Non-lubricated, air-actuated, pump-operating, shuttle valve arrangement, in a reciprocating pump

A pilot spool is interposed between the compressed air supply and the diaphragm pump-operating main spool, to insure that, at any one time, only one end of the bore in which the main spool reciprocates receives the compressed air. The pilot spool has an annular recess of a length which does not bridge across passageways which admit the air to the main spool, so alternatively, each passageway opens onto an end of the main spool bore. The reciprocating pump structure, that is, the double diaphragms, shaft, and clamp plates, cause the pilot spool to shift, to communicate one of the passageways, with each shift, with the air supply and the main spool bore. No lubrication is provided or needed, and the pilot spool insures that the main spool will not stall.

BACKGROUND OF THE INVENTION 
This invention pertains to reciprocating pumps, generally, such as 
compressed air-operated, double-diaphragm pumps, having a pump-operating, 
main spool valve or shuttle valve, and in particular to such a 
non-lubricated, air-actuated, pump-operating, shuttle valve arrangement, 
in a reciprocating pump. 
Compressed air-operated, diaphragm pumps are susceptible to stalling; 
stalling occurs when the pump-operating main spool or shuttle valve 
becomes halted at the midpoint of its reciprocating motion in its bore. In 
this circumstance, the pump is prevented from restarting without 
repositioning the stalled main spool or shuttle valve. This condition can 
occur when the compressed air source is interrupted with the pump running, 
or when there is a low air supply pressure. In prior art pump designs 
which incorporate shuttle valves or shafts which use O-rings in dynamic 
sealing conditions, the O-rings can become set, during periods of non-use, 
or the shaft can become frozen in position so as to become "stalled". 
Manufacturers of these prior art designs, even though they claim 
lubrication free configurations, must use oil or grease of some kind to 
lessen such stalling. Restarting of these designs, if possible, would 
require significantly higher than normal operating inlet air supply 
pressures. 
Prior art, air-operated, diaphragm pumps, typically, are unable to operate 
at low inlet air supply pressures, and they are known to be susceptible of 
unreliable operation at extremely low pump discharge flow rates. Too, the 
prior art, air-operated, diaphragm pumps have an inability to operate 
smoothly and reliably during constant, start-stop, duty cycles. 
Most current versions of air-operated, diaphragm pumps utilize a lubricated 
pilot spool or lubricated main shaft (which also serves to pilot the main 
spool or shuttle valve), which requires O-rings to seal in a dynamic 
condition. In order to qualify for non-stall operation, the O-rings need 
to be lubricated by oil mist or grease pack to be able to slide without 
binding at low air supply pressures. 
Polytetrafluorethylene-encapsulated O-rings were tried, to eliminate the 
need for lubrication in the aforesaid prior art pumps, but these were 
unsuccessful. 
At least one, current, "non-stall" air valve manufacturer, which claims its 
pilot spool with O-rings requires no outside lubrication, requires the use 
of an in-line lubricator on the air supply for other than intermittent 
operation. For continuous operation, light oil injection is recommended. 
One other, current, "non-stall" air valve manufacturer utilizes an 
unbalanced main spool, or shuttle valve, to allow a greater force to bias 
the main spool or shuttle valve in one direction to prevent centering 
thereof, and resultantly, stalling. This design comprises a grease pack to 
allow the sliding of close tolerance components to occur. 
Further, current versions of such air valves utilize two spring-loaded 
actuators (i.e., popper valves) to shift the main spool or shuttle valve. 
Even though these versions were lubrication free, they had a tendency to 
hang-up or fail to shift completely, on low air supply pressures, or on 
constant start-stop operation. Since the spring in a spring-loaded popper 
valve allows the valve to remain open only momentarily, a low inlet air 
pressure condition results in an insufficient volume of air to reach the 
main spool or shuttle valve. Further, in these low pressure applications, 
this incomplete main spool shift can result in "centering" or air valve 
"hang-up". This low inlet air pressure condition is aggravated by designed 
"controlled leakage" to exhaust which reduces further the volume of air 
which is available to cause main spool or shuttle valve shifting. The 
necessity to overcome the spring force to open a spring-loaded actuator is 
also disadvantageous in a low supply air pressure condition. 
Known, prior art embodiments of such air valves also have an inordinate 
number of discrete parts and components, and/or complicated arrangements 
and assemblies which make any routine maintenance and servicing very 
troublesome and expensive. 
