US2048736A - Lubricant pump structure - Google Patents

Description

July 28, 1936.

R. P. ESSER 2,048,736

LUBRICANT PUMP STRUCTURE Flled March 21 1955 4 Sheets-Sheet 1 Jaw/#42 A flu er! 2. fine/ yd/172974,!

yiggw July 28,1936. R. P. ESSER 2948,7336

LUBRICANT PUMP STRUCTURE Filed March 21, 1935 4 Sheets-Sheet"4 p I M a m 4 11M. 7 z 5 W f 2 M 06 4 M w O. HM ,J V M MMMM M 7% Q U! 222 N2 m vuuan wM O H 2 M 1! "V v a; .M M 0 N J 4 .u 2 M l i r A w 4 nflfll wk! 2 w. %4 12 1 o Z Z N Amp W v z W w a w 1 I ll n7 W Mm w w fl b Patented July 1936 amateur r STRUCTE Eupert F. Esser, Bryan, Ohio," assignor to The- Equipment Corporation, Bryan, Ohio, a

corporation oi? Qhio Application ram-tn 21, 1935, s rial No. 12,191

The object of my invention is to provide a lubricant pump structure, which is simple, durable and comparatively inexpensive to manufacture. I

A further object is toprovide a lubricant pump structure adapted for delivery of lubricant at either a high pressure or a low presure as'desired, a single adjustment being necessary for changing from one to the other.

Still a further object is to provide a novel operating means for a high and low pressure lubricant pump, wherein the low pressure pump supplies lubricant to the high pressure pump in such a manner that a minimum ofcompressed air is used for either low or high pressure operation.

Still another object is to provide low and high pressure pistons so associated with each other that the high pressure piston drives the low pressure piston in one direction and the low pressure piston drives the high pressure piston in the opposite direction when lubricant is being discharged at low pressure, while when lubricant is being discharged at high pressure, the high pressure piston is driven by the lubricant pumped by the low pressure piston rather than directly by the low pressure piston itself.

Still a further object is to so associate a control valve with the two pistons that it serves for both during either high pressure or low pressure operation of the pump structure.

Still another object is to provide a check valve connection between the low pressure and high pressure pumps, which is selectively renderable operative or inoperative, so that high pressure or 35 low pressure dispensation of lubricant respectively can be accomplished.

Still another object is to provide a novel type of relief valve to prevent undue pressure in the low pressure pump, this valve being so arranged o that it is responsive to lubricant pressure in proportion tothe pressure of the actuating fluid for the pump structure.

Still another object is to provide a unitary (Cl. 221i) of the invention a pair of control valves, one for the low pressure pump and the other for the high pressure pump, and a manually settable selector for selecting either high pressure or low pressure dispensation from a single nozzle. 5

- over a wheeled platform for supporting a con- 15 tainer of lubricant, the wheels being within the outline of the casing, so that a minimum of floor space is required for the unit.

With these and other 'objects in view, my in vention consists in the construction, arrangement 20 and combination of, the various parts of my lubriv cant pump structure, whereby the objects contemplated are attained, as hereinafter more fully set forth, pointed out in my claims, and illustrated in the accompanying drawings, in which: 25

Figure 1 is a side elevation, mostly in section, of a lubricant pump structure embodying my 121- vention and showing it associated with a lubricant barrel, a high pressure lubricant line and control valve being illustrated in connection Figure 2 is a sectional view on the line 2-2 of Figure 1.

Figure 3 is a sectional view on the line 3-8 of Figure 1, and showinga low pressure delivery hose and control valve associated therewith.

Figure 4 is an enlarged sectional view on the line H of Figure 2. t

Figure 5 is a side elevation of another form of the invention utilizing a single dispensing hose instead of oneforlow pressure and one for high pressure.

Figures 6 and 7 are enlarged, sectional views on the lines H and ll of Figure'5.

Figure 6A is a sectional view on the line @A$A of Figure 6, showing a selector control in another position.

Figure 8 is a. sectional view on the line 8-8 of Figure 6, showing the control valves for the low and high pressure pumps.

. Figure 9 is a sectional view on the line 9-9 of Figure 6; and

Figure 10 is a sectional view on the line lt-lt of Figure 9.

In the accompanying drawings, I have used 55 therewith.- l

the reference numeral I to indicate a container for lubricant or the like, which is usually in the form of an oil barrel. The upper end thereof is open, the container being shown with a neck I2, although my device may be used with a barrel having an opening of but slightly larger diameter than a foot valve fitting shown at I4. The foot valve fitting I4 is mounted on the'lower end of a low pressure cylinder I6.

