US2532247A - Displacement pump - Google Patents

Description

Nov. 28, 1950 R. E. SYKES 5 32 47 DISPLACEMENT PUMP Filed Aug. 20, 1945 6 Sheets-Sheet? 6 I [OZ 65 I I Q46 I00 Nov. 28, 1950 R. E. SYKES 2,532,247

DISPLACEMENT PUMP Filed Aug. 20, 1945 Y 6 Sheets-Sheet s R; E. sYKss' DISPLACEMENT PUMP 6 Sheds-Sheet 4 Filed Aug. 20, 1945 Nov. 28, 1950 R. E. SYKES 2,532,247

DISPLACEMENT PUMP Filed Aug. ,20, 1945 e Sheets-Sheet 5 I87 IZZ ms I COMPRESSED AIR lNL-ET LIQUID 99 DISCHARGE AIR OUTLET Nov. 28, 1950 R. E. sYKEs DISPLACEMENT PUMP Filed Aug. 20, i945 6 shget sshegt' a Patented Nov. 28, 1950 UNITED STATES PATENT OFFICE DISPLACEMENT PUMP Robert E. Sykes, Sheboygan, Wis.

Application August 20, 1945, Serial No. 611,573

11 Claims.

The invention relates to fluid pressure operated pumps and the like and While not limited thereto it is especially applicable to liquid receiving and transmitting pumps operated by compressed gas acting directly upon the liquid, commonly known as displacement pumps.

Pumps of the aforementioned character have heretofore been provided with two displacement chambers, each having a suction and a discharge valve for the liquid and with a reversing valve for supplying pressure to each chamber and alternately exhausting the air therefrom, the

arrangement being such that while one chamber was under air pressure the air in the other chamber was exhausted to the atmosphere, or was returned to the suction side of the air supply. The pumps aforedescribed had the disadvantage that the discharge pressure of the fluid substance varied during the switching operation of the valve and they are therefore unsuited where a constant pressure of the discharge liquid is required.

The present invention has for one of its objects to provide a displacement pump in which the discharge pressure of the fluid substance is maintained substantially constant at all times.

Another object is to provide a displacement pump having a plurality of pump chambers whose operating cycles are so arranged that the discharge period of at least two chambers overlap in such a way as to assure a constant discharge stream of liquid substance.

Another object is to provide sequence control means for a multichamber displacement pump affording admission and discharge of the working fluid of the various chambers in regular sequence with overlapping of the discharge periods of consecutively discharging chambers.

Another object is to provide simple and efiicient timing means for timing the operating cycle of the pump.

Another object is to provide pneumatic timing means which are operated by the pressure fluid which also furnishes the energy for operating the pump chambers.

Another object is to provide a plurality of pumps which may be operated in parallel or in tandem and supplied with working fluid controlled by a single timing or sequence control mechanism.

Another object is to provide means affording a constant liquid discharge pressure for varying discharge rates.

Another object is to provide for adjustment of the discharge pressure of the pump.

Another object is to provide a portable displacement pump.

Another object is to provide a portable displacement pump which can readily be adjusted to operate from different sources of pressure fluid.

Another object is to provide a displacement pump which is compact and small in size for its capacity and which can be installed in wells of various depths and of small diameter, or which can be inserted into a container through a small opening therein.

Another object is to provide a pump in which the several pump chambers are combined into an integral unit, while the timing and fluid control mechanism comprises another unit, both unitsbeing so arranged that they may be mounted together to form a unitary assembly, or the timing and control unit may be located apart from the pump unit and connected thereto by conduits of suitable length.

Another object is to provide a pump unit in which intermingling of the two fluids is avoided by preventing the conveyed liquid from entering into the pressure fluid supply conduit and the pressure fluid passing through the admission and discharge valves into the discharge conduit.

Another object is to provide a pump in which the maximum rate of discharge is limited.

Another object is to provide a pump in which the frequency of the operating cycle may be controlled.

Another object is to provide snap action pressure fluid operated pneumatic timing means for a pair of pressure fluid reversing valves controlling the supply of a pressure fluid.

Another object. is to provide ready accessibility of the operating parts of a displacement pump.

Another object is to provide a displacement pump for conveying fluids of relatively high viscosity.

Another object is to provide a pump which consumes pressure fluid varying in accordance with the rate of liquid discharge, thus affording high efliciency for varying loads.

The accompanying drawings are illustrative of several embodiments of the invention. In the drawings Fig. 1 is an elevation partially in section of a preferred form of the displacement pump.

Fig. 2 is a bottom view of Fig. 1.

Fig. 3 is a transverse section along the lines 3-3 of Fig. 1.

Fig. 4 is a vertical section along the lines 4-4 of Fig. 1.

Fig. 5 is a vertical section along the lines 5-5 of Fig. 4.

Figs. 6 and 7 are transverse sections along the lines 6-6 and 'i-l, respectively, of Fig. 5.

Fig. 8 is a vertical section through the upper part of the pump in the same plane as the section Fig. 5.

Fig. 9 is a vertical section along the lines 99 of Fig. 8.

Figs. 10, ll, 12 13, 1e, and 15, are horizontal sections along the lines !i3l5, ll-ll, l2--|2, iii-I3, ifl-Jd, and i5-l5, respectively, of Fig. 9.

Figs. 16 and 17 are a vertical section along the lines l5ll5 and l'l-l'l, respectively, of Fig. 13.

Figs. 18 and 19 are diagrammatic showings of the coordination of the various elements of the pump illustrating the operation thereof.

Fig. 20 is a vertical section of a modification of certain parts shown in detail in Fig. 8.

Figs. 21 to 23, respectively, show diagrammatically various methods of installing the pump.

