US2816515A - Pumps - Google Patents

Description

Bed, 1957 A. SENKOWSKI ETAL PUMPS 3 Sheets-Sheet 1 Filed May 14, 1953 INVENTORS. V ALEXANDER SENKOWSK 8i FREDERICK D. COOPER by 642...,

Dec. 17, 1957 A. SENKOWSKI ETAL PUMPS Filed May 14, 1953 3 Sheets-Sheet 3' INVENTO ALEXANDER SENKOW a BY FREDERICK D. COOPER ATTOR/VEKS.

PUMPS Alexander Senkowski, Earlsdon, Coventry, and Frederick D. Cooper, Stoke, Coventry, England, assignors to Massey-Harris-Ferguson (Sales) Limited, a British comn y Application May 14, 1953, Serial No. 354,905

Claims priority, application Great Britain May 16, 1952 9 Claims. (Cl. 103-169) The invention relates to improvements in pumps and more particularly to piston-type pumps foruse in tractor power lift systems operating in accordance with the principles taught in the Ferguson Patent No. 2,118,180 issued May 24, 1938.

One object of the invention is to provide in a pump of the above general character improved mechanism for imparting reciprocatory mot-ion to the pump piston or pistons from a rotary driving shaft.

A more specific object is to provide improved mechanism for reciprocating a pump piston through the medium of a crosshead fixed on the piston and having a connection with a follower rotatably mounted on. an eccentric on a rotatable shaft whereby positive movements are imparted to the piston in both directions while lateral stresses on the parts are reduced to a minimum Another object is to provide a pumpv construction in which the pump cylinders and driving shaft are interrelated so as to reduce the bending moment on the mechanisms connecting the pistons with the: shaft in the stroke range in which such bending moments are ordinarily at their maximum.

Still another object is to provide a pump wherein the components are arranged and. interrelated so that the cylinder bores and connecting passages can. all be formed in the pump body by simple drilling operations with a resultant simplification of manufacture and substantial reduction in cost.

A further object is to provide improved means for efficiently and positively lubricating the moving parts of the pump.

It is also an object of the invention to provide a pump which is simple in construction and extremely rugged and dependable, which has ample capacity to meet the requirements of a tractor hydraulic lift system and which is sufficiently compact and appropriately shaped to find ready accommodation within the tractor body.

Other objects and advantages of the invention will become apparent from the following detailed description of the preferred embodiment illustrated in the accompanying drawings in which:

Figure 1 is a side elevational view ofa pump and control valve assembly embodying the features of the inven tion with parts broken away to show details of construction.

Fig. 2 is a transverse sectional view through the pump taken in a vertical plane substantially on the line 2-2 of Fig. l.

Fig. 3 is a sectional view taken in a plane substantially on the line 3-3 of Fig. 2..

Fig. 4 is a sectional view through the control valve mechanism taken in a vertical plane-substantially on the line 4-4 of Fig. 1.

Fig. 5 is a fragmentary sectional view taken through the valve mechanism and pump body substantially on the line 5-5 of Fig. 1.

Fig. 6 is a sectional view through the pump body taken in a vertical plane substantially on the line 6-6 of Fig. 1.

nited States Patent 0 Fig. 7 is a fragmentary sectional view taken in a vertical plane substantially on the line 77 of Fig. 1.

Fig. 8 is a fragmentary sectional view taken in a horizontal plane substantially on the line 8-8 of Fig. 1.

Fig. 9 is a fragmentary sectional viewtaken in a horizontal plane substantially on the line 9-9 of Fig. 1-.

While we have shown and will herein describe the invention as embodied in a particular form of pump, it is to be understood that this detailed disclosure isnot in-' tended to limit the invention but merely to illustrate what is now believed to be its preferred form and that it is our intention to cover all modifications and alternative constructions falling withinthe spirit and scope of the invention as expressed in the appended claims;

For purposes of illustration, the invention has been shown as embodied in a pump particularly suitable for use in a tractor hydraulic lift system of the same general type as that employed in the Ferguson tractor. The exemplary pump, by reason of its size, shape and capacity, is especially well suited for use in the tractor disclosed in the co-pending application of Alexander Senkowski and Arthur E. Lynes, Serial No. 354,904, filed May 14, 1953-, and finds ready accommodation within the body of such tractor.