Within the cylinder. I6, a piston rod I8 is arranged, having secured to the lower end thereof a piston consisting of parts 20, 22 and 24.

The part 20 is a washer-like element secured to the lower end of the rod I8 and the part 22 is also a washer-like element secured by a cap screw 26 to the element 20 with the element 24 (a cup leather) interposed between them. The elements 20 and 22 are perforated and a check valve disc 28 rests against the upper face of the element 20, it being retained thereagainst by a spring 30.

The foot valve fitting I4 has therein an intake check valve 82, the disc 28 being a discharge check valve.

From the description of the parts thus far made, it is obvious that vertical reciprocation of the piston with its cup leather 24 in the cylinder I6 will upon the down stroke. cause the valve 28 to open, and upon the up stroke cause the valve 32 toopen, whereby upon a plurality of reciprocations, lubricant is caused to rise in the cylinder I6.

The rising lubricant enters a passageway 34 from which it flows into a bore 36. From the bore 36, it fiows through perforations 38 of a sleeve 40 and into a bore 4201. the sleeve.

A low-pressure hose 44 is connected with the sleeve 40 and terminates in a control valve 46 and a discharge nozzle 48.

A check valve 60 is associated with the sleeve 40 and normally retained seated-by a spring 62.

The spring 52 and the check valve60 are rendered operative in the position shown in Figure 3, althoughthey can be rendered inoperative by unscrewing a screw 54 to the inner end of which a plug 56 is secured. When this plug is turned outwardly, so that it seats against the inner end of a closure nut 68, the check valve 60 can no longer function.

The discharge side of the check valve 60 is connected by a passageway 60 to a high pressure cylinder 62. A high pressure plunger 64 is reciprocable therein. a

The high pressure cylinder 62 has a discharge passageway 66 connected with adischarge fitting 68.

A ball check valve 10 is arranged in the fitting 68 and serves as an outlet check valve for the high pressure lubricant from the cylinder 62.

A swivel fitting 12 is connected with the fitting 68 and by a high pressure hose 14 with a control valve 16. The control valve has a discharge fitmember 84 ofthe cylinders 84 and 86. This basemember is mounted on a base plate 96, which is supported on the barrel or other container I0.

The cylinders 84 and 86 are provided with suitable cylinder heads 88 and I00, while the pistons 80 and 82 are provided with piston rods I02 and I04.

' A control valve is provided for admitting compressed air to the upperends of the cylinders 84 and 86 and exhausting air therefrom. It is shown best in Figure 4 and comprises an intake valve seat I06, an outlet valve seat I08 in the form of a washer of fiber or the like, and a valve plug H0. The valve plug IIO has an intake end II2, engageable with the seat I06, arid an exhaust end H4 engageable with the seat I08. 15

Compressed air is supplied from the chamber 80 through a pipe -I I6 to the valve seat I06. Air is exhausted from the valve seat I08, through exhaust ports H8. The control valve body (between the seats I06. and I08) is connected by passageways I20 with hollow mounting bolts I22, which in turn communicate with passageways I 24 leading to the upper ends of the cylinders 84 and 86.

The valve plug H0 is operable to its opposite 25 positions by a snap acting toggle lever I26, with which an over-center spring I28 is associated. The toggle lever I26 is initially moved by either a shoulder I30 or a shoulder I32 of a valve rod I34. The rod I34 is connected with a cross piece I36 30 having one end rigidly connected with the piston rod I04 as by being confined between a shoulder I38 and a lock nut I40. Its opposite end is freely movable along the rod I02, the rod having .a

Cal

tion relative thereto.

In Figures 6 to 10, I show a modified construction in which there is a foot valve I54 on the lower end of a low pressure grease cylinder I56. A piston I58 is reciprocably mounted within a cylinder I 60 and is connected by a plunger I62 and a stem I64 with a low pressure grease piston I66. A check valve I68 is mounted in the piston I68.

Air and grease packings I10 and I12 are provided for the cylinder I56. Compressed air constantly acts on the under side of the piston I58, it being introduced through a supply pipe I14 into a chamber I16.