The apparatus illustrated in drawings Figs. 1

to 19, comprises a duplex displacement pump unit 49, and an air control and timing unit ll, connected with the pump unit as will be explained later. The pump unit ii! has two pump chambers 42 and it of like construction, one of which only needs to be described in detail. The pump chamber '52 is provided at its lower end with a normally closed ball type fluid admission valve Ml, having an inlet orifice located in a foot casting E6. The ball ii of valve 44 is arranged to engage a seat 48 interposed between the orifice and a valve chamber 55 located in a bottom header casting 55, in line with the lower end 5i oi the pump chamber. A spacer 52 attached to the upper end of the header 5!! is provided with a bore 53 of like di ameter as the bore 5 and coaxial therewith. Attached to the top of the spacer 52 in a liquid tight manner is a tube 5 3 which is semi circular in cross section and which forms the intermediate part of the chamber 62. The upper end of the tube 54 is attached in a liquid tight manner to an upper chamber header or manifold 55. The header 55 is provided with an orifice 55, through which the chamber 122 communicates with a threaded recess 5? extending downwardly into the manifold 55. A conduit 58 threadingly engages said recess 5l. Arranged inside of the conduit 58 are two air conduits 59 and 69, one for each chamber. The conduit 59 communicates with the orifice 56, as will be explained hereafter. The lower header 53 is also provided with two ball type outlet valves i i and 62 for the chambers 32 and d3, respectively. The outlet valve ti is connected through a horizontal channel 63 with the chamber 69 and it is further connected to a liquid discharge conduit 64 which passes in a liquid tight manner through spacer 52. The upper end of the conduit 6 3 is connected through the upper header 55 to the recess 5i. The connections of the chamber as are arranged In a manner similar to those of the chamber 62 as will be apparent from the drawings.

In the operation of the pump the unit is immersed into a liquid preferably so that the liquid surface is above the highest point of the upper header 55. Thercupon, if the conduits 59 and 6B are open to atmosphere, the liquid enters through valves 44 into the respective chambers 42 and 43, until the liquid inside of the chamber is level with the liquid on the outside of the pump. If now air under pressure is passed into the chamber 42 through the conduit 59, it displaces the liquid therein, the valves 44 closing due to combined gravity and pressure, while the valve 6! is opened by the pressure of the liquid and the latter rises into the conduit 54 from where it is discharged as will be explained hereinafter. The air is supplied to the tWo conduits 55 and 68 alternately as will also be explained hereinafter. After the liquid in the chamber 52 has been emptied through the conduit 54, the supply of air to the conduit 59 is stopped and the air in the chamber 42 is permitted to exhaust to atmosphere or is sucked out of the chamber 42 to permit liquid to again fill the chamber, as aforedescribed, and the cycle is repeated. The admission and exhaust of air from the conduits 55 and 56 is controlled by valves which are arranged in the timing unit 3!.

The more detailed construction of the pump unit will now be described. The foot casting 45 is provided at its lower edge with a number of downwardly projecting feet so arranged that when the pump rests on the bottom of a liquid container, liquid may enter under the foot casting iii through the spaces between the feet 65.

- The casting 15 is further provided with a central recess 65, of large diameter into which open the orifices of the admission valves 44. The lower end of the recess 55 is closed by a mesh screen Si, which prevents foreign matter carried by the liquid from entering the admission orifices. Interposed between the foot casting 4G and the bottom header 55, is a gasket 58 which has suitable openings for the connecting ducts. A valv seat 69, may be interposed between the cylindrical bore 55 and the valve chamber 39 for a purpose which will be explained hereinafter. A further gasket H3 is interposed between the header casting 50 and the spacer 52. Suitable screws H, which extend through holes l2 in the extension 55- and in the header 50, and which engage tapped holes in the spacer 52 provide for the aligned assembly of the three last named parts into a unitary lower cylinder head.

The upper face of the spacer 52 is provided with two semi-circular grooves it, into which are fitted the lower ends of the semi-circular tubes 55, and suitable packings M, are interposed between said tubes and the spacer 52. The com cluits 54 pass through bores 15 in the spacer 52, which are axially aligned with the valves El and 62, respectively. The lower ends of these bores are countersunk at it to a larger diameter to accommodate packing nuts ll. The packing nuts are internally threaded to engage the threaded ends of the tube 5 so that upon screwing them on the tubes they pull the same downwardly into the spacer 52. Suitable packings it are interposed between the upper end of the packing nuts and the shoulder of the bores E5, to provide a liquid tight joint. The packing nuts H are also provided at their lower end with a U-shaped stirrup l5, which affords means for turning the nuts and also affords a passage for the liquid into the conduits Be. The valve 5! is provided with a valve ball St the upward movement of which is limited by the stirrup '15. The countersunk hole it in the casting 52 is extended downwardly into the header 5E3 and is provided with a valve seat 51 for the valve 5i, from which a bore 82 extends downwardly. The lcwer end of the bore 82 is closed by the gasket 68 and communicates through the horizontal channel 53 with the chamber :35. The extension of the bore E6 in the casting 50 also serves as a cage for the valve ball and permits the passage of liquid around and past the ball.

The lower face of the upper cylinder header 55 is provided with semi-circular grooves 83, similar to the grooves 73, to receive the upper end of the semi-circular tubes 54' and packings 8d are interposed between the end of the tubes 5% and the bottom of said grooves. The conduits 5d are threaded into the lower end of bores 85, which in turn communicate with the recess 5'! and thus with the interior of the conduit 58. It will thus be apparent that after the conduits 6 1 are screwed into the casting 55 and the latter is assembled with the tubes 54, the spacer 52 and the packing nuts 11, the tightening of the latter clamps the tubes 5d tightly into the upper and lower seats, so as to assemble the top header 55 with the tubes 54 and the spacer 52 into a solid unit. Thereafter the bottom header 5B and the foot casting l6 with their component parts may be assembled and fastened together with the screws H.

The bottom 86 of the recess 53 in the header is also provided with two threaded holes 8?, one each connecting with one of the orifices 56. The tubes 59 and respectively, are threaded into said holes to provide a direct connection between said tubes and the pump chambers 52 and 33, respectively. lhe orifices 55 may each be provided with a valve seat 38, the purpose of which will now be explained.

It may be desirable to provide the pump with means which upon the discharge and admission of liquid by the pump chamber will prevent the passage of air to and through the liquid outlet valves 5! and $2 of the pump or the rise of liquid into the air supply conduits 59 and it For this purpose a cylindrical float valve 139, which is so proportioned that it will float in a substantially vertical position may be arranged in each pump cylinder as shown in dotted lines in Fig. i. The valve is so proportioned that it is only partially immersed in the liquid. It is provided with conical upper and lower ends 90 and 9|, respectively, to provide for cooperation with the valve seats 58 and 59, respectively, when the float has been moved to the corresponding end of the chamber by the liquid. The body of the float is of a diameter to aiiord free passage for the liquid between the float and the wall of the bores 53 and at. Thus when the liquid in the cylinder A2 is at a certain low level, the lower cone 9! cooperates with the valve seat 59 to stop the flow of liquid into the compartment l'fi which prevents the air above the liquid level in the cylinder 52 from entering into the said compartment. On the other hand, if the rising liquid level in the cylinder 42 approaches the valve seat 88, the up per cone 96 of the iloat cooperates with the valve seat 88 to provide a seal which prevents any fur ther escape of air and the rise of the liquid beyond the valve seat 88 into the air conduit 59.

