US2825289A - Pump - Google Patents

Description

March 4, 1958 i J. E. PALMER PUMP 'Filed June 2'7, 1955 3 Sheets-Sheet l INVENTORI.

JOHN E. PALMER 'I' 1 MW PATENT ATTYS March 4, 1958 J. PALMER 2,825,289

PUMP

Filed June 2'7, 1.955 3 Sheets-Sheet 2 INVENTOR JOHN E. PALMER WMWM PATENT ATTYS March 4, 1958 J. E. PALMER PUMP 3 Sheets-Sheet 3 Filed June 27, 1955 'NVENTOR' JOHN E. PALMER V PAIENT ATTORNEYS the drive means for the pistons. Figure 11 is an enlarged fragmentary United States Patent 9 PUMP John E. Palmer, Calgary, Alberta, Canada Application June 27, 1955, Serial No. 518,270

3 Claims. (Cl. 103-474) My invention relates to new and useful improvements "in pumps, more particularly to pumps used for long periods of time for the pumping of chemical agricultural sprays, the principal object and essence of my invention being to provide a device of the character herewithin described in which the drive means eliminate sliding frictron between the crank pin and the connecting rods.

A further object of my invention is to provide a device of the character herewithin described which permits rapid and easy servicing of the piston, cylinder and valve units without the necessity of dismantling the pump from the a carrier.

Another object of my invention is to provide a device of the character herewithin described which, due to the integrally formed components thereof virtually eliminates I leakage occurring.

Still another object of my invention is to provide a device of the character herewithin described, in which the inlet and outlet valves are identical in construction, and

which furthermore can be removed externally without further dismantling of the cylinder and piston components. v A further object of my invention is to provide a device of the character herewithin described, which is relatively simple in construction, economical in manufacture, and

otherwise well suited to the purpose for which it is designed.

With the foregoing objects in view, and such other objects and advantages as will become apparent to those. I skilled in the art to which this invention relates as this specification proceeds, my invention consists essentially in the arrangement and construction of parts all as heremafter more particularly described, reference being had to the accompanying drawings in which:

' components sectioned in part to show the interior thereof. p

Figure is a side elevation showing one of the pistons. Figure 6 is a perspective view reduced in scale showing the completed pump.

' Figure 7 is a schematic view of the pump shown in association with various tanks and controls therefor.

Figure 8 is a plan view of the pump with the cover removed.

Figure 9. is a plan view of the body portion of the pump per se.

Figure 10 is an enlarged fragmentary plan view of view of the pressure relief valve portion of the device.

Figure 12 is a partial sectioned side elevation of the drive means.

In the drawings like characters of reference indicate corresponding parts in the different figures.

With the extensive advancement of chemical spraying and hydraulic power industry, a significant requirement has developed for pumping equipment capable of improving the shortcomings that are prevalent in present day pumps. Conventional piston and plunger type pumps have long been recognised as the ideal medium of transferring fluids of corrosive and abrasive types and at high or low pressures, however, the greatest objection to these types of pumps is the high initial cost and lack of versatile application due to construction principles that involve bulky driving mechanism and serviceability. The pump hereinafter described, overcomes objections to conventional type pumps principally with respect to piston drive mechanism that is commonly used.

The advantages of the new drive principle become most obvious when it is understood that power is transmitted to multiples of radially located pistons through the medium of bearings mounted in parallel on the same crank pin. It can be further appreciated that sliding friction has been virtually eliminated due to the rolling action of the crank pin bearings which are permitted to actuate multiples of pistons without interference to each other due to the speed changes of piston travel that occur from the alternating crank angles when in motion. The new method of drive provides significant merit in the facility to produce compact construction that is comparatively high in performance with minimum horse power driving requirements and wide range of operating speeds.

Proceeding therefore to describe my invention in detail, it will be seen upon reference to the accompanying drawings that I have provided a main body portion ll, cylindrical in configuration and preferably formed by means of casting from one of the aluminium alloys. Inherent in this casting is a radially disposed inlet duct 2 extending from a point 3 radially around the inside of the body 1 to a point 4. Concentrically located inwardly of the inlet duct is a radially located outlet duct 5 extending completely in the form of a circle.