A high pressure pump is provided in the form of a cylinder I84 and a plunger I96. The cylinder I 84 communicates by means of passageways I88 and 200 with the low-pressure cylinder I 56' (see Figure 10). A check valve 202 is interposed between a hollow fitting 204 and the high pres- 5:

sure cylinder I 84, the check valve 202 seating against its inner end. The interior of the fitting 204 communicates by means of an opening 206 with the passageway 200.

An outlet check valve 208 (see Figure 9) com- (3:) municates with the cylinder I94 and a lubricant delivery hose 2| 0 is connected therewith, a noz-- zle being mounted on the outer end of the hose as shown forinstance in Figure 1.

For reciprocating the plunger I86, I provide a C3 piston 2l2 reciprocable in a cylinder 2.

Communicating with the chamber I 16 is a hollow cap screw I18 for retaining a control valve body- I80 in position as shown in Figure 6. A second cap screw I82 is also used for retaining 7:) the valve body I80 in position. The hollow cap screw I18 afi'ords communication between the chamber I16 and a valve seat I 84 in the valve body I 80. A valve member I86 is adapted for seating against the seat I84 and when unseated therefrom as shown in Figure 6 permits the compressed air to flow through a passageway I88 and a tubular rod I90 to a normally closed control valve I92.

For opening the valve I92, I provide a cam disc 2I6 pivoted on a sleeve 2I8 held in position under a nut 220 on a tie rod 222. The cam disc 2I8 has a wing like handle 224 and a depression shown at 226 to receive a pin 228 when the depresion registers therewith. The pin 228 when pressed downwardly opens the valve I92 and is sealed relative thereto by a flexiblediaphragm 230.

As shown in Figure. 6A when the wing 22% is swung in either direction from a central position where the depression 226 does not register with the pin 228,- the pin will be depressed for opening the valve. Instead of the construction just described, the wing 224 may have but two positions, the left position for instance with the valve I92 closed and the right position causing the valve to be open for high pressure operation.

When the valve i92 is open, air can flow from the tubular rod 590 through a passageway 232 to/the upper end of the cylinder 2M. The valve member itt when unseatedfrom the seat I86 is seated against a seat 236 of suitable material, and when unseated from this seat and seated against the seat ass, air can flow from the cylinder 2&8 through the parts 232, m2, N and H88, past theseat 236 to atmosphere through passages 23$, for thus exhausting the air from the cylinder 2%. The valve plug B85 is operated to its opposite positions by a toggle lever 238, which in turn is operated by shoulders 2&0 and 2&2 of a reciprocable rod 2%. The rod 265 is connected with the piston 2i2 (see Figure 8).

The parts are to 990 and 235 to 26% are for the'high presure pump. Similar parts are.pro-' vided for the low pressure pump and are given the same reference numerals with the addition of GIG".

As shown in Figure 7, the tubular rod 890a communicates directly through a passageway 2 36 with the cylinder itil. Since the lower side of the piston 558 is subjectedto air pressure, I provide a seal as at 288 to prevent leakage around the rod Edda.

Practical operation for low pressure delivery of grease being in the position shown inFigure s will admit air to the upper ends of the cylinders 8% and 88. This air in the cylinder 86 will counterbalance the air in the chamber 90, while in the cylinder 3t, it will force the piston 82 and the plunger b8 downwardly. This will tend to pump grease through the cylinder 62 past the check valve 56 and into the hose 55, until the arm W6 engages the shoulder M2, whereafter the piston 88 and the low pressure piston 25 will be driven downwardly.

At the lower end of the stroke, the position of the valve lit will change, whereupon air is exhausted from the upper ends of the cylinders as and 88, and the air pressure in the chamber at will then raise the piston 80 and through the cross be! iSBthe piston 82. This will cause the low premure pump piston 24 to pump grease into the hose Q4.

At the upper end of the stroke, the position of the valve 0 will again change and as long as the valve 86 is held open,-simultaneous reciprocation oi the pistons will continue.

Referring to Figures 6 to 10, air pressure within the chamber I16 tends constantly to raise the piston I58 for drawing grease in through the foot valve I54.

For low pressure operation, the wing 224 is adjusted, to the position shown in Figure 6, so that air can not flow past the valve I82 into the high pressure pump cylinder. 7 When how of grease is permitted by opening .the nozzle-on the outer end 01' the hose 2H! and the valve of the valve body I80a is in the position 5 mitting the piston its to move downwardly through the grease in the cylinder lit, the foot valve 85% also being closed. At the lower end of the strolre, the position. of the valve V will be changed tln'ough the rod 246a and the toggle lever mechanism 238a, so that the air will be exhausted from the cylinder 860 to atmosphere through the ports 238a.