The air control and timing unit assembly ll will now be described. The assemby comprises a housing made up of the following parts: a manifold casting 9 i, a manifold spacer 2, a valve housin $3 a top spacer unit 9 8, and a cover The manifold unit 8i is a substantially circular casting provided with an axial bore 83, with re duced diameter at its lower end to provide an annular seat 9?, intermediate of its ends. The bore 56 is tapped at its bottom end to receive the upper end of the conduit 58. A tapped bore as, extends through the side of the manifold into the bore lit. The tapped bore 58 is adapted to receive a liquid outlet pipe 99, through which the liquid under pressure is conveyed to its destination. A circular disc Hill is arranged to rest onthe seat Ell. The disc is provided with two bores llll through which the upper ends of the tubes 59 and 69, respectively, extend. These tubes terminate approximately level with the upper face of the manifold 9i. Afterthe manifold is screwed on to the conduit 53, the conduits 5d and Gil are rigidly clamped to th circular disc H10 by means of a semi-circular plate :92, which is slightly larger in dimensions than the distance between the wall of the bore 96 and the outer wall of the respective tube 59 or (iii. Clamping plate m2 is normally slightly tilted so that when it is pulled towards the disc Hill by means of a screw me, which engages a threaded hole in the disc, said plate 32 forms a wedge to hold the tubes 59 and 60, respectively, rigidly in the disc.

The spacer a2 is mounted on top the upper face of the manifold 9!, a gasket i ll being interposed therebetween to provide a liquid and air tight joint. The spacer 92 is provided with two recesses 92a, into which the tubes and E55, respectivel extend. Bores 92!) extend from each recess through the spacer and a ice is interposed between the spacer S2 and the valve housing 93. Suitable packing rings 520 are interposed between the ends of the tubes 55% and (iii and the respective recess.

The manifold, spacer and the valve housing may be fastened together by means of headed screw bolts it, which pass through suitable holes in the manifold and spacer which engage tapped holes in the valve housing. At its lower end the valve housing is provided with a circular recess Eel in which is mounted a metallic bellows 5&3. The bellows is closed at its lower end by a disc its. An orifice i i e extends through the gaskets Hi l and N15. The spacer 32 and the disc I89, together with orifice it'fia in disc 1653, provide a connection between the recess $6 and the inside of the bellows 08. The lower end of the bellows and the disc i239 are further provided with a circular flange iii which is seated air tight in a counter bore 5 I2 of the recess 45?. The upper end of the bellows is provided with a circular disc N3 of suitable material arranged to be normally forced against a valve seat lit inserted in a vertical bore H5, in the valve housing, the force being supplied by precompression of the bellows H18 upon assembly. The valve housing is also provided with a threaded inlet conduit M5 for the admission of air, which inlet connected by a bore 5 ll with the recess The cylindrical valve housing 93 contains two horizontal high pressure admission valves 52B and Hi, and two exhaust pressure valves E22 and I23. for controlling the air which actuates the timing mechanism for the pump control unit. The valves I29 and I22 are mounted in axial alignment with each other and at right angle to the central axis of the valve housing 93. The valves HI and I23 are also arranged in axial alignment with each other and with the first pair of valves, but below the latter. All four valves are alike in construction and it is therefore only necessary to explain the construction of one. The valve 12a has an inner valve chamber I24 and an outer valve chamber with a valve seat I26 arranged intermediate of the two chambers. A cone shaped valve member i2? is provided with a central stem lit the lower end of which is arranged to slide in a radial bore are extending into an axial recess I39 in the valve casing. The outer end of said valve stem provides a guide for a. compression spring I3 I, which is interposed between the valve cone and the bottom of a recess I32 in a cover screw I33, which closes the outer valve chamber I25, the spring biasing the valve to the closed position.

The valves I23 and I2I, I22 and I23, may be forced open by a concave barrel shaped cam I34, which is provided with an upward extension having circular grooves of V-shaped cross section I35 and I365. The upper end of the cam we is slidable in a bushing I31, which is shrunk into the bottom wall of the spacer unit 94. The spacer. unit 94 is provided with a recessed circular chamber I38 extending from its upper face downwardly for. purposes which will be explained hereinafter. Clamped between the spacer unit 94 and the cover 95 is a flexible circular diaphragm I39 of suitable material. The valve housing 93, the spacer unit 94, and the cover 95 may be aligned and assembled into a unit by cap screws I4Il, which extend through the cover 95 and the spacer unit 94 into tapped holes in the valve casing 93. A gasket I il is interposed between the casing 93 and the spacer unit 94. The center of the I39 is clamped between an upper diaphragm plate I42 and a lower diaphragm plate I43. The diapragm and the upper diaphragm plate are each provided with a hole I44 through which passes a registering raised boss I45 on the upper face of the lower diaphragm plate I43.

The diaphragm and the upper and lower diaphragm plates are clamped together by a headed bolt I46, whose diameter is progressively reduced to form shoulders I41 and I48. The end of the bolt is threaded to engage a nut by means of which the diaphragm and the plates are rigidly held against the shoulder I48. The cover 95 is provided with a recess or chamber I49 to aiford a space permitting oscillation of the diaphragm and the upper diaphragm plate. Said chamber is provided with a downwardly depending circular abutment I52, which limits the upward movement of the diaphragm by engaging the upper diaphragm plate I42. The lower diaphragm plate is bell shaped, the central part of its inner face being provided with an abutment surface II, which is arranged to engage the upper end surface I52 of the actuating cam I34.

