e.g., causes some fluid passage in
communication with the control valve to be opened or closed so as
to direct or exhaust fluid through a part of the control valve, and
thus causes the control valve to shift positions so as thereby to
change the direction of fluid flow to the pumping means. However,
once this valve is moved sufficiently to reverse the flow of fluid,
it often happens that this reversal causes the fluid passage to be
again closed or opened before the control valve has gone entirely
to its opposite position. Thus, part of the movement of the control
valve is due to the momentum of its initial movement. If the pump
malfunctions, or if it is simply shut off during the period of time
when the control valve is moving under momentum, it is possible
that the control valve can stop intermediate of its two positions.
Thus, when the pump is to be started again, it will be necessary to
somehow gain access to the control valve or to employ some
auxiliary start-up means so as to move the control valve to one of
its two positions so that the self-acting pumping may occur and
reciprocation can be initiated.
It is an object of this invention to provide a pump in which the
control valve is positively impelled between its two reciprocating
positions, so that the pump cannot stall.
Another object is to provide an improved reciprocating diaphragm
type pump which is compact, light-weight non corrodible, easy to
assemble and maintain, and of simple, reliable construction.
The invention features a pump comprising an inlet for a motive
fluid supply, such as a source of compressed air, a housing divided
into two separate compartments, and a pumping member such as a
flexible diaphragm spanning and dividing each of these compartments
into inner and outer chambers. The material to be pumped enters and
exits the outer chambers through appropriate material inlet means
and outlet means. A connecting member secures the two pumping
members together for simultaneous movement in like direction, each
pumping member being so located in its compartment that it
alternately increases and decreases the size of the outer chamber
in relation to the inner chamber, by virtue of the introduction of
motive fluid to the inner chambers, expelling fluid from the outer
chambers while decreasing the size of that chamber, and taking
fluid into the outer chamber when travelling in the opposite
direction so as to increase the size of the outer chamber. A valve
assembly is located between the two compartments and comprises a
valve chamber which has a port in communication with each of the
inner chambers, a motive fluid inlet port in communication with the
motive fluid supply, at least one exhaust port, a control valve,
and a pair of spaced apart valve seats. The control valve has
opposed actuating ends located opposite the respective valve seats,
an internal fluid passage between its ends, and a motive fluid
inlet to this internal fluid passage. The valve is disposed to be
movable in the valve chamber between two positions, in which one or
the other of the actuating ends rests on the respective one or the
other of the valve seats, the valve being constructed to connect
one of the inner compartments to the fluid inlet port of the valve
chamber and the other of the inner compartments to an exhaust in
accordance with its position.
To produce automatic movement of the control valve between its
positions at each extreme of the reciprocating stroke of the
connecting member and its associated pumping members, the
connecting member is arranged to extend through the aforesaid
internal valve passage between the actuating ends of the valve. Two
spaced apart sealing members, mounted for movement with the
connecting member, are sized to form sliding seals in the internal
valve passage, one member being disposed on each side of the motive
fluid inlet to the valve passage to prevent motive fluid from
passing out of the valve passage to the respective end of the
valve. However, when the connecting member reaches the alternate
extreme of its stroke, alternate ones of sealing members are
carried out of the internal valve passage, to admit motive fluid
out of the internal valve passage past one or the other of the
actuating ends of the valve, between that end and its seat.
Additional sealing means, also moving with the connecting member,
seal that end from exhaust while opening the opposite end to
exhaust. The valve thus is moved to its other position. Positive,
as well as rapid movement of the control valve between these two
positions is assured because as soon as the sealing member moves
out of the valve passage to admit fluid, the valve immediately
moves in the opposite direction, thus increasing the available area
for further motive fluid flow from the valve passage to the
actuating end. Since there is increasingly more room for motive
fluid to be admitted, the valve movement is continuously
accelerated. Moreover, this rapid movement means that the fluid
flow area will remain open to the motive fluid from the internal
valve passage until the valve has reached its other position, since
the sealing member, the movement of which has also been reversed,
will be unable to catch up to the valve. Thus, the valve cannot
stop between the opposite ends of its cycle, and the pump will be
always ready for immediate start-up.
In a preferred valve construction, the internal valve passage of
the valve is of cylindrical shape, the sealing members are secured
to the connecting member, and the connecting member has a portion
between the sealing members of smaller cross-sectional area than
that of the internal valve passage so as to provide an annular
pressure region therebetween, to which the ends of the valve are
alternately exposed.