Reciprocation of the low pressure pump piston i as will continue until the nozzle on the end of the hose 2th is closed, whereupon the back pressure will stop operation of the low pressure pump. During low pressure operation, the plunger i9$ is held in its upper position by lubricant in the cylinder 6%,- so that the plunger does not interfere with the lubricant flowing at low pressure through the cylinder.

During reciprocation, displacement of air between the packings H0 and H2 is taken care of bus passageway 25@ shown in Figure 10 and indicated by dotted lines in Figure 9. This passageway communicates at its lower end with the atmospheric space within a chamber 252 depending from the base of the cylinders ibii and 29%.

Practical operation for high pressure delivery of grease Referring to Figures 1 to 4, the check valve E0 is adjusted to the position of Figure 3 and the control valve i6 is used. I

Assuming the parts to be in the positions shown '55 in Figures 1, 2 and 4, when the valve 56 is opened, the compressed air in the upper ends of the cylinder db will cause the plunger 6A to move downthrough the check valve in and into the hose it.

when the cross arm E36 engages the shoulder N2 of the piston rod .802 in addition to pumping the lubricant out at high pressure, the pump piston 243 will be driven downwardly for i take of lubricant into the cylinder it above the piston 2s.

' en the position of the valve I it changes, air pressure in the chamber 90 will raise the pump piston 2t for causing upward flow of lubricant in the cylinder it and through the check valve 50 into the high pressure cylinder 62.

Since the area of the piston 2c is greater than that of the plunger 56. the plunger will be driven the piston 24, causing the arm I66 to leave the shoulder 142, as shown in Figure 1. According- In the event that during high pressure delivery,

foreign matter gets under the check valve 69, there will be danger of the high pressure lubricant acting upon, the low pressure hose and damaging it. To take care of such a contingency, I have provided a relief valve shown in Figure 3, having a cup leather I, responsive to the pressure in the chamber 99, and a plunger pin I66 responsive to the pressure in the passageway. A passageway I68 is provided for. this purpose.

Whenever the pressure of the grease exceeds a certain proportional relation to the pressure of the compressed air, the plunger I66 will be driven inwardly far enough to permit the excess lubricant to pass through ports I60 into the space in the base 94 and fall back into the container I6.

By utilizing air pressure to constrain the relief" valve toward closed position instead of a spring,

.the relief pressure of the lubricant is in exact proportion to the pressure of the actuating fluid.

Referring to Figures 6 to 10 for high pressure I operation, the wing 224 is turned so that the cam 2l6depresses the pin 228 for opening the valve 292 and opening the check valve 208 and forcing the lubricant through the hose 2H! through the nozzle at high pressure whenever the nozzle is opened.

At the lower end of the stroke of the piston 2I2,

the high pressure control valve (indicated generally by the reference character V in Figure 8) will be changed in position so as to exhaust the air from the cylinder 2M. The low pressure pis-- ton I66 can then move upwardly for forcing another charge of lubricant through the check valve 202 intothe cylinder I94 and thereby causing the plunger I96 to move upwardly at a more rapid rate than the movement of the piston I66 because of the relative areas. For instance the piston I66 might 'move about 5th of its stroke for efiecting a full stroke upward movement of the plunger I96. I

When the piston 2I2 reaches its upward limit of movement the valve V' will again be changed in position for starting the down stroke, and this cycle will be repeated a number. of times, while the piston I66 is moving upwardly. When the piston I66 finally reaches its upward limit of movement, it will again move downwardly and then move up again in steps as long as the high pressure pump is being used.

In the event that there are air pockets in the grease, ,these can be taken care of through a relief valve I62 shown in Figure 1 or a similar valve I62 shown in Figure 9.

In Figure 9, I have shown the passageway 264 through which the'grease can flow after the air pocket has been eliminated back into the chamber 262 and find its way back into the grease drum IIIa, instead of being discharged to atmos: phere as in Figure l.

After the air pockets are eliminated, the pump is properly primed, so that it can work in the manner intended for either low or high pressure dispensation of lubricant.

The pump shown in FiguresB to 10 is mean on a flared base member 266 secured to the upper .end of an encasing member 266. The member 266 is preferably mounted on a wheeled platform 269 having-pastor wheels 262 for convenience in wheelingthe pump structure from one positlon to another about the service station.