The upper end of the actuating cam is provided I with a central recess I53 in which is mounted a spring I54 which is under initial compression and is of such proportions that it can be further compressed until the surfaces I5I and I52 engage upon movement of the diaphragm. When said surfaces engage further downward movement of diaphragm is directly transmitted to said cam. A central bore I55 in the cam provides for sliding engagement of the latter with the intermediate portion of the bolt I45, while the lower portion I56 of said bore is enlarged to form a recess for receiving a prec'ompressed lower spring I51, which is arranged to abut the bottom of the recess I56 and the inner face of the head of the bolt I465. The two springs I54 and I51 are normally precompressed an equal amount so that the thrusts which they exert between the cam and the bolt are balanced. The shoulder I41 of the bolt I45 is adapted to engage the bottom of the recess I56 upon further compression of the lower spring I51. The bushing I31 is provided at its outer circumference with a circular groove I58, which houses a tension spring I59 arranged in the shape of. a toroid. Coplanar with the groove 533 I are a number of, radial holes I60 extending through the wall of the bushing to, house balls IISI which are urged by the spring I59 into the groove I35 or I36 of the cam, when the respective groove is coplanar with the groove I58. Thus the balls oppose movement of the cam in an axial direction in response to longitudinal thrusts of the springs I54 and I51, but when the surface I5I engages the surface I52 or the shoulder I41 engages the bottom of recess I56, the thrust on the cam I34 exerted by the diaphragm I39 is high enough to overcome the force of the spring I59 and to push the balls out of the grooves and thus permit the cam to yield to such pressure and move under the influence of the springs I54 and I51 until it is again arrested by the balls engaging the other groove. The concave surface IE2 of the cam I35 is of such proportions longitudinally and diametrically that when (as shown in Fig. 9 in full lines) the stems of the valves I28 and I22 engage the cam at its smallest diameter, the stems of the valves I2! and I23 engage the same at one of itslargest diameters and vice versa. In the position shown in full lines in Figs. 8 and 9, the cam is in its uppermost position and the valves I2I and I23 are open, while the valves I28 and I22 are closed. When the cam been moved to the dot-ted position wherein the balls [6| engage the upper groove I36, the valves I20 and. I22 are open, while the valves I2! and I23 are closed.

The passages for the air actuating the diaphragm I39 are as follows: As already pointed out air under pressure is admitted through the inlet He and passes thence through the bore H1 The air exerts a pressure into the recess I91. on the outside of the bellows I58 tending to compress it and if the resulting force is sufiiciently in excess of the force due to the pressure exerted on the bellows by the liquid admitted to the interior through the orifice H0 and the precompression force on the bellows, the latter is compressed to separate the disc I53 from the valve seat H4 to admit air through the duct M5 to the horizontal duct I54, thence into a circular recess I in the valve housing 93, through the slanting duct I56, downward through the duct I61, to the outer valve chamber I25 of valve I22 and through the duct I61 to the outer chamber of the valve I2I. The inner chamber I24 of the valve I 213 is connected to the lower diaphragm chamber I38, through the vertical duct $8.. The inner chamber of the valve I2I is connected to the upper diaphragm chamber I49,

through the upwardly slanting duct I59 in the valve housing and shown in dotted lines. The duct I89 connects with the vertical duct I10 in the upper spacer 94 through the horizontal duct I'II which leads to the upper diaphragm chamber I49.

The upper diaphragm chamber is connected to the outer chamber of the valve I22 through the horizontal duct I12, the vertical duct I13, the horizontal duct I14 and the vertical duct I15.

The lower diaphragm chamber I38 is connected to the outer chamber of valve I23, through the slanting duct I16 and inwardly slanting duct I11 in the valve cage 93. The inner valve chambers of the valves I22 and I23 are connected to a common vertical duct I18. Said duct is provided near its lower end with a set screw I19, which may be screwed into said duct to more or less restrict it so as to afford an obstruction for the air flowing therethrough. The duct I18 connects to a horizontal duct I80, thence through 9 the horizontal ducts I8I and I82, to the air exhaust conduit I83.

The operation of the device is as follows: If with the apparatus shown in Figs. 8 and 9, air under pressure is admitted through the conduit lit, the pressure of the air opens the valve I I4 and air is admitted through the passages already traced, through the valve IN to the upper diaphragm chamber I as. The diaphragm thus is deflected downwardly thereby increasing the compression of the spring I54 and reducing the compression of the spring I51 and urging the cam i341 downwardly. But the cam is held in place by the locking action of the balls IS! in the groove I35, the excess thrust of the spring I54 not being sufficient to unlock the cam. When the diaphragm ultimately has been deflected by the air in the upper chamber to the extent that the surfaces I5I and 552 engage each other, its full thrust is exerted against the cam. This forces the balls it! out of the groove I35, and the spring lt 'i moves the cam with a snap action until the shoulder I il abuts the bottom of the recess E55. In this position the balls I35 under the impulse of the spring I59 drop into the groove ltd and thus again look the cam, but now in its lowermost position.

While the cam was in its upper position the valve 522 was closed so as to cut on the escape of the compressed air from the upper diaphragm chamber. As already explained, the lower diaphragm chamber was connected with the inner valve chamber of the valve I23 in the original upper position of the cam. However, in this position the valve l23 is open, therefore the air in the lower diaphragm chamber, which is displaced by the downward movement of the diaphragm, can flow through the passages already traced to and through the lower valve l23 to the air exhaust list. The speed of escape of the air and therefore the resistance offered to the downward movement of the diaphragm and thus its speed of movement may be regulatable by the adjustment of the screw Il -9. Obviously, instead of providing the adjustment screw lid to throttie the air exhaust from the compartments I38 and 539, a similar arrangement may be substituted in the inlet duct I5! for the valves I23 and iii for regulating the inlet pressure to the diaphragm compartments.

As soon as the cam has been moved to its lowermost position as described, the valves iEi and IE3 close, while the valves I and I22 are opened. Thus the supply of compressed air to the upper diaphragm chamber and the exhaust of air from the lower diaphragm chamber are out off. However, now the lower diaphragm chamber is connected to the source of compressed air through the valve I20, whereas the upper diaphragm chamber is connected to theexhaust conduit through the valve I22 and the diaphragm moves upwardly, the operation being apparent from the foregoing. Thus the diaphragm oscillates up and down at a rate which is determined by the adjustment of the rate of exhaust by the screw H9, thepressure of the air supplied through the conduit H6 and by the throttling effect of the valve il l, resulting from the action of the bellows W8. This action is as follows: If the pressure of the liquid at the delivery conduit 99 exceeds a certain value by stoppage or low rate of discharge of liquid so that the closing force of the bellows due to the liquid pressure exerted by the bellows IE8 is greater than the opening force due to the air pressure on the 10 outside, the valve H4 partially closes thereby throttling the passage of compressed air to the diaphragm chambers, which in turn reduces the pressure differential between the two sides of the diaphragm and causes it to move slower and thus reduce the frequency of its oscillations.