An inlet port 6 extends from the Wall 7 of the body to the inlet duct 2, with an alternatively positioned in let 8 being located diametrically opposite the inletGJ An outlet poit 9 extends through the wall 7 of the body and communicates with the outlet duct '5, it being observed that this port extends through the wall of the body between the two closed ends 3 and 4 of the inlet duct; A further port It) is provided Within the wall 7 of the body diametrically opposite to the outlet port 9, and this port is provided with a pressure relief valve 11 spring-loaded as at 12 and providing communication between the outlet duct and the inlet duct via drilling 11 if a-predetermined pressure is surpassed.

Upon the face 13 of the body portion, and extending through to the outlet duct 5 is a plurality of ports 14. In

this particular embodiment four such ports are indicated,

it being understood that there are four cylinder and piston components collectively designated 35, the construction of which will hereinafter be described.

Also formed within the face 13 of the body portionis a plurality of inlet ports 16, said ports communicating with the aforementioned inlet duct 2. Once again in'this embodiment there are four such ports. Finally, onthe said face 13 of the body portion, is a plurality of transfer passages 17, there being four of said passages one for each cylinder and piston component. Each of these transfer passages consist of an elongated recess formed in the face of the body portion out not communicating with either the inlet duct 2 or the outlet duct 5. a

' to the interior of the cylinder.

cates with achannel 22,formed within the base plate, one end of said channelcommunicating through an outlet port i one another but it will be understood; that ifvnecessary, further pairs could be added as required; providing the.

diametri c angle between each pair was equidistant, thus giving balance to the running of theassernbly.

Each of said cylinder and piston components consist of a base plate 18 having the configuration most clearly shown in Figures 3 and 4, and formed integrally upon this base plate and located substantially centrally is a cylinder 19 closed at the outer end Zilthereofl Within this closed end and adjacent the base plate 18 is amanifoldZl open This manifold communiing, which is situated vertically from the base plate 18,

containsa screw-threaded plug 27- engageable within an aperture 28 at the top of the valve housing, said plug being apertured internally to support and receive the stem 29 of an inlet valve 39, including valve head 31. A spring 32 reactsbetween the plug 27 and the valve head 31, and norrnally maintains the valve head in position-upon seat 33 of an inlet port 34 formed through the base plate 18.

Upon the opposite side of cylinder 19 is:an outlet valve housing 35 similar in construction to the valve housing 26 and containing a plug 36. screw-threadably secured within the top of the housing. An outlet valve 37 similar in construction to.the inlet valve 29 is mounted within the plug 36 and is adapted to normally maintain closed an outlet port 38 formed at the base of the valve housing, it being understood that a similar spring to spring 32 is present, although same is not illustrated in the accompanying drawings.

However, in the case of the outlet valve housing, a further transfer passage 39 is formed integrally within the cylinder and valvehousing component, said transferpassagebeing formed above the base plate and communicating via a drilling 40 to the interior of the valve housing above thevalve head 41. The opposite end 42 of the transfer passage turns downwardly and communicates via a drilling 43 through the base plate 18.

. Each cylinder and piston component is secured to the face 13 of the main body portion bymeans of bolts 44 engaging the body portion, a sealing. gasket 45 being provided to maintain gas-tight inter-facial relationship be tween the base plate and the face. When in position, the inlet port 34 of the cylinder component registers over the inletport 16 in the body portion. The end23 of the channel 22 registers over one end of the transfer passage 17 in the face of the body portion. The'outlet port 46 in the outlet valve housing; communicates over the opposite end of the transfer passage 17; Finally the port 43 of the transfer passage 39 registers over the outlet port 14 in the face of the body portion.