Lugs 266 serve to limit the downward movement of the casing 266 relative to the platform, 260' for predetermining the position of the foot valve I66 relative to the bottom of the drum Inc which rests on the platform.

Also the lower end of the casing259 is consid-- erablybelow the foot valve I64, so that when the casing is removed from its position surrounding the grease drum and set on the floor, dirt and other foreign matter from the floor does not get into the foot valve.

Suitable latches of the leaf spring type shown at 266 can be provided, if found necessary, to prevent undesired disconnection of the casing 269 from the platform 260. These are conveniently retracted by knobs 268 when it is desired to remove the casing 269 from the platform 260. p

The wheels 262, it will be noted, are within the outline of the casing 269. This makes a unit, the outline of which is defined by the casing and the casing is preferably of square shape with rounded comers, so that a minimum of door space must be provided for a plurality of lubricant pump structures. This makes it possible for a plurality of the casings to be positioned compactly along the wall in a service station without taking upprohibitive floorspace, and such an arrangement presents a very neat appearance for the station.

Changes may be made in'the construction and arrangement of the various parts of my lubricant pump structure, without departing from the real spirit and purpose of my invention, and it is my intention to cover by my claims, any modified forms of structure or use of mechanical equivalents, which may be reasonably included within their scope.

I claim as-my invention:

1. In a lubricant pump structure, a low pressure high volume pump, a high pressure low volume pump receiving lubricant from said low pressure pump, a first power piston connected with said low pressure pump for discharging lubricant therefrom, a second power piston connected with said high pressure pump for discharging lubricant therefrom and an operative connection between said pistons, whereby each will cause intake of lubricant into the pump of the other piston.

v 2. In a lubricant pump structure, a low pressure high volume pump, a high pressure low volume pump receiving lubricant from said low pressure pump, a first power piston connected with said low pressure pump for discharging lubricant therefrom, a second power piston connected with said high pressure pump for discharging lubricant therefrom and a lost motion operative connection between said pistons, whereby each will cause intake of lubricant into the pump of the other piston, and lubricant from said low pressure pump can act upon said high pressure pump to cause movement of said second piston independent of said first piston, such movement being permitted by said lost motion connection.

3. In a lubricant pump structure, a low pressure high volume pump, a high pressure low volume pump receiving lubricant from said low pressure pump, a first power piston connected with said low pressure pump for discharging lubricant therefrom, a second power piston connected with said high pressure pump for discharging lubricant therefrom, an operative connection between said pistons, whereby each will cause intake of lubricant into the'pump of the other piston, and a check valve between said low and high pressure pumps and opening toward the high pressure one.

4. In a lubricant pump structure, a low pressure high volume pump, a high pressure low volume pump receiving lubricant from said low pressure pump, a first power piston connected with said low pressure pump for discharging lubricant thereirom, a second power piston connected with said high pressure pump for discharging lubricant therefrom, a lost motion operative connection between said pistons, whereby each will cause intake of lubricant into the pump of the other piston and lubricant from said low pressure pump can act upon said high pressure pump to cause movement of said second piston independent of said first piston, such movement being permitted by said lost motion connection, a check valve between said low and high pressure pumps and opening toward the high pressure one, and means for selectively rendering said check valve operable for high pressure delivery of lubricant from said high pressure pump or inoperative, for low pressure delivery of lubricant from said low pressure pump.

5. In a lubricant pump structure, a low pres= sure high volume pump, a high pressure low volume pump receiving lubricant from said low pressure pump, a first power piston connected with said low pressure pump for discharging lubricant therefrom, a second power piston connected with said high pressure pump for discharging lubricant therefrom, an operative connection between said pistons, whereby each will cause intake of lubricant into the pump oi the other piston, and an actuating fluid valve for admitting actuating-fluid to and exhausting it from said pistons.

6. In a lubricant pump structure, a low pressure high volume pump, a high pressure low volume pump receiving lubricant from said low pressure pump, a first power piston connected with said low pressure pump for discharging lubricant therefrom, a second power'piston connected with said high pressure pumpfor discharging lubricant therefrom, a lost motion operative connection between said pistons, whereby each will cause intake of lubricant into the pump of the other piston, and lubricant from said low pressure pump can act upon said high pressure pump to cause movement of said second piston independent of said first piston, such movement being permitted by said lost motion connection, and an actuating fiuid valve for admitting actuating fluid to and exhausting i" from said pistons.