For a full understanding of the control of the air supplied to the chambers 42 and ts reference is made to the diagrammatic showings Figs. 18 and 19. As has been pointed out heretofore the diaphragm I 39 and the diaphragm disc I43 oscillate cyclicly'between an upper and lower limit. The total travel of the disc I43 may thus be divided from top to bottom into four equal zones A, B, C and D, as indicated in the drawing.

The air supplied to the chambers 42 and 43 is controlled by four spring biased normally closed valves (shown in detail in Figs. 16 and 17) as follows: An inlet valve I85 and a discharge valve I8 3 control the air for the chamber 42, and an inlet valve IS? and a discharge valve I85 control the air for the chamber 43. Each valve comprises a conical valve body cooperating with a valve seat which is interposed between an inner and an outer valve chamber. The valve I85 is provided with a valve stem at its inner end, said stem projecting upwardly through a suitable packed guide hole in the upper spaced 93.

. The stem is of such length that with the valve 585 closed a lower annular flange I88 of the diaphragm plate M3 makes contact with it to open the valve when said plate enters the zone B on the downstroke of the diaphragm and to maintain the valve open until the diaphragm on its succeeding upstroke returns to the same position. The outer valve chamber of valve IE5 is closed by the screw plug IBfl, which is provided with a recess to receive a compression spring interposed between the plug and the valve, to urge the latter to its closed position. The outer chamber of valve I is connected through a conduit i953. conduit H5, valve Ii l, recess lil'i, conduit Ill to air supply inlet H5.

The valve iii i is provided with an upward extending valve stem which is adapted to engage with a lost motion the flange tilt of the diaphragm plate Hi3, so that said valve is opened when the diaphragm plate enters the zone A on its up strike and it stays open until said plate on its succeeding downstroke returns to the same position. A compression spring is interposed between the upper face of the valve and on abutment at the lower face of the upper spacer, said spring urging the valve to its closed position. The valve I88 is constructed similarly to valve i535, except that its valve stem is of such length that the valve is opened when the diaphragm plate enters the zone I) on its downstroke it is kept open until said plate on the succeeding upstroke reaches again the point of opening. A compression spring is interposed between the lower surface of the valve and the gasket I85 to bias the valve to its closed position. The valve I8! is similar in construction to the valve I84, except that its stem is proportioned so that said valve I3? is opened when the diaphragm plate on its upstroke enters the zone C and is kept open until the diaphragm returns to the same position on its succeeding downstroke.

The outer chamber of the inlet valve I8! is connected through the slanting conduit H54 to the conduit H5, and thus over the path already traced to the inlet conduit H6. The inner chamber of the valve I 31 is connected through the horizontal conduit I9I, vertical conduit I92, the short connection I93 and one of the bores 9212 to the tube The outer chamber of the exhaust valve lfiii is connected to the tube 553, through the horizontal connection I93 and one or" the bores 92b. The inner chamber of the valve its is connected through the conduits IBI and to the exhaust conduit use. The inlet chamber of the valve I is connected through chamber lii'tvalve lit and conduits H5 and 59:3 to the inlet conduit lid. The outer chamber of the valve E85 is connected through the horizontal conduit ill l, vertical conduits i535, i2 5, and one of the bores 92!) to the tube 59. The outer chamber of the outlet valve l fi i is connected through the conduits I95, H95, and one of the bores 92b to the tube 59, while the inner chamber of said valve I36 is connected through. the bores I98, lfil and H32, to the exhaust conduit M33.

The diagrammatic showing, Figs. 18 and 19, illustrate the control of the admission of air to and its exhaust from the pump cylinders. The valve M35 is the air admission valve and the valve id lis the air discharge valve for the chamber 22, while the valve i8? is the air admission valve and the valve iSt the air discharge valve for the chamber d3.

Fig, 18 shows the diaphragm I39 in full lines on its upward stroke shortly after its reversal at its lowermost position. The cam i134 thus is in its lower position as has been described. The circular flange of the lower diaphragm plate M3 is in the position shown and maintains the admission valve !85 open, so that compressed air is passed into the cylinder 42 to force the liquid therein through the valve 6i, conduit 65, conduit 58 and into the liquid outlet conduit 99. As the diaphragm Hi9 continues to move upwardly it opens the valve EB'I, thereby admitting compressed air into the cylinder i3 and forcing the liquid therein through the ball valve 62, conduit 53, into the discharge conduit 99, So that for a brief interval both cylinders A12 and 43 discharge liquid. Shortly thereafter the valve I85 closes thereby shutting ofi further delivery of compressed air to the cylinder 42. By this time the liquid in the cylinder 42 has reached its lowest level. As soon as the compressed air is shut off from the cylinder 12, the ball valve 6| closes. At the same time the valve its is opened, thereby relieving the air pressure in the cylinder 42 and permitting the air therein to exhaust through said valve I85, whereupon the pressure of the liquid in the tank T opens the valve Ml of cylinder 2 to again force liquid into the cylinder 32. During this upward movement of the diaphragm, the valve I8? remains open and the compressed air continues to push the liquid in cylinder 33 through the valve 62 into the exhaust conduit 99,, the admission valve 44 of cylinder 33 remaining closed due to the excess pressure above said valve' over the pressure or the liquid in the tank T.

After the diaphragm Hi3 reverses its movement from the upstroke in the manner already described, moves down again to the position shown in full lines in Fig. 19 during which interval the valve lBl remains open so that the discharge of liquid from the cylinder 43 continues, while the cylinder 42 has been filled with liquid, the air in the latter cylinder having been exhausted through the valve use. When the diaphragm. reaches the position shown in full lines in Fig. 19, the valve .585 again begins to open and the valve Hi l closes, so as to again cause discharge of liquid from the cylinder '42, as has already been described. A :brief interval thereafter the valve 81 is closed and the valve 1'86 is opened, thus again cutting off the supply of compressed air from the cylinder 43, to stop the discharge of liquid therefrom and thereafter permitting liquid from the tank T to fill the cylinder 43.