To provide exhaust from the two actuating ends of the valve, a
preferred pump includes a partition between each compartment and
the valve assembly, an exhaust passage in each partition,
concentric with the internal valve passage so as to allow the
connecting member to extend through the partitions, and an exhaust
port in each passage. The surface at the interior end of each
passage defines one of the valve seats. The connecting member is
sized to allow fluid flow between the actuating ends of the valve
and the respective exhaust passage, and the aforesaid sealing means
are located to prevent such flow. Preferred sealing means comprise
two additional spaced apart sealing members secured to the
connecting member for movement with it, and sized to form sliding
seals in the exhaust passages. The sealing members are so located
that one of them is disposed in the respective one of the exhaust
passages, sealing the actuating end of the valve from the exhaust
port at certain intervals during the stroke at the connecting
member, such as when the member is at the extremes of its stroke so
that motive fluid is being introduced into the opposite actuating
end. The operation of this embodiment is further facilitated by
locating these exhaust sealing members in such a manner that even
before motive fluid is admitted from the internal valve passage to
one end of the valve, the opposite end of the valve is already
opened to exhaust and thus, in a sense, the valve is primed for
movement between its positions. In addition, the preferred pump
construction has baffle means, constructed, e.g., of a synthetic
cellular or foam material, located between the exhaust outlet and
atmosphere to reduce noise caused by the very rapid reciprocation
of the control valve.
In a preferred valve assembly, the valve chamber has two exhaust
ports, one for each of the inner chambers. The control valve has an
outer surface comprising axially spaced peripheral seals which
define therebetween three axially spaced annular fluid flow spaces.
The two opposite end spaces are continually in communication with
the exhaust ports whereas the intermediate space is continually in
communication with the motive fluid inlet port. Then, at each
alternate position of the control valve, one of its end spaces is
closed to one of the inner chambers, the intermediate space is open
to that inner chamber to admit motive fluid to it, and the other
end space is open to the other inner chamber so as to exhaust
it.
A preferred pumping member is a flexible diaphragm, which spans its
compartment, and which may be reinforced by rigid plates located on
each side of the diaphragm and connected to each end by a rigid
connecting rod. The diaphragm compartments are preferably in the
form of opposed outer and inner frustro-conical shapes joined at a
common base. The material inlet means to such a compartment is
preferably through an inlet conduit disposed radially into the
outer frustro-conical shape along its truncated apical end wall and
the material outlet means from said compartment is of similar
construction. The material inlet means (or outlet means) also
includes a single tubular material passage which has an inlet (or
outlet) intermediate of its ends, and each of its ends arranged to
communicate, past a one-way valve means, with one of the inlet (or
outlet) conduits to the diaphragm compartments, so that a single
inlet simultaneously feeds fluid under a unitary pressure to both
compartments.
Other objects, features, and advantages will be apparent to one
skilled in the art from the following description of a preferred
embodiment of this invention, taken together with the attached
drawings thereof, in which:
FIG. 1 is a sectional view of a preferred embodiment of a diaphragm
pump taken along the line 1--1 of FIG. 2;
FIG. 2 is another sectional view of this pump, substantially
perpendicular to that of FIG. 1 and along the line 2--2 of FIG.
1;
FIG. 3 is another sectional view of this pump, along the line 3--3
of FIG. 1, showing in particular the interior construction of a
diaphragm compartment; and,
FIGS. 4 and 5 are enlarged views of the valve assembly of FIG. 1,
with the control valve and connecting rod shown in different
positions from that of FIG. 1.
The figures show a diaphragm pump 10 including a pump housing 12
substantially enclosing a first diaphragm compartment 18, a second
diaphragm compartment 20, and a valve compartment 22. Pump housing
12 comprises a pair of spaced apart identical cylindrical end
plates 24, 26, a pair of identical opposed inner plates 32, 34, and
an annular spacing ring 35. All of the plates and rings are secured
together by six spaced studs 37, extending through appropriate
aligned openings in the plates 24, 32, 34, 26 and in spacing ring
35, and held at one end by nuts 40 and washers 41, and at the other
end by acorn nuts 44 and retainers 45.
Referring to FIGS. 1 and 3, the first diaphragm compartment 18 is
formed between a first frustro-conical shape 48 formed in
cylindrical plate 24, joined at a common base to an opposed
frustro-conical shape 50, formed in inner plate 32. Two tubular
counterbores 52 extend radially into the truncated apical end wall
of shape 48, are sealed at their two ends by appropriate plugs 54,
and define, with perpendicularly disposed passages 57, 58, a
material inlet conduit 59 to diaphragm compartment 18 and a
material outlet conduit 60 from that compartment. A cylindrical
counterbore 62, centrally located in the shape 48 of inner plate
24, is sized to receive a nut 64 and the protruding threaded end 65
of connecting rod 67.