'7. In a lubricant pump structure, a low pressure high volume pump, a high pressure low volume pump receiving lubricant from said low pressure pump, a first power piston connected with. said low pressure pump for discharging lubricant therefrom, a second power piston connected with said high pressure pump for discharging lubricant nd means, an operative but lost motion connectherefrom', fluid pressure tending constantly to reciprocate said first piston, said low pressure pump being associated with said high pressure pump so that lubricant from said low pressure pump can act upon said high pressure pump to cause move- 5 mentof said second piston in one direction, fluid pressure for moving said second piston in the opposite direction, and means for selectively rendering said high pressure pump responsive or non-responsive to said fiuid pressure. said low pressure high volume pump delivering low pressure high volume lubricant when said means renders said high pressure pump non-responsive.

8. In a lubricant pump structure, a low pressure high volume pump, a high pressure low volume pump receiving lubricant from said low pressure pump, a first power piston connected with said low pressure pump for discharging lubricant therefrom,'.a second power piston connected with said high pressure pump for discharging lubrlcant therefrom, an'operative connection between said pistons, whereby each will cause intake of lubricant into the pump of the other piston, actuating fluid acting constantly on said first piston in a discharging direction, and an actuating fiuid'control valve for admitting actuating fluid to counterbalance said constantly acting fluid pressure to permit the second piston to move in a direction for intake of lubricant into said high volume pump, said valve being operable to also exhaust fluid from said first piston and simultaneously therewith exhaust actuating fluid from said second piston and to introduce actu ating fluid thereto to move it in a direction for discharge of lubricant from said low volume pump when actuating fluid is being introduced to said first piston.

9. In a lubricant pump structure, low and h pressure pumps, said high pressure pump receiving lubricant from said low pressure pump, a first means for operating said low pressure pump, a

second means for operating said high pressure permitting si'lch movement.

10. In a lubricant pump structure, low and high pressure pumps, said high pressure pump receiv ing lubricant from said low pressure pump, a first means for operating said low pressure pump, a second means for operating said high pressure pump, a controller for first and second means, said controller operated by. movement oi the section between said first and second means, low pressure lubricant flowing from said low pressure pump acting upon said high pressure pump to cause movement thereof at a greater speed than said first means, said lost motion connection per- -mitting such movement, and a check valve between said low and high pressure pumps and opening toward the high pressure one.

11. In a lubricant pump structure, low and high pressure pumps, said high pressure pump receiving lubricant from said low pressure pump,

a first'means for operating said low pressure pump, a second means for operating said high pressure pump, a controller for said means, said controller being responsive to movement of the 7 cant from said low pressure pump acting upon said high pressure pump to cause movement thereof and of said second means, at a greater speed than said first means, said lost motion connection permitting such movement, and acheclr valve between said low and high pressure pumps for opening toward the high pressure one, said check valve being selectively renderable operative or inoperative for high orlow pressure delivery respectively. I

12. In a lubricant pump structure, lowand high pressure pumps, said high pressure pump receiving lubricant, from said low presure pump, a first means for operating said low pressure pump, a second means for operating said high pressure pump through part of a cycle of operation, a pair of controllers, one for each of said means, said controllers being responsive to movement of the first and second means, said low pressure pump being operable to cause completion of the cycle of operation of said high pressure pump, said first and second means being operable-by flow of compressed air thereto and therefrom, and snap acting valves for controlling the flow of compressed air to and from said first and second means.

13. In a lubricant pumping structure, low and high pressure pumps, said high pressure pump receiving lubricant from said low pressure pump, a first means for operating said low pressure pump, a second means for operating said high pressure pump through part of a cycle 01 operation, a pair oi, controls, one for each of said means, said controls being responsive to movement of the first and second means, said low pressure pump being operable to cause completion of the cycle of operation of said high pressure pump to cause movement thereof in one direction, compressed air means to cause return movement thereof and a controller for said compressed air means responsive to movement of said high pressure pump.

a 14. In a lubricant pump structure, low and high pressure pumps, the intake of said high pressure pump being connected with the outlet of said low pressure pump, a first means for operating said low pressure pump, a second means for operating said high pressure pump, a controller for said means, said controller being operable by movement of the second means, an operative but lost motion connection between said means, said low pressure pump being operable to cause movement of said high pressure pump and said second means at a greater speed than it would otherwise be operated by said controller, said lost motion connection permitting 6 such movement, said means being operated, and

a relief valve for said low pressure pump, normally retained seated by the compressed air for operating said means.