Thus it will be seen that the discharge of liquidfrom the two cylinders alternates, but so, that there is .an overlap during which both cylinders discharge liquid simultaneously. The pressure at which the liquid is discharged is substantially that of the pressure of the air supply and it is substantially constant due to the "overlapping of the discharge from the two cylinders. The pressure of the liquid at the discharge conduit 99 is somewhat affected by the friction in'the valves, the liquid and the air conduits, In order to regulate the liquid pressure further :the exhaust conduit 99 is connected, as described, to the interior of the bellows I08, while the com.- pressed air inlet conduit I6 is connected to the chamber surrounding the bellows, so that the bellows is compressed or extended depending upon the relation between the sum of the precompression pressure and internal pressure and the opposing external pressure acting on the bellows. If the pressure of the liquid increases relative to that of the compressed air the bellows tends to close the valve H4 and vice versa. Thus the pressure delivered to the valves I20 to H3, inclusive, and I84 to I81, inclusive, is regulated in accordance with said differential pressure, thereby regulating the speed of operation of the diaphragm and the speed of liquid flow through the pump chambers in accordance with the liquid demand. Furthermore, the amount of pressure fluid is varied in accordance with the amount of liquid discharged, thus conserving fluid pressure and the corresponding energy to produce it.

To regulate the frequency of alternation of the diaphragm with respect to the speed with which the liquid flows into the cylinders on the admission stroke, the set screw valve I19 'in the air exhaust from the diaphragm chambers is provided. This-valve permits the adjustment of the speed with which the diaphragm oscillates as has already beendescribed. It is thus possible to adjust the frequency of oscillation with respect to the maximum. speed with which liquid is admitted into and exhausted from the cylinders to insure a substantially 'full stroke during the operation of the pump.

Fig. 20 is a modification of the mechanism for actuating the cam134 by the diaphragm 139. The lower diaphragm disc I43 shown in Fig. 8 is replaced by 'a modified disc 200, which is similar in shape to the disc I43, except that it is provided with a generally cylindrical extension 2M, which projects downwardly below the circular flangeZilZ, which latter corresponds in shape to the circular flange I88 of the disc I43. The bushing I3? in Fig. 8 is replaced by a bushing 283, which is provided with a number of radial bores 2'94, to receive the balls lfil, which c'ooper ate with the circular grooves I35 and I36 of the cam I3 4. The balls I6l are normally retained in the groove I35 or I36, respectively, by an internal circular cam surface 205 of the bushing 203, which is of such diameter as to normally look the balls in one or the other of said grooves to hold the cam I34 in the respective position. As the diaphragm and with it the disc 200 move down from the position shown, the balls are forced outwardly due to the action of the spring I54 and i"! and slide over the conical surface 296 to ultimately engage the inner cylindrical surface 201, which is of larger diameter than the cam surface 265, thus releasing the balls from the respective groove and permitting the cam to move to its other extreme position as has been described heretofore. This, as will be apparent, causes reversal of the diaphragm. Upon the succeeding upward motion of the cam the balls are again locked in the respective groove by the cam surface 205. It will thus be seen that the cam is positively locked against movement in one or the other of its extreme positions during travel of the diaphragm and is only permitted to be moved thereby from its one extreme position to the other when the diaphragm is in its respective extreme position,

Fig. 21 illustrates the installation of the pump shown in Figs. 1 to and described in connection therewith. The pump may be inserted in a barrel or tank T, and the air inlet conduit H6 and the air outlet conduit I 83 connected to the delivery and the inlet ports, respectively, of a compressor C. By returning the exhaust air from the controller 41 to the compressor, the energy which is in the exhaust air is to a large extent recovered and therefore the device as a whole operates more efficiently. However, it is also possible to open the exhaust conduit I83 directly to atmosphere in which case the pressure of the exhaust air is that of atmosphere, while when the exhaust air conduit is connected to the suction end of the compressor the exhaust air pressure is below atmosphere. Connection of the exhaust conduit to the intake of the compressor is particularly advantageous for pumping high viscosity liquids, as it increases the speed of filling of the pump chambers and thus increases the capacity of the pump.

Fig. 22 shows another method of installation of the device. In this case the pump is installed at a level above that of the liquid contained in the barrel T, or in a well. In this case the return conduit I83 of the control unit 4! must be connected to the suction end of the compressor C so as to produce in the cylinders of the pump a suction head which will draw the liquid into the cylinder against the atmospheric pressure. Also the foot casting 45, instead of being open at the bottom, is closed. In other words, the recess 66 forms a closed chamber to which a suction pipe 250 which extends down into the liquid is attached. In all other respects the device is constructed the same and operates in the same manner as heretofore described. It will be apparent that the conduits 58, 59, and 60, which connect the control unit 4| with the pump unit may be made in different lengths to provide for different distances of mounting between the pump unit 40 and the control unit 4!.

Fig. 23 shows schematically two pump units 40 and 240 connected in tandem to lift liquid from a deep well W in two stages. The two units 40 and 240 may be controlled by a single control unit 4| supplied by a compressor C. The lower unit 40 is immersed below the level of the liquid and is controlled and functions in the same manner as the unit shown in Fig. 1. However, the liquid delivery pipe 99 0f the unit 40 is connected to the bottom of the unit 240 which is provided with a closed foot casting smiliar to the unit shown in Fig. 22. The unit 246 in turn is provided with a liquid header and delivery pipe 299 which may extend a desirable distance above the top of the pump unit 240. Air delivery pipes 259 and 260 with branches 59 and 60 extend from the controller 4| to the units 24!] and 40, respectively. The compressor is connected in the usual manner to the air delivery conduit I I6 and the air exhaust conduit I83 of the controller 4|. The cylinders 42 and 43 of the lower pump unit 40 are filled by the liquid under the influence of the static head of the latter. On the exhaust stroke for the cylinders 42 and 43, compressed air is supplied to the cylinders by the conduits 59 and EB, respectively. The liquid thereupon rises in the conduit 99 and into the cylinders 242 and 243, respectively, from where it is delivered through the chamber 264 int the header and exhaust conduit 299. The delivery head of the two pumps H and respectively, depends upon the pressure of the air supply, the two heads being approximately equal though they may differ from each other.