In general, the exemplary pump has a body 10 formed with a plurality of main cylinder bores 11 each having a piston 12 reciprocable therein. Reciprocation of the pistons in the cylinders is efiected through the medium of a shaft 13 extending across the upper ends of the cylinders and rotatably supported at opposite ends by bearings carried on the upper end of the pump body. Driving mechanisms 15 of novel and advantageous construction, described in detail hereinafter, operatively connect the shaft 13 with the respective pistons 12. The pump body 10 is formed with suitable passages and valves accommodating fluid flow to and from the cylinders 11 in the operation of the pump.

A housing 16 attached to one end of the pump body and forming therewith a unitary structure, encloses control valve mechanism for controlling the operation of the pump. More particularly, the control valve mechanism is associated with the pump intake and pump operation is started or stopped by opening or closing the intake, as taught in the Ferguson patent above referred to.

An auxiliary pumping device 17 provided in the pump body acts to supply oil under pressure to certain moving parts of the pump for lubrication so that the pump may be operated dry, that is, without being submerged in a body of oil.

In accordance with the invention, the pump body 10 and other components of the pump are constructed and arranged to afford compactness and to-simplify manufacture and assembly. As shown in Figs. 1, 2 and 5 of the drawings, the pump body comprises an elongated flat and relatively narrow intermediate section 20 disposed generally vertically and having a generally horizontal section 21 extending rearwardly therefrom somewhat above its lower end. An integral depending flange or skirt 22 supports and reinforces the outer end of the section 21. The intermediate and horizontal sections 20 and 21 are preferably formed as integral parts of a unitary casting and have formed integrally therewith upright end sections 25 and 26 of somewhat greater width and extending above the intermediate section.

The end sections 25 and 26' of thepump body cooperate with bearing blocks 27 to rotatably support the shaft 13. As shown in Fig. 6, the blocks 27 are removably secured to the upper ends of the end sections by screws 28 and the blocks and adjacent portions of such end sections are formed to provide recesses for bearings 29 journaling the shaft 13 at opposite ends. One of the end sections, in this instance, the section 26, has a fiat pad 30 machined on its outer face for the mounting of the valve housing 16 which may be secured thereto as by machine screws 31.

End section 25 of the pump body and valve housing 16 preferably terminate at their lower ends in outturned flanges 32 (Fig. 6) for supporting the pump and valve assembly. The exemplary pump is designed to be supported within the body of a tractor as by bosses 33 extending upwardly from the bottom 34 of the tractor crank case. Machine screws 35 inserted through holes in the bosses and threaded into tapped holes in the flanges 32 securely anchor the pump and valve assembly in place in the tractor.

The intermediate section of the pump body is formed with one or more of the cylinder bores 11, there being three such bores in the exemplary pump although it will be appreciated that the number of cylinders to be provided is a matter of choice. The bores 11 extend entirely through the intermediate section 20 opening in its narrower upper and lower faces as shown in Fig. 2. Each bore is stepped adjacent its lower end so as to present axially spaced downwardly facing shoulders 40 and 41, the purpose of which will become apparent as the description proceeds.

Extending longitudinally of the body section 21 are two passages 42 and 43 opening in the pad 30 for communication with passages in the valve housing 16 and respectively forming inlet and outlet passages for the pump cylinders 11. As shown in Fig. 2, the inlet passage 42 is located so as to intersect the cylinder bores 11 below the shoulders 40. The outlet passage 43 is located above the inlet passage and at one side of the cylinders 11. Communication with the cylinders is by way of cross passages 44 drilled from the rear face of the body section 21 to intersect the passage 43 and open into the cylinder bores.

Communication between the inlet passage 42 and the cylinders 11 is controlled by inlet valve assemblies 45, one of which is fitted into the lower end of each cylinder bore. As shown in Fig. 2, the valve assembly 45 comprises a guide member 46 adapted to abut against the shoulder 40 in the cylinder bore and having drilled passages 47 establishing communication between the inlet passage 42 and a chamber 48 in the upper end of the guide member. Communication between the chamber 48 and the cylinder is controlled by a movable valve member having a head 49 coacting with a valve seat encircling the chamber. The valve member is guided between open and closed positions by a stem 50 extending downwardly from the head 49 and slidable in a central bore in the guide member 46. A compression spring 51 interposed between the lower end of the guide member and an abutment such as a collar 52 fixed on the end of the valve stem urges the valve to closed position but permits it to open when necessary to admit fluid to the cylinder with which it is associated.