SUMMARY OF THE INVENTION 
In view of the aforecited problems with prior art main spool or shuttle 
valve arrangements, it is an object of this invention to define an 
inventive embodiment of such an arrangement which obviates the prior art 
problems. 
Particularly, it is an object of this invention to set forth a 
non-lubricated, air-actuated, pump-operating, shuttle valve arrangement, 
in a reciprocating pump, comprising a pump housing having a first bore 
formed therein; a pump-operating shuttle valve slidably disposed in said 
bore; a source of energized air; a first passageway, formed in said 
housing, for conducting air from said source to one end of said bore; a 
second passageway, formed in said housing, for conducting air from said 
source to the opposite end of said bore; and reciprocating means, 
interposed between said source and said passageways, for preventing an 
operative stall of said shuttle valve due to a dead centering thereof, in 
said bore, substantially equidistant from said one and said opposite ends 
of said bore. 
Further objects of this invention, as well as the novel features thereof, 
will become apparent by reference to the following description, taken in 
conjunction with the accompanying figures.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
Referring now to the drawings in detail, and first to FIG. 1 thereof, it 
will be seen that a double-diaphragm, air-operated, reciprocating pump is 
depicted. The pump, per se, in its general operation, is not especially 
germane to the present invention and, in fact, is not significantly 
dissimilar from prior art pumps. U.S. Pat. Nos. 4,494,574, issued to 
Joseph C. Casilli, et al, on 22 Jan. 1985, for a Valve Arrangement for an 
Air-Operated Diaphragm Pump, and 4,555,222, issued on Nov. 26, 1985, for 
an Air-Operated Diaphragm Pump and a Valve Arrangement Therefor, to Joseph 
C. Casilli, clearly describe the operation of such double-diaphragm, 
air-operated pumps. Accordingly, it is deemed unnecessary to detail the 
general functioning of the FIG. 1 double-diaphragm pump, herein, as such 
is known to those of ordinary skill in the relevant art. In addition, the 
aforesaid U.S. Pat. Nos. 4,494,574 and 4,555,222 are hereby incorporated, 
by reference, for any perceived background information which my be 
necessary to an understanding of the double-diaphragm functioning of the 
instant pump. 
As shown in FIG. 1, there is an air distributor 1 and a main spool or 
shuttle valve 2, the latter being slidable in a main spool or shuttle 
valve bore 3 formed in the spool or shuttle valve-confining portion of the 
pump housing 4. A novel pilot spool 5, which is reciprocable in parallel 
with the main shaft 6 of the pump, serves an inventive performance of 
which more is detailed in the ensuing text. The main spool or shuttle 
valve 2 has piston rings 7 thereabout, the same being seen in FIG. 2. Air 
exhaust ports 8 are formed in the housing 4 and the compressed air supply 
9 is conducted to the pilot spool 5 for communication thereof to one or 
the other end of the bore 3. An air exhaust muffler 10 is in communication 
with the ports 8. The diaphragms 11 are disposed astride the housing 4, 
the latter having a pair of passageways 12 formed in the housing for 
distributing the compressed air supply 9. Inner clamps plates 13 of the 
pump diaphragms 11 impinge against opposite-ended, extended portions of 
the pilot spool 5 to cause the spool 5 to reciprocate in the pilot spool 
bore 14 as a consequence of the reciprocation of the main shaft 6 of the 
pump. The pilot spool 5 has sealing piston rings 15 set thereabout, and 
the extended portions 16 of the pilot spool 5 have seals 17 thereabout. 
Rings 15 and seals 17 cooperate with the spool 5 and the bore 14 to define 
variable volume chambers 18 and 19 at opposite ends of the bore 14. 
In an axial, cross-sectional view, FIG. 2 depicts the main spool or shuttle 
valve 2 in the bore 3 of the spool portion of the housing 4, and shows the 
sealing piston rings 7 disposed about each end of the main spool or 
shuttle valve 2. 
As is somewhat conventional, the main spool or shuttle valve 2 and the 
pilot spool 5 are used to direct the compressed air supply 9 to work the 
diaphragms 11 of the pump. The main spool or shuttle valve 2 directs the 
supply air 9, alternately, to each diaphragm 11, and then to the exhaust 
muffler 10. The pilot spool 5 is used to shift the main spool or shuttle 
valve 2. 
The pilot spool 5 operates by simultaneously opening and closing four 
distinct air passageways, namely: two exhaust passageways 8 and two main 
spool or shuttle valve passageways 12, to control the air flow to and from 
the main spool or shuttle valve 2 for the purpose of shifting it. The two 
passageways 12 connect the pilot spool 5 to each end of the main spool or 
shuttle valve 2. Two other passageways 8 connect the pilot spool to the 
exhaust. 