The device operates in the following manner: Assuming that at the start the lower cylinders 42 and 43 are filled with liquid and pressure air is supplied through the conduit 259 and 59. This will force the liquid from the cylinder 42 into the conduit 99, while at the same time the cylinders 43 and 243 are connected through the conduit 2% and the controller H to the exhaust conduit I83. The liquid therefore will rise from cylinder t2 through conduit 99 into the cylinder 243 to fill the same. When the cylinders 42 and 243 are about filled the controller 4i operates in the usual manner to disconnect the conduit 25%! from the high pressure air and connect it to exhaust, while the conduit 26! is conected to the high pressure air. Thereupon the cylinder 42 will again fill with liquid while the liquid in the cylinder 43 is now forced through the conduit 99 and into the cylinder 232. At the same time the air delivered to cylinder 242 forces liquid therein into the header 299. When the cylinders 43 and 242 are again filled and the cylinders 32 and 243 are again emptied, the air delivery to the conduits 259 and 260 is again reversed and the cycle is repeated. Thus it is apparent that by connecting the two pumps in tandem a much higher head of liquid can be overcome than by the use of the same pump, the pressure of the air supply being in both cases the same.

It will of course be possible to use more than two pump units in tandem, the operation being obvious. It will also be possible to operate the lower pump unit 42 with a suction head in the same manner as explained in connection with the arrangement Fig. 22.

It will be obvious that the delivery conduit 299 may be arranged for control of the inlet pressure of the air supplied through conduit I83 as explained in connection with Figs. 8, 18 and 19.

Other modifications within the scope of the present invention and the scope of the appended claims will be apparent to those skilled in. the art.

What I claim as new and desire to secure by Letters Patent is:

1. In a displacement pump, in combination, a header, a plurality of displacement units each providing a chamber adapted to contain oppositely varying volumes of a fluid substance and a pressure fluid, each unit having non-return fluid admission and discharge means affording admission to the respective chamber of fluid substance from a source of such substance and alternatively discharge thereof from said chamber to said header in response to variations of the volume of pressure fluid in said chamber, joint pressure fluid and sequence control means operl able to afford periodic supply of pressure fluid to each chamber individually, with initiation of supply to each chamber prior to termination'of such supply to at least one of the chambers preceding in sequence of operation :and -to effect withdrawal of such fluid irom each chamber in the intervals between the respective supply periods, and means to regulate thespeed of .operation of said sequence control means independently of the supply of pressure fluid to said chambers.

2. In a displacement pump, in combination a header, a plurality of displacement units each providing a chamber adapted to contain oppositely varying volumes of a fluid substance and a, pressure fluid, each unit having non-return fluid substance admission and discharge means affording admission 'to the respective chamber of Jfluid substance from a source of such substance and alternatively discharge thereof from said-chamber to said header in response to variations of the volume of pressure fluid in said chamber, and means operable cyclically to withdraw pressure fluid from the chamber and alternately supply pressure fluid thereto, sequence control means for the several of said plurality of cyclically operable means to effect sequential initiation of their operating cycles and initiation of supply of pressure fluid to each chamber prior to termination of supply of pressure fluid to at least one of the chambers preceding in the sequence of operation, and means to regulate "the speed of operation of said sequence control means independently or the supply of pressure fluid to said chambers.

3. In a displacement pump, in combination, a header, a plurality of displacement units each providing a chamber adapted to-contain opposite- 1y varying volumes of -a fluid substance and a pressure fluid-each unit having non-return fluid substance admission and discharge means affording admission to the respective chamber of fluid substance from a source of such substance and alternatively discharge thereof from said chamher to said header in response to variations of the volume of pressure fluid in said chamber, means operable cyclically to Withdraw pressure fluid from the chamber and alternately supply pressure fluid thereto means responsive to the fluid level in saidchamber to prevent access of pressure fluid to said fluid substance admission means and access of fluid substance to .said cyclically operable means, and sequence-control means for said plurality of cyclically operablemeans to effect sequential initiationof their operating cycles and initiation of supply of pressurexfluid to each chamber prior to termination of .supply'of :pressure fluid to at'least one of the chambers;preceding in the sequence of operation, and means to regulate the speed of operation of said sequence control means independently of the supply .of pressure fluid to said chambers.

4. In a displacement pump, in combination, a header, a plurality of displacement units each providing a chamber adapted to contain .opposite varying volumes of a fluid substance and a pressure fluid, each chamber having'anadmission valve affording admission of fluid substance from a source-of such substance and a discharge valve affording discharge-oi fluid substance from said chamber to said header in accordance with variations of the volume of pressure fluid in said chamber and individual pressure fluid control means operable cyclically 'to withdraw pressure fluid'from the respective chamber-and alternate ly to supply pressure fluid athereto, .a sequence cycles and initiation of supply of pressure fluid to successive chambers prior to termination of supply of pressure fluid to at least one of the chambers preceding in the sequence of operation, and means to regulate the speed of operationof said sequence control means independently of the supply'oi pressureflu'id to said chambers.

5. Inadisp1acement pump, in combination, a header, a plurality -of displacement units each providing achamb'er adapted to contain opposite varying volumes of a fluid substance and a pressure fluid, each chamber having near its lower end an admission valve aflording admission of fluid substance from a source of such substance and a discharge valve aflording discharge of fluid substance from said chamber "to-saidheader in accordance with variations of the volume of pressure fluid in said chamber, a pressure fluid connection near the upper end of said chamber, individual pressure fluid control means operable cyclically to withdraw through said connection pressure fluid from the respective chamber and alternately "to supply pressure fluid thereto, means responsive to the fluid substance level in said chamber to prevent access of pressure fluid to said admission valve and access of "fluid substance to said connection, a sequence controller arranged to aiiect cyclic operation of said several pressure fluid control means with sequential initiationlcf their-operating cycles and initiation of supply of'pressurefluid to successive chambers prior to termination of supply of pressure fluid to at least one of the :chambers preceding in the sequenceof operation, andmeans to regulate thespeed of operation of said sequence control means independently-of the supply of pressure fluid to said chambers.

6. In a displacement pump, in combination, a header, a pair of displacement units each providing achamber adapted to contain oppositely varying volumes of a fluid substance and 1 a pressure fluid, each chamber having an admission valve affording admission of fluid-substance from alsourc'e of such substance and a discharge valve affording discharge of fluid substance from said chamber tosaid header in accordance with variations of the volume of pressure fluid in said chamber and individual pressure fluid control means operable cyclically to withdraw pressure fluid from the respective chamber andalternate- 1y to supply pressure fluid thereto, a sequence controller arrangedito aiTect cyclic operationcf both of said pressure fluid control means with sequential initiation of their operating cycles and initiation of supply-of pressure fluid to each chamber prior to termination of supply of :pressure ffluid to the other chamber, and means to regulate the speed of operation-of said sequence control means independently of the supply of pressure fluid to said chambers.