A plug 53, recessed for the accommodation of the valve stem and its spring and threaded into the lower end of the cylinder bore 11, abuts the guide member 46 and wedges it into sealing engagement with the shoulder 40. The shoulder 41 in this instance defines the limit position of the plug. As shown, the plug is formed with a slot 54 or other suitably shaped recess for engagement with a tool, such as a screw driver, by which the valve assembly may be removed for inspection, cleaning or repair.

Communication between the outlet passage 43 and the cylinder bores 11 is controlled by outlet valve assemblies 55, one of which is fitted into each of the cross passages 44. The valve assembly in its preferred form comprises a movable valve member having a head 56 adapted to engage a seat formed by a rearwardly facing shoulder 57 in the bore 44. A stem 58 extends rearwardly from the valve head and is guided in a flanged guide member 59 held against the shoulder 60 in the bore 44 by a plug 61 threaded into the bore. A compression spring 62 interposed between the valve head 56 and the flange on the guide member urges the valve to closed position. The plug 61 like the plug 54 has its outer end formed for convenient engagement with a tool such as a screw driver by which the valve assembly may be removed for cleaning or servicing.

Each of the plungers 12 is dimensioned for a working fit in its cylinder 11 so that as it is moved upwardly in the cylinder, fluid will be drawn from the passage 42 through valve 45 into the cylinder. In the downward movement of the plunger, the fluid is trapped by closure of the valve and is forced out of the cylinder through the valve 55 and outlet passage 43. As shown in Fig. 2, the piston 12 may be formed with a series of circumferential grooves 63 operative to trap a quantity of oil and insure adequate lubrication of the cylinder wall when the pumping action is stopped, that is, when the inlet passage 42 is closed to shut off the supply of fluid.

Reciprocation of the valve plungers 12 is eflected by the shaft 13 acting through the drive mechanisms 15, as mentioned heretofore. For this purpose, each of the pistons 12 is provided at its upper end with a transverse member or crosshead 65 fixed to the piston intermediate its ends as by a pin 66. The drive shaft 13 is formed with a plurality of eccentrics 67, one for each cylinder, and these eccentrics are located in alinement with the respective cylinders. Rotatably mounted on each eccentric is a follower member or slipper 70 having a pair of laterally spaced guide elements 71 depending from its lower end and dimensioned to slidably receive the crosshead 65 and to confine its movements relative to the slipper in a direction normal to the axis of the piston. In other words, the guides and crosshead operatively connect the slipper with the piston in a manner such that positive movements are imparted to the piston in both directions, that is, into and out of the cylinder as the slipper is traversed around a circular orbit in the rotation of the eccentric upon which it is mounted. The crosshead, of course, slides back and forth in the guides as the slipper follows its orbital path.

The crosshead 65 is preferably rectangular in cross section and dimensioned to present a bearing surface of relatively large area on its upper face for receiving the thrust of the slipper 70. In the particular embodiment illustrated, a bearing plate 72 of bronze or other suitable bearing material is interposed between the bearing surfaces on the crosshead and the slipper to reduce friction. However, if it is desired to further simplify the pump construction, the bearing plate may be omitted in which case the crosshead is desirably made of chilled cast iron and the slipper of bronze with lead flashed on the coacting bearing surfaces. When the bearing plate is used, it is held in place by a dowel pin 73 fitted into the slipper.

For convenience of manufacture and assembly, the follower or slipper 70 is constructed in two sections adapted to meet in a substantially vertical plane through the axis of the eccentric 67. The two sections are secured together in any suitable manner as by machine screws 75. Preferably, a bearing ring 76 is interposed between the eccentric and the slipper, the ring being split along a line at right angles to the cylinder axis and installed with the split displaced approximately degrees from the junction between the two parts of the slipper to relieve the latter of a portion of the stresses developed by the thrust on the piston. Means such as a dowel pin 77 may be provided for retaining the hearing ring in place.

In accordance with another aspect of the invention, the bending moment imposed on the crosshead 65 at the point of maximum thrust from the slipper 70 is substantially reduced by locating the drive shaft 13 with its axis offset toone side of the axes of the cylinders 11. As shown in Fig. 2, the offset is such that the cylinder axis when extended passes approximately midway between the axis of the shaft and the center of the eccentric 67. As maximum thrust occurs when the piston 12 is substantially at its midstroke, as shown in Fig. 2, it will be evident that the bending effect on the crosshead at this point will be materially reduced.