pressure pump. a first piston for discharging lubricant from said low pressure pump, a second piston for discharging lubricant from said high pressure pump, fluid pressure and control means therefor responsive to the movement 01 said first piston for causing the fluid pressure s to tend constantly to reciprocate said first piston, the discharge of said low pressure pump be-, ing connected with the intake of said high pressure pump so that lubricant from said low pressure pump can act upon said high pressure pump to cause movement of said second piston in one direction, said second piston being movable in the opposite direction by fluid pressure, means for selectively rendering said. high pressure pump responsive or non-responsive to said fluid pressure, and a fluid pressure valve for each piston operable by reciprocating movement thereof.

17. In a lubricant pump structure, low and high pressure pumps, said high pressure pump receiving lubricant from said low pressure pump, a first means for operating said low pressure pump, a second means for operating said high pressure pump through part of a cycle of operation, a pair of controllers, onefor each of said means, said controllers being operable by movement of the first and second means, said low pressure pump being operable to operate said high pressure pump through the remaining part of said cycle of operation.

18. In a lubricant pump structure, low and 30 high pressure pumps, said lhigh pressure pump receiving lubricant from said low pressure pump, a first means for operating said low pressure pump, a second means for operating said high pressure pump through part of a cycle of operation, a pair of controllers, one for each of said means, said controllers being responsive to movement of the first and second means, said low pressure pump being operable to operate said high pressure pump through the remaining part of said cycle of operation, and selective means to render said second means inoperative.

19. In a lubricant pump structure, a reciprocating high volume pump, a reciprocating low volume pump receiving lubricant therefrom, means for reciprocating said high volume pump comprising a cylinder, a piston reciprocable therein and meansresponsive to the reciprocatioris of said piston to control the flow of a fluidpressure to and from said cylinder, the outlet of said high volume pump being connected with the intake of said low volume pump, said high volume pump constituting hydraulic means to rerection and to control the flow of a fluid pressure 65 from said second cylinder to permit said second piston to be reciprocated in said one direction by said hydraulic means.

20. In a lubricant pump structure, a low pressure high volume pump, a high pressure low volume pump receiving lubricant from said low pressure pump, afirst power piston connected with said low pressure pump for discharging lubricant therefrom, a second power piston con- 75 21. In a lubricant pump structure; low and highpressure pumps, a first means for operating said low pressure pump in both directions, a second means for operating said high pressure pump in one direction only, the outlet of said low pressure pump being connected with the intake of said high pressure pump, said low pressure pump expelling lubricant into said high pressure pump to cause movement thereof in the opposite direction, said first and second means being air operated and a snap acting valve for controlling the flow of compressed air to and from each or said means. said valves being operable to their opposite positions by movement 01' said first and second means. i

22. In a lubricant pump structure, a low pressure high volume reciprocating pump, a high pressure low volume reciprocating pump, a first power piston for reciprocating said low pressure pump, a second power piston Ior reciproeating said high pressure pump, the outlet oi said low pressure pump being connected with the intake-of said high pressure pump, said low pressure pump constituting hydraulic means to move said high pressure pump and said second piston in one direction and to charge said high pressure pump with lubricant, a, check. valve between said low and high pressure pumps and opening toward the high pressure one, means tending constantly to move said first piston in one direction and actuating fluid valve means for admitting actuating fluid to and exhausting it from one side only of said pistons.

23. In a lubricant pump structure, a low pressure high volume reciprocating pump, a high pressure low volume reciprocating pump, a first power piston for reciprocating said low pressure pump, a second power piston for reciprocating said high pressure pump, the outlet of said low pressure pump being connected with the intake of said high pressure pump, a check valve between said low and high pressure pumps and opening toward the high pressure one, means for selectively rendering said check valve operable for high pressure delivery of lubricant from said high pressure pumpor inoperative, said high pressure pump, on the discharge stroke thereof, returning lubricant through said check valve when inoperative toward said low pressure pump and actuating fluid valve means for admitting actuating fluid to and exhausting it from said pistons.