The travel of the pilot spool 5 can be broken down into three positions of 
operation: a.) pilot spool 5 centered; with the pump shaft 6 moving 
axially, an inner diaphragm clamp plate 13 impinges against one extended 
portion 16 of the pilot spool 5. With the pilot spool being moved to its 
center position, all supply air 9 to the main spool or shuttle valve 2 is 
shut off. This is so, as the annular recess 20, formed about the pilot 
spool 5 has a length which will not bridge across the spaced-apart 
passageways 12. As can be discerned in FIG. 1, either one of the 
passageways 12 can be in communication with the recess, or neither 
thereof. The latter circumstance obtains, with the pilot spool 5 centered 
in the bore 14. This positioning of the pilot spool 5 prevents pressured 
air 9 from being directed to both ends of the main spool or shuttle valve 
2 at the same time, a condition which would cause the pump to stall. 
A next condition of the pilot spool is b.) pilot spool off center to the 
left; with the pump shaft 6 and the inner diaphragm plate 13 continuing to 
move, the pilot spool 5 is moved off center. Simultaneously, only one end 
of the main spool or shuttle valve 2 is opened to the pressured air supply 
9, while the opposite end thereof is put in communication with the exhaust 
8, 10. The main spool or shuttle valve 2 shifts, causing a reversal of the 
travel of the pump shaft 6. 
There is another condition of the pilot spool 5, to wit: c.) pilot spool 
off center to the right; the pump shaft 6 continues its reversed travel 
until the other clamp plate 13 contacts the opposite, extended portion 16 
of the pilot spool 5, driving the pilot spool 5 past its center position 
and into its off center-right positioning. This now reverses the porting 
12 to the main spool or shuttle valve 2; the exhaust and supply pressure 
ends of the main spool or shuttle valve 2 are switched, in effect, causing 
the main spool or shuttle valve 2 to shift and cause a reverse travel of 
the pump shaft 6 and diaphragm clamp plates 13. 
The cycling is repeated, indefinitely, resulting in continuous pumping 
action by the double-diaphragm pump. 
Functioning of the pilot spool 5 is accomplished by isolating the four air 
passageways 8 and 12 from one another either through tight radial 
clearances between the pilot spool and the bore 14, or, as depicted, by 
utilizing piston rings 15 on the pilot spool 5 to seal to the pilot bore 
14. 
The invention offers a means for overcoming any requirement for lubrication 
in the pump; as disclosed herein, no O-rings requiring lubrication, in 
fact no lubrication of any kind is needed. The main spool or shuttle valve 
2 comprehends a non-metallic component; the same can be of plastic or 
other non-metal material. The main spool or shuttle valve 2 reciprocates 
in the bore 3, having equal, balanced areas at either ends thereof on 
which the supply air 9 acts. The main spool or shuttle valve 2 rides on 
two anti-friction piston rings 7 which provide lifetime, dry lubrication. 
Stall-free operation is accomplished by the pilot spool 5 which is actuated 
by the clamp plates 13, due to translation of the pump shaft 6, and the 
actuation supplies high pressure air to only one end of the main spool or 
shuttle valve 2; this, of course, causes the latter to shift in its bore 
3. Too, the actuation of the pilot spool 5 maintains high pressure air 9 
at one end of the bore 3 until the pump stroke is completed. Centering, or 
hang-up, of the main spool or shuttle valve 2 is prevented by maintaining 
high pressure air at one end of the bore 3 through the full pump stroke. 
This invention overcomes the shortcomings of the spring-loaded poppet 
design through elimination of the popper valve closing spring and the 
"controlled leakage" of this design. The typical, two spring-loaded popper 
valves and their seats are replaced by a single pilot spool 5. This pilot 
spool 5, when actuated, remains in an open position during the entire pump 
stroke, providing sufficient and continuous supply air 9 to guarantee a 
conplete shift of the main spool or shuttle valve 2. By eliminating the 
controlled leakage of the prior art designs, inlet air is not lost 
directly to exhaust 8 before it can reach and effect a complete shift of 
the main spool or shuttle valve 2. The latter, and the pilot spool 5 act 
as two distinct air switches which "toggle" between ends of their axial 
travels. 
While we have described our invention in connection with a specific 
embodiment thereof, it is to be clearly understood that this is done only 
by way of example, and not as a limitation to the scope of the invention, 
as set forth in the objects thereof, and in the appended claim.