The invention also contemplates the provision of a novel arrangement for positively lubricatingthe bearings for the shaft 13 and other moving parts at the upper end of the pump structure so that the pump may be operated dry, that is, with the upper portion above the level of the oil in the sump or compartment of the tractor body in which it is installed. As indicated heretofore, a supply of lubricating oil under pressure is furnished by the auxiliary pumping device 17 which may comprise a small plunger-type pump adapted to be driven from the pump drive shaft 13.

Referring to Figs. 6-9 of the drawings, the auxiliary pump 17 comprises a cylinder formed by a generally upright hole 81 drilled in the intermediate body section 20 closely adjacent the end section 25. A plunger 82 having a working fit in the cylinder 81 is operatively connected by a pin 83 with the crosshead 65 of the adjacent pump piston. The plunger 82 therefore reciprocates in its cylinder 81 in synchronism with the reciprocation of the adjacent pump piston.

An inlet for the cylinder 81 is formed by a vertical passage 84 drilled in the body section 25 and opening at the bottom thereof to receive oil from the compartment in which the pump is mounted. Adjacent its upper end the passage 84 is connected by a drilled transverse passage 85 with the cylinder 81 preferably at a point slightly above the midstroke of the plunger 82. This allows the plunger to trap oil in the bottom of the cylinder in its downward stroke and eliminates the need for an intake valve. A threaded plug 86 closes the outer end of the cross passage, as shown in Fig. 8.

Fluid under pressure is discharged from the cylinder 81 through a drilled passage 87 in the pump body section 25 which passage communicates with the cylinder through a drilled cross passage 88 (Fig. 9) having its outer end closed by a threaded plug 89. The cross passage 88 is formed with a shoulder defining a seat for a ball check valve 90 adapted to restrict oil flow through the passages to one direction, that is, outwardly from the cylinder 81. A spring 91 interposed between the end of the plug 89 and the ball 90 urgesthe latter to closed position.

At its upper end, the passage 87 opens into an annular channel 92 (Fig. 1) formed in the body section 25 and bearing block 27 so as to encircle the shaft 13. It will be observed that the bearing 29 for the shaft is in the form of two rings located on opposite sides of this channel. The channel communicates through radial holes 93 in the shaft with a central lubricating passage 94 extending axially through the shaft 13. This passage is preferably drilled from one. end of the shaft (the left end, as viewed in Fig. 1), and the open end of the passage is closed by a ball-type relief valve 95 urged to closed position by a spring 96.

Radial passages 97 in the shaft 13 lead from the central passage 94 to the bearing surfaces of the eccentric 67 and also to a space between the bearings '29 at the right end of the shaft. Passages 97' (Fig. 2) in each slipper 70 conduct oil from the eccentric bearing to the bearing surfaces of the slipper and the associated crosshead 65. Thus the bearings for the shaft, the hearing surfaces for the eccentric and slippers and the bear ing surfaces for the crossheads are continuously supplied with oil under pressure to ensure adequate lubricating whenever the pump is operated.

In the exemplary pump the shaft 13 is arranged to be driven through the medium of a gear 98 keyed to the projecting end of the shaft. Thegear is located closely adjacent the end section 25 and in a position to receive oil forced through the bearing 29 for the shaft. Such oil is caught in a circumferential groove 99 in the inner face of the gear and thrown outwardly at relatively high velocity through diagonally disposed passages 100 in the body of the gear. Adjacent moving parts of the tractor are thus lubricated.

The control valve mechanism enclosed in the housing 16 is particularly designed for operation in systems of the type disclosed in the Ferguson patent previously referred to. Structurally, it is generally similar to the valve mechanism disclosed in the co-pending application of Alexander Senkowski and Witold Czarnocki, Serial No. 126,603, filed November 10, 1949 now Patent No. 2,763,528, issued March 30, 1954. As shown in Figs. 1 and 4, the valve mechanism comprises a movable valve member or plunger 101 reciprocable in a liner sleeve 102 fitted into a bore 103 in the housing 16. The sleeve 102 is in communication at its lower end with a fluid inlet passage 104 formed in the lower section of the housing which passage is connected by a conduit 105 of relatively large diameter with a sump or reservoir in the tractor body which holds a supply of fluid for use in the hydraulic system. Ports 106 in the sleeve open into an annular chamber 107 in the valve housing which is in communication with the pump inlet passage 42. Plunger 101, by opening or closing the ports 106, admits fluid to the pump or shuts off the fluid supply when the pumping operation is to be stopped.