24. In a lubricant pump structure. a low pressure high volume reciprocating pump, a high pressure low volume reciprocating pump, a first power piston for reciprocating said low pressure pump, a second power piston for reciprocating said high pressure pump, the outlet of said low pressure pump being connected with the intake of said high pressure pump, lubricant pumped from said low pressure pump into said high pressure pump causing movement of said second piston in one direction, a check valve between said low and high pressurepumps and opening toward the high pressure one, actuating fluid valve meansfor admitting actuating fluid to and exhausting it from said first piston and for admitting actuating fluid to and exhausting it from said second piston and a control valve for shutting off the actuatingfluidto said second piston to thereby render it inoperative and permit low pressure lubricant to pass through said high pressure pump.

25. In a lubricant pump structure, a'lowpressure pump, a high pressure pump, the outlet of said low pressure pump being connected with the intake of said high pressure pump, fluid pressure means for reciprocating said low pressure pump,

ciprocated-in one direction by low pressure lubricant thereagainst" from said low pressure pump, fluid pressure means for reciprocating said high pressure pump in the opposite direction only and a control valve operableto cut off the fluid pressure from said highcpressure pump whereupon the low pressure lubricant from said low pressure pump passes through said high pressure pump.

26. In a lubricant pump structure, a low pres:

sure pump, a high pressure pump, the outlet of said low pressure pump being connected with the intake of said high pressure pump, fluid pressure means for reciprocating said low pressure pump,

said high pressure pump including a plunger reciprocated in one direction by low pressure 111- bricant thereagainst fro-m said low pressure pump, fluid pressure means for reciprocating said high pressure pump in the opposite direction only anda control valve operable to cut oii the fluid pressure from said high pressure pump whereupon the low pressure lubricant from said low pressure pump passes through said high pres= sure pump, a high pressure pump, the outlet of said low pressure pump being connected with the intake of said high pressure pump, a discharge hose connected with the outlet of said high pressure pump for discharging either low or high pressure lubricant, fluid pressure means for reciprocating said low pressure.pump,- said high pressure pump having an expansible chamber, said highpressure pump being reciprocated in one direction by pumping low pressurelubricant thereinto, said low pressure pump being connected therewith to pump low pressure lubricant thereinto, fluid pressure means for reciprocating said high pressure pump in the opposite direction only and a control valve operable to cut ofl the fluid pressure from said high pressure pump low pressure pump passes through said high pressure pump and is discharged from said discharge hose.

28. In a lubricant pump structure, a low prespump for discharging lubricant therefrom, second power piston connected with said puriip plunger for discharging'lubricant therefrom, fluid,

pressure tending constantly to move said first whereupon the low pressure lubricant from said 15. said high pressure pump including a plunger repiston in one direction, fluid pressure for moving said first piston in the opposite direction, a con trol valve operated by movement of said first piston to alternately cause introduction of fluid pressure for moving said first piston in said op- Y volume lubricant when said means renders said high pressure pump non-responsive.

29. In a lubricant pump structure, a low pressure pump, a high pressure pump, a discharge hose connected with the outlet of said high pressure pump, the outlet of said low pressure pump being connected with the intake of said high pressure pump, means for operating said low pressure pump comprising a cylinder, a piston therein, one side of said piston being constantly subjected to fluid pressure, means for alternately admitting and exhausting fluid pressure with respect to the other side only of said piston in response to movement of the piston, means for operating said high pressure pump comprising a the side only or said second piston which causes it to move in a direction for discharging lubricant from said high pressure pump and exhausting fluid pressure therefrom in response to move-' low pressure pump moving said high pressure pump in the opposite direction when said last 30. In a lubricant pump structure, a low pres- 1o sure pump, a high pressure pump, a discharge hose connected withv the outlet of said high pressure pump, the outletoi said low pressure pump being connected'yith the intake of said high pressure pump, means for operating said low 15 pressure pump comprising a cylinder, a piston therein, one side of said piston being'constantly subjected to fluid pressure, means for alternately admitting and exhausting fluid pressure with respectto the other side of said piston in response 20 to movem nt of the piston,-means for operating said high pressure pump comprising a second cylinder, a second piston therein and means for alternately admitting fluid pressure to the side of said second piston which causes it to move in 25 a direction for discharging lubricant from said high pressure pump and exhausting fluid pressure therefrom in response to movement of said second piston and a valve for cutting 01! fluid pressure from said second cylinder, lubricant at low'ao pressure from said low pressure pump passing through said high pressure pump and discharging from said nomle when said valve cuts 03 fluid pressure from said second cylinder.

RUPERT P. ESSER. 35

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