A flexible diaphragm 68 is secured between the opposed faces of
plates 24 and 32 around its entire periphery, to divide the
compartment 18 into an outer or pumping chamber 70 in communication
with inlet conduit 59 and outlet conduit 60, and an inner or motive
chamber 72, sealed from those passages by the diaphragm 68, and in
communication, through a tubular inlet 74 formed in plate 32, with
the valve compartment 22. Diaphragm 68 may be formed of, e.g.,
various reinforced elastomers such as nylon-inserted Buna N,
silicon rubber, or fluorocarbons such as those sold under the trade
names "VITON," "Kel-F" and the like, or other flexible materials
such as thin, convoluted stainless steel sheet. Diaphragm 68 has a
central aperture, through which extends one end of connecting rod
67, and disc-shaped diaphragm reinforcing plates 75 are secured on
each side of diaphragm 68 between the shoulder 76 of rod 67 and the
nut 64, with a gasket 78 arranged to provide a fluid-tight seal
between the pumping chamber 70 and the motive chamber 72.
A material inlet 80 communicates with the opening 81 into the
tubular passage 82. A spring-biased ball valve 84 is arranged in
the ball valve chamber 83 with the shoulder 85 provided at the end
of passage 82 forming a valve seat for ball valve 84. This ball
valve is arranged to pass material from inlet 80 and passage 82 to
diaphragm pumping chamber 70. A gasket 88 seals the interface of
inner plate 32 and spacing ring 35 at valve chamber 83. A material
outlet 90 communicates with the tubular passage 92. A spring biased
ball valve 94 is arranged in the ball valve chamber 93, with the
shoulder 95 provided at the end of tubular passage 58 forming a
valve seat for ball valve 94. This ball valve 94 is arranged to
pass material from diaphragm pumping chamber 70 to outlet 90. A
gasket 98 seals the interface of inner plate 32 and spacing ring 35
at valve chamber 93. The diaphragm 68 has an opening adjacent and
concentric with each valve chamber 83, 93.
The second diaphragm compartment 20 is formed of frustro-conical
shapes 148 and 150, identical to the shapes 48, 50 of first
diaphragm compartment 18, and includes two tubular counterbores 152
extending radially into shape 148, sealed at their two ends by
plugs 154, and defining, with perpendicularly disposed passages
157, 158, a material inlet conduit 159 to compartment 20, and a
material outlet conduit 160 from the compartment 20. Cylindrical
counterbore 162, identical to counterbore 62, is for receiving a
nut 164 and opposite threaded end 165 of connecting rod 67. A
flexible diaphragm 168 (formed of materials such as previously
described for diaphragm 68) is secured between the opposed faces of
plates 26 and 34, around its entire periphery, to divide the
compartment 20 into an outer or pumping chamber 170 in
communication with inlet conduit 159 and outlet conduit 160, and an
inner or motive chamber 172, sealed from those passages by
diaphragm 168, and in communication, through tubular inlet 174,
with the valve compartment 22. Disc-shaped diaphragm reinforcing
plates 175, which are secured between rod shoulder 176 and nut 164,
and gaskets 178 are arranged as previously described for plates 75
and O-rings 78. A cylindrical ball valve chamber 183 is formed in
inner plate 34 adjacent the tubular passage 82. A spring-biased
ball valve 184 is arranged in chamber 183, with the shoulder 185
provided at the end of passage 82 forming a valve seat for ball
valve 184. Ball valve 184, like valve 84, passes material from
inlet 80 to diaphragm pumping chamber 170. A gasket 188 seals the
interface of inner plate 34 with spacing ring 35 at valve chamber
183. A spring-biased ball valve 194 is arranged in the ball valve
chamber 193, with the shoulder 195 provided at the inner end of
tubular passage 158, forming a valve seat for ball valve 194. This
ball valve 194 passes material from diaphragm pumping chamber 170
to outlet 90. A gasket 198 seals the interface of inner plate 34
with spacing ring 35 at valve chamber 193. The diaphragm 168 has an
opening adjacent and concentric with each valve chamber 183,
193.
Referring now to FIGS. 1 and 4, valve assembly 200 includes a
stationary annular valve housing 202, secured by fasteners 203
between opposed shallow cylindrical detents 205, 206, formed in the
opposing surfaces of inner plates 32, 34. Spool valve 208 has four
annular lands 209 each having an annular rubbery O-ring seal 210 at
its outer surface, slidingly engaging the inner cylindrical valve
chamber 211 of housing 202, the seals 210 being located so as to
maintain, by friction with chamber 211, the spool valve 208 in
position, in the absence of other forces acting on the spool valve.