The valve housing 16 is also formed with a horizontal passage 110 (Figs. 4 and 5) communicating through a branch passage 111 with the outlet passage 43 in the pump body as shown in Fig. 5. A check valve 112 guided in a sleeve 113 and urged to closed position by a s ring 114 prevents fluid flow from the valve to the cylinders while permitting flow in the opposite direction. The passage 110 opens to an annular chamber 115 encircling the sleeve 102 and also to a vertical passage 116 which turns forwardly at its lower end and is connected by a conduit 117 (Fig. 1) with the actuator of the tractor power unit. Pressure fluid from the pump is thus delivered to the actuator by way of the passages above mentioned, and the conduit 117.

To provide for exhaust of fluid from the actuator, the sleeve 102 is formed with radial ports 118 communicating with the ch mber 115. When the plunger 101 is shifted downwardly from the position in which it is shown in the drawings, the ports 118 are uncovered to permit flow of fluid into a chamber 119 in the upper part of the valve housing connected by a passage 120 (Figs. 4 and 5) with the passage 104 which, as before explained, is connected to the sump. The chamber 119 is closed at its upper end by a suitable sealing member 121 fitted into the upper end of the valve member and apertured to slidably receive an extension sleeve 122 fixed to the upper end of the valve plunger.

As will be seen by reference to Figs. land 4, the ports 106 and 118 are spaced apart so that the plunger 101 closes both sets of ports when in the neutral position in which it is shown in the drawings. The pump therefore operates idly, that is, it delivers no fluid, and exhaust of fluid is blocked by the closed ports 118. As the plunger is moved upwardly, ports 118 remain closed and the ports 106 are opened progressively to admit fluid to the suction side of the pump. The pump accordingly delivers fluid under pressure through the passages 43, 110, 116 and conduit 117 to the actuator.

Movement of the valve plunger 101 in the opposite direction, that is, downwardly from the neutral position, opens the ports 118 while keeping the ports 106 closed. The pump is therefore idle and fluid is exhausted from the actuator and returned to the sump by way of the conduit 117, passages 116 and 110, chamber 115, ports 118, chamber 119, passages 120 and 104 and conduit 105. Ports 118, which are preferably of relatively small cross sectional area, serve to meter the exhaust from the actuator and thus determine the maximum rate at which fluid is permitted to exhaust from the actuator under the gravity load imposed on it by the implement attached to the tractor hitch linkage. Precise regulation of the discharge rate is facilitated by tapering the upper end of the valve plunger, as indicated at 123.

The plunger 101 is shifted between its various positions by control mechanism on the tractor which includes a lever (not shown) having one end confined between spaced fianges 124 on the extension sleeve 122. To prevent the valve plunger from sticking, provision is made for continuously oscillating it about its longitudinal axis. In the exemplary embodiment, oscill tion is effected through the medium of a torsionally flexible rod 125 secured at its lower end to the plunger 101 as by a pin 126 adjacent its junction with the extension sleeve. The upper end of the rod is formed with radially projecting arms 127 engageable in longitudinal grooves in the inner wall of a sleeve member 128 journaled in a bracket 129 bolted or otherwise rigidly secured to the end of the pump body. The sleeve 128 has a fork 130 at its upper end embracing the pump drive shaft 13 and carrying follower rolls 131 engaging in a cam groove 132 in the enlarged end portion of the shaft. This groove is disposed in a plane oblique to the axis of the shaft and consequently rotation of the shaft is effective to oscillate the sleeve 128 about its axis and oscillating movements are transmitted to the valve plunger 101 through the torsion rod 125.

Provision is made for lubricating the cam groove and follower 131 from the pressure feed system of the pump described heretofore. To this end, the drive shaft 13 is formed with an inclined passage 133 (Fig. 1) communicating with the oil space between the bearing rings 29 for the right end of the shaft. The passage 133 extends to an axial passage 134 in the shaft which has radial branches 135 (Fig. 4) opening at the bottom of the cam groove.