'7. In a-timer andsequence controller for controllinglthelpressure fluid ofa multi-chamber displacement pump, incombination, a casing having a cavity, a deflectable diaphragm mounted in saidcavitycnd dividing it into two fluid tight compartments,apressurefluid exhaust, snap action means operated by said diaphragm and adapted tolconnect one of said compartments to said inlet and the other to said exhaust alternately to aflcrd corresponding alternate deflections of said diaphragm in oppositedirections in response to the fluid pressure in said compartments, a throttling valve connected in series with said reversing means and said outlet for regulating the flow of pressure fluid therethrough, individual reversing valve means for each chamber of the pump and operable by said diaphragm to sequentially connect the several chambers alternately to said inlet and said exhaust, a regulating valve connected to said inlet for regulating the pressure of the fluid supplied therethrough, a bellows connected to said valve for normally biasing it to closed position and having its outside subjected to the fluid pressure in said inlet to open said valve, and means to subject the inside of said bellows to the pressure of the liquid discharged by said pump to oppose the opening action of said fluid pressure.

8. In a timer and sequence controller for controlling the pressure fluid of a multi chamber displacement pump, in combination, a casing having a cavity, a deflectable diaphragm mounted in said cavity and dividing it into two fluid tight compartments, a pressure fluid inlet, a pressure fluid exhaust, a reciprocatory selector, a resilient motion transmitting connection between said diaphragm and said selector tending to maintain a given relative position therebetween and adapted to store up energy upon departure from said given relative position, a latch arranged to normally look said selector at opposite ends of its travel against movement by said stored energy and to release said selector for response to said stored energy upon approach of said diaphragm of its extreme positions of travel, reversing valve means operated by said selector to connect one of said compartments to said inlet and the other to said outlet in one position of said selector and to connect said one compartment to said exhaust and said other compartment to said inlet in the other position of said selector to afiord corresponding alternate deflections of said diaphragm in opposite directions in response to the fluid pressure in said compartments, a throttling valve connected in series with said reversing means and said outlet for regulating the flow of pressure fluid therethrough, individual reversing valve means for each chamber of the pump and operable by said diaphragm to sequentially connect the several chambers alternately to said inlet and said exhaust, a regulating valve connected to said inlet for regulating the pressure of the fluid supplied therethrough, a bellows connected to said valve for normally biasing it to closed position and having its outside subjected to the fluid pressure in said inlet to open said valve, and means to subject the inside of said bellows to the pressure of the liquid discharged by said pump to oppose the opening action of said fluid pressure.

9. In a displacement pump, in combination, a header, 3, pair of displacement units, each providing a chamber adapted to contain oppositely varying volumes of a liquid and a gas, each chamber having an admission valve afiording admis sion of liquid from a source of liquid and a discharge valve afiording discharge of liquid from said chamber to said header in accordance with variations of the volume of gas in said chamber and individual gas control means operable to withdraw gas from the respective chamber and alternately to supply pressure fluid thereto, a reciprocatory selector, an operative connection between said selector and each of said gas control means afiording cyclic operation thereof upon alternately in opposite directions, a resilient mo- 18 reciprocation of said selector with sequential initiation of their operating cycles and initiation of supply of gas to each chamber prior to termination of supply of gas to the other chamber, a diaphragm, means to subject said diaphragm to a cyclically varying gas pressure for deflecting it tion transmitting connection between said diaphragm and said selector tending to maintain a given relative position therebetween and adapted to store up energy upon departure from said given relative position, and a latch responsive to movement of said diaphragm and arranged to normally look said selector at opposite ends of its travel against movement by said stored energy and to release said selector for response to said stored energy upon approach of said diaphragm of its extreme positions of travel.

10. In a fluid operated pressure pump unit of the class described adapted to be lowered in a well casing to the liquid to be pumped, a lower cylinder head providing a fluid admission, a plurality of chambers within said lower cylinder head, a fluid discharge valve for each of the chambers, an upper cylinder head providing an air conduit and a fluid discharge orifice for each of the chambers and a common fluid header for said orifices, a cylinder intermediate and joining said heads and comprising a plurality of parallel tubes respectively forming a corresponding second chamber, each tube connecting one of said fluid admission valves with a corresponding air conduit, and a liquid discharge conduit for each said first chamber interposed between the respective discharge valve and the corresponding fluid disgharge orifice.

11. In a fluid operated pressure pump unit of the class described adapted to be lowered in a well casing to the liquid to be pumped, a lower cylinder head providing a fluid admission, a plurality of chambers within said lower cylinder head, a fluid discharge valve for each of the chambers, an upper cylinder head providing an air conduit and a fluid discharge orifice for each of the chambers and a common fluid header for said orifices and cylinder units selectively adapted to be disposed intermediate and to join said heads and comprising a plurality of liquid discharge conduits and corresponding tubes each forming respective second chambers, each tube connecting one of said fluid admission valves with a corresponding air conduit, a liquid discharge conduit for each said first chamber and being interposed between the respective discharge valve and the corresponding fluid discharge orifice, the respective tubes and conduits comprising said units being of difl'erent lengths whereby the capacity and operation of said pump may be adjusted.

ROBERT E. SYKES.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,305,040 Walls May 27, 1919 1,377,776 Janney May 10, 1921 1,843,686 Koch Feb. 2, 1932 2,093,474 Okell et a1 Sept. 2.1, 1937 2,292,703 Lawler Aug. 11, 1942 2,362,802 Ciabattari Nov. 14, 1944 Certificate of Correction Patent No. 2,582,247 N ovember 28, 1950 ROBERT E. SYKES It is hereby certified that error appears in the printed specification of the above numbered patent requiring correction as follows:

Column 10, line 27, for the Word spaced read spacer; line 5L8, for strike?- read stroke; column 16, line 69, after the Word and comma compartments,

insert a pressure flMZCZ 2'nZet,;

and that the said Letters Patent should be read as corrected above, so that the same may conform to the record of the case in the Patent Ofiice. Signed and sealed this 30th day of January, A. D. 1951.

[SEAL] THOMAS E. MURPHY,

Assistant Commissioner of Patents.

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