The seals 210 are fluid-tight and define therebetween three annular
fluid flow spaces 212, 213, 214 with chamber 211. The entire spool
valve, exclusive of seals 210 may be formed of a rigid plastic,
such as acetal. Spool valve 208 also has opposed actuating faces
216, 217 at its opposite ends, disposed opposite the valve seats
218, 219 formed in inner plates 32, 34, respectively. Spool valve
208 has a central bore defining an internal valve passage 220
within which is slidingly received the rubbery O-ring sealing
members 222, 223, 224, 225 located on connecting rod 67. These
sealing members provide fluid-tight sliding seals around the
connecting rod 67, which has, disposed within the valve passage
220, upper and lower portions 228, 230 and a reduced diameter
central portion 232. The connecting rod 67 also extends slidingly
through exhaust passages 233, 234 in inner plates 32, 34,
respectively, and is sealed from the diaphragm compartments 18, 20,
by gaskets 236, 237, respectively.
Referring also to FIG. 2, valve housing 202 has an inlet passage
240 in communication with valve space 213 and also with a
compressed air line 242, providing a motive fluid supply to operate
the pump, and which in turn extends through an opening 244 in
spacing ring 35. An annular exhaust port 246 is located between the
opening 244 and air line 242, and in communication with the exhaust
space 247 in valve compartment 22. An annular air-permeable foam
packing ring 248 is arranged as a baffle interior of and adjacent
opening 244, to reduce any noise caused by operation of the spool
valve 208.
Two outer exhaust passages 250, 251 extend between valve chamber
211 and exhaust space 247, are in communication with valve spaces
212, 214, respectively, and also communicate with valve exhaust
passages 252, 253, respectively, which in turn communicate, through
diagonal passages 254, 255, respectively, formed in inner plates
32, 34, respectively, with exhaust passages 233, 234, respectively.
The diagonal passages 254, 255 are sealed from motive chambers 72,
172, respectively, by connecting rod portion 228 and gasket 236,
and connecting rod portion 230 and gasket 237, respectively. Inner
chamber fluid passages 258, 259, sealed to have a right-angle
configuration by sealing fasteners 260, 261, respectively,
communicate through passages 74, 174, respectively, with motive
fluid diaphragm chambers 72, 172, respectively.
Inlet 240 is also in communication, through the valve space 213,
with one of the inner chamber passages 258, 259, depending on the
position of the spool valve 208. The other inner chamber inlet
passage is in communication, through valve space 212 or 214, with
outer exhaust passage 250 or 251, respectively, Inlet 240 is also
in communication, through narrow radial inlet passages 272, 273
through spool valve 208, with the annular pressure region 274
between the central portion 232 of connecting rod 67 and the
internal valve passage 220 of spool valve 208.
In operation, a motive fluid, such as compressed air, is introduced
through inlet line 242 and passage 240 to valve space 213. In the
position of spool valve 218 shown in FIG. 1, this valve space is
open, through passages 259, 174 to second diaphragm inner chamber
172. Although both valve spaces 212, 214 are open to atmosphere
through passages 250, 251, respectively, only valve space 212 is
open to inner diaphragm chamber 72 through passages 258 and 74.
Valve space 214 is closed to inner chamber 172. In this spool valve
position, therefore, air under pressure is being introduced into
motive chamber 172 and air is being exhausted from chamber 72,
causing the diaphragms 68, 168 to travel, in unison by virtue of
connecting rod 67, in the downward direction in FIG. 1, tending to
decrease the size of the inner chamber 72 of the first diaphragm
compartment 18, and increase the size of the inner chamber 172 of
the second diaphragm compartment 20.
The material being pumped, in the meanwhile, is introduced, under
pressure, through inlet 80 into passage 82. So long as the fluid
pressure in expanding pumping chamber 70 of the first diaphragm
compartment 18 is insufficient, together with the biasing spring of
ball valve 84, to overcome the pressure of incoming material in
passage 82, ball valve 84 will be unseated, allowing material to
pass into pumping chamber 70. However, since pumping chamber 170 of
the second diaphragm compartment 20 is decreasing in size with the
movement of the diaphragms indicated in FIG. 1, the combined
pressure in chamber 170 and the force of the biasing spring of ball
valve 184, will be sufficient to retain ball valve 184 seated, and
hence no material will enter chamber 170. The increasing pressure
in contracting pumping chamber 170 will also unseat ball valve 194,
so that material may exit through passage 92 and outlet 90, whereas
the pressure in expanding pumping chamber 70 will be insufficient
to unseat ball valve 94. The one-way orientation of valve seats for
the ball valves 84, 184, 94 and 194 prevents backflow of material
through the pump.