It will be apparent from the foregoing that the invention provides a pump of novel and advantageous construction particularly well adapted for use in tractor hydraulic systems. By reason of its simple construction and the novel relationship of its components, the pump may be manufactured at low cost. It is rugged and dependable and capable of functioning with a minimum of attention under the severe operating conditions encountered in a tractor environment.

The novel drive mechanism provided for driving the pump plungers from the rotary drive shaft is advantageous in minimizing strains on the parts with the consequent reduction in wear and material lengthening of their useful life. Furthermore, the novel arrangement provided for forced lubrication permits the pump to be installed with the major portion of its moving parts located above the oil level in the tractor body.

We claim as our invention:

1. A pump comprising, in combination, an elongated generally fiat casting having a series of main cylinder bores disposed in parallel relation in a straight line, a drive shaft extending across the ends of said cylinders and rotatably supported at opposite ends in bearings carried on said casting, eccentrics on said shaft positioned adjacent the respective cylinders, a slipper rotatably mounted on each eccentricand having means defining a guideway disposed transversely of the axis of the adjacent cylinder, a piston rcciprocable in each cylinder, a crosshead operatively associated with each piston and engaging in the guideway of the adjacent slipper for transmitting reciprocatory movement to the piston, an auxiliary cylinder bore formed in said casting at one end of the line of main cylinder bores, said auxiliary cylinder bore having an inlet communicating with a source of lubricating oil and a branched outlet extending to the bearings for said shaft, said slippers and to said guideways, a plunger reciprocable in said auxiliary cylinder bore, and means operatively connecting said plunger with the crosshead of the piston in the adjacent main cylinder bore for reciprocation thereby.

2. A pump comprising, in combination, an elongated generally fiat casting having a series of generally vertical cylinder bores arranged in a line and opening at opposite ends in the narrow ends of the casting, a piston reciprocable in each cylinder bore, a shaft extending across said cylinder bores and rotatably supported at opposite ends, a series of eccentrics on said shaft alined with the respective cylinder bores, means connecting said eccentrics to said pistons for reciprocating the latter in response to the rotation of said shaft, said casting having a first horizontal bore intersecting said cylinder bores at their lower ends and defining an inlet passage for the cylinder bores, valve mechanism removably mounted in the lower end of each cylinder bore controlling communication between said inlet passage and the cylinder bore, said casting having a second horizontal bore disposed along one side of the cylinder bores and connected with the latter by transverse passages, said second bore defining an outlet passage for the cylinder bores, valve mechanism in each transverse passage controlling communication between the cylinder bores and said outlet passage, control valve mechanism including a housing secured at one end of said casting, said housing defining a valve chamber and having drilled passages connecting said inlet and said outlet passages respectively with said valve chamber.

3. A pump comprising, in combination, a body adapted to be mounted in an oil sump with its upper end above the oil level in the sump, said body having an upright main cylinder bore, a piston reciprocable in said cylinder, a shaft extending transversely across the upper end of said cylinder, bearings on said body rotatably supporting said shaft at opposite ends, an eccentric on said shaft, a follower member rotatably mounted on said eccentric, said shaft having a passage for conveying lubricant to said bearings and said follower members, a crosshead operatively connecting said follower member with said piston, said pump body having at one end a generally upright auxiliary cylinder bore, a plunger reciprocable in said auxiliary cylinder bore, means operatively connecting said plunger with said crosshead for reciprocation with said piston, an inlet passage extending from said auxiliary cylinder bore to the bottom of the pump body for admitting oil to the cylinder bore from the sump in which the pump body is mounted, and means defining an outlet passage in said pump body connecting said auxiliary cylinder bore with the lubricant passage in said shaft, said plunger being operative in its reciprocation to draw oil through said inlet passage and deliver it under pressure to said lubricant passage.

4. A pump comprising, in combination, a body adapted to be mounted in an oil sump with its upper end above the oil level in the sump, said body having an upright main cylinder bore, a piston reciprocable in said cylinder, a shaft extending transversely across the upper end of said cylinder, bearings on said body rotatably supporting said shaft at opposite ends, an eccentric on said shaft, a follower member rotatably mounted on said eccentric, said shaft having passages therethrough for conveying lubricant to said bearings and to said