Cylindrical pistons 47 having compression rings 48 thereon, are pin-connected ina conventional. manner to 4 bearing portions 59 of which engage. around .the outer races 56 thereof. In the present embodiment, inasmuch as there are four piston and cylinder components, there are two connecting rods provided situated at right angles to one another, and reference to Figures 10 and 12 will show that the bearing portions 56 thereof cross over one another. In order to provide the necessary clearance the upper connecting rod 49 (with reference to Figure 12) is offset at either end as shown by reference character 49'.

Rotation of the drive shaft 52 by means of a source of power (not illustrated) causes the offset crank pin 54 to rotate, carrying with it the bearings 55 and 55'. As each connecting rod is engaged by aseparate bearing 55, the connecting rod is reciprocatcd with the outer race 56 of the bearing merely rolling across the bearing surfaces 51, thus eliminating entirely sliding friction which would be present if one bearing operated both connecting rods. in this connection .thezbearingportions :50 are of such a size thatthe race 55 or 55 isja clearance fittherewithin.

With this construction and assuming that the pin 54 is rotating: in the direction of arrow 54' 1(Figure 10) it will each end of a connecting rod 49, and it will be observed that the connecting rod 49 is double ended-having a piston on each end. The connecting rod 49. which is solid, is

provided with an open-faced elongated rectangular bearing or yoke 50 medially along the length thereof, said bearing having bearing faces 51 formed thereon. A drive shaft 52 extends centrally through the main body portion or roller bearing race for each connecting rod 49, the

, be noted that as theupper bearing 555 urges'thewupper fconnecting rod .49; from the extreme. left-hand position to theextremeright-hand position, that all the load is exerted between the outer race 56 and the right-hand bearing face 151 and that in the first'ninety degrees of rotation-of pin 54' from leftdead centre the outer race 56 will roll upward against the right-hand bearing face 51 and in the second ninety degrees of rotation of pin 54 the outer race-56 will roll downward against the right-hand bearing face 51 and that as the upper bearingSS' urges the upper connecting rod-49 from the extreme right-hand position to the extreme left-hand positionthat all the load is now exerted between the outer race 56 and the lefthand bearing face 51 and that inthe first ninety degrees of rotation of pin 54 from right-hand dead centre the outer race 56 will roll downward against the leftehand bearing face 51 and the second ninety degrees of rotation of pin 54 the outer race 56 will roll upward against the lefthand bearing face 51. The lower bearing 55 urges the lowerconnecting rod 49-back and forth in a manner similar to that described hereinbefore for the upper components; except that the rotation of the outer race of the lower bearing 55 is always in the opposite direction to the rotation of the outer race 56 of the upper bearing 55 thus illustrating the importance of. an-individual hearing for actuating each set ofopposing pistons arranged in a radial position and operated from the same crank pin.

In the operation of the pump following hereinafter, only one piston and cylinder component will be described, it being understood that the other three act in exactly the same way. Figure 7 shows 'a' schematic layout for the pump 1, and it will be observed that a tank-57 is provided carrying the spray fluid to be pumped. A conduit 58 extends'from the bottom of the tank 57 to the inlet 6 of the pump, and an outlet conduit 59extends from the outlet 9 to a control block 60,whichincludesavalve 61 and pressure gauge 62. When the valve is in one position, fluid is pumped from the itank'through the pump to the control block 60, and thence via conduit '63 to a further control block 64, whence it may be routed via conduit'65 to the spray boomsi (not illustrated).

However, when the 'sprayingcycle is finished,"it is desirable to drain the booms etc., as sornesuch sprays are corrosive in action. Under these circumstances, the valves 61 are changed so that the alternative inlet 8 upon the other side of the pump 1 acts :upon the control block 64 by means of conduit 66 and sucks the remaining fluid back from the booms, through ,the pump l through conduit 59 to control block 60', and thenceback tothe tank via conduit 67.,

As the piston 47 movesawayfrom the head 20 of the cylinder block 19, suction is created in the cylinder which acts via manifold 21 upon"inlet-'valve 29, thus' 'raising same against pressure of sprihg 32. It will be noted also thatthis suction acts on the outlet valve 37 but, due to the arrangement of ports and transfer passages, this suction merely serves to keep the valve head upon the seating. As valve 29 opens, this suction acts through port 34 to port 16 and thence to the inlet conduit 2 and draws fluid from the tank 57 as hereinbefore described.

As the piston rises within the cylinder, pressure is built up within the cylinder which then assists spring 32 in closing the inlet valve 29, thus forcing the fluid via the manifold 21 into the passage 22, and thence through transfer passage 17 to act upon outlet valve 37, which is thus opened against its spring pressure. Still acting under pressure, the fluid fiows through the outlet valve housing 35, through transfer passage 39 and thence through ports 40 and 14 into the outlet conduit 5. As soon as the piston starts to descend again, the outlet valve 37 closes and the cycle re-commences.

From the foregoing, it Will be observed that by the arrangement of porting and transfer passages, both valves are similar in location and operation, and both can readily be removed without dismantling the remainder of the asembly merely by unscrewing plugs 27 and 36. Furthermore, because of the integral porting arrangement of the body portion, there is only one pressure seal needed, namely between the piston and cylinder components and the face of the body portion, and furthermore, said piston and body components are readily removable for repair. Figure 6 shows a hollow cover panel 68 which is adapted to cover the piston and cylinder components when the pump is in operation, in order to prevent the ingress of dirt, dust and the like.

Since various modifications can be made in my invention as hereinabove described, and many apparently widely different embodiments of same made within the spirit and scope of the claims without departing from such spirit and scope, it is intended that all matter contained in the accompanying specification shall be interpreted as illustrative only and not in a limiting sense.

What I claim as my invention is:

1. A fluid pump comprising in combination a main body portion, inlet and outlet ports in said body portion, substantially radially located inlet and outlet ducts formed within said body portion and communicating by one end thereof to said inlet and outlet ports respectively, a plurality of diametrically opposed selectively detachable piston and cylinder components secured to the face of said body portion, centrally located drive means adapted to reciprocate said pistons in said cylinders, each of said piston and cylinder components including a cylinder block, an inlet valve and an outlet valve, one upon each side 6 of said cylinder block, said inlet valve adapted to control communication between said inlet duct and the interior of said cylinder, said outlet valve adapted to control communication between said outlet duct and said cylinder, a manifold formed in the head of said cylinder, said manifold being common to both said inlet and outlet valves, a transfer passage connecting said manifold with said outlet valve, and a further transfer passage connecting said outlet valve to said outlet duct.

2. The device according to claim 1, in which each of said cylinder and piston components includes a base, adapted to be detachably secured to the face of said body portion, said cylinder being formed integrally with said base and lying parallel to said face, said valves extending upwardly at right angles to said face, housings for said valves formed integrally with said cylinder, an inlet valve port in said base upon the underside thereof communieating between said inlet valve housing and said manifold, an outlet port in said base upon the underside thereof communicating between said outlet housing and said manifold, said first-mentioned transfer passage being formed in the face of said body, said last mentioned outlet port and said outlet valve port registering over said passage when said component is in situ, said second mentioned transfer passage being formed integrally with said component and communicating between said outlet valve housing and a port formed in said base plate adapted to communicate with said outlet duct.

3. The device according to claim 2, in which each of said valves is adapted to be removed externally, said means including a screw-threaded, centrally apertured plug adapted to be secured externally into said housing, said valve including a head and a stem, said stem adapted to reciprocate within said plug, and spring means reacting between said head and said plug.

References Cited in the file of this patent UNITED STATES PATENTS 288,007 Calver Nov. 6, 1883 679,876 Blake Aug. 6, 1901 999,220 Harmon Aug. 1, 1911 1,274,955 Sundh Aug. 6, 1918 1,466,230 Johnson Aug. 28, 1923 2,633,082 McFarland Mar. 31, 1953 2,696,788 Funston Dec. 14, 1954 2,736,267 Mosbacher Feb. 28, 1956 FOREIGN PATENTS 747,449 Great Britain Apr. 4, 1956

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