In the position shown in FIG. 1, the diaphragms 68, 168 and
connecting rod 67 have nearly reached one extreme of the stroke,
with pumping chamber 70 almost filled and pumping chamber 170
almost emptied. The outer diaphragm pad 174 is close to the apical
wall of shape 148, and the nut 164 and rod end 165 have begun to
enter the counterbore 162. The motive fluid main flow around and
within flow spool valve 208 is as follows. Compressed air from
passage 240 is being led continuously through passages 272, 273 to
the pressure region 274, but sealing members 222, 223 are still
preventing air from passing to the actuating faces 216 or 217 of
valve 208. Diagonal passage 254 is open, however, through the
narrow annular space between the upper portion 228 of connecting
rod 67 and the exhaust passage 233, to the valve chamber space
adjacent actuating face 216, allowing air in that space to exhaust
through passages 254, 252 and 250. Diagonal passage 255, however,
is sealed from the valve chamber space adjacent actuating face 217
and hence from the valve spool itself by sealing member 224, which
is disposed within exhaust passage 234.
With slight further movement of the diaphragms and connecting rod
in the downward direction, the sealing member 224 will be moved all
the way out of internal valve passage 220, to open the valve
chamber adjacent valve actuating face 217 to compressed air from
pressure region 274. The valve chamber adjacent opposite actuating
face 216 being open to atmosphere, the sudden onrush of compressed
air adjacent valve face 217 will lift the spool valve 208 off valve
seat 219. As the spool valve 208 is lifted, the annular area for
air flow from space 274 between the valve 208 and the sealing
member 224 rapidly increases in size, accelerating spool valve
movement until the spool valve 208 has travelled to the opposite
end of the valve chamber 214, actuating face 216 resting on valve
seat 218, in the position shown in FIG. 4. The valve space 213 has
now been shifted so as to be between air inlet passage 240 and
diaphragm compartment passage 258 to direct compressed air to
motive chamber 72, whereas valve space 214 is located to exhaust
air from motive chamber 172 through passage 259, space 214, and
passage 251. Thus, the rod 67, and hence diaphragms 68, 168
connected thereto, will begin to move in the upward direction,
material being expelled from pumping chamber 70 past ball valve 94
and through outlet 90, and material being introduced into expanding
pumping chamber 170 through inlet 80, past ball valve 184. Long
before rod 67 moves sufficiently for sealing member 224 to reseal
pressure region 274 from the actuating face 217, the spool valve
208 has gone completely to the position shown in FIG. 4. Thus, the
entire spool valve movement is under the constant force of
compressed air from the source 242, causing a rapid and positive
movement of the valve, and making it impossible for the spool valve
to stop in any position intermediate of those shown in FIGS. 1 and
4. The pump is always, therefore, ready for use. Even when
compressed air is exhausted from below the valve face 217,
frictional forces between the sealing members and the wall of valve
chamber 211 maintain the valve on one or the other of its valve
seats.
As the connecting rod 67, with movement of the diaphragms under
compressed air, moves to the position shown in FIG. 5, first
sealing member 224 seals pressure region 274 from valve face 217.
Next sealing member 225 moves out of exhaust passage 234, opening
the valve chamber adjacent actuating face 217 to atmosphere through
passages 255, 253, and 251, as sealing member 222 moves into
exhaust passage 232, to close communication between the valve
chamber adjacent actuating face 216 and atmosphere through passages
254, 252 and 250. In this position, as shown in FIG. 5, both
actuating faces 216, 217 are closed to the compressed air in space
274, and face 217 is already exposed to atmosphere. Finally, as rod
67 is moved to and past essentially the reverse of the position of
FIG. 1, sealing member 223 will move out of internal valve space
220, exposing valve face 216 to compressed air from pressure region
274, rapidly returning the spool valve 208 to the FIG. 1 position,
to commence another stroke. With air now being introduced into
motive chamber 172 and exhausted from chamber 72, the diaphragms
68, 168 will travel back in the direction indicated in FIG. 1, and
material being expelled from pumping chamber 170 and filling
pumping chamber 70, the diaphragms 68, 168 and rod 67 will complete
the cycle back to the position shown in FIG. 1.
Substantially all parts of the pump may be formed of metal, such as
stainless steel, or of light-weight, noncorrodible rigid plastic
materials, such as acrylics and the like. The diaphragm pads 74,
174, and connecting rod 67, for greater rigidity, are preferably
formed of a metal such as stainless steel, which may be coated, if
desired, with a noncorrodible coating such as a thin fluorocarbon
film.
Other embodiments will occur to those skilled in the art and are
within the following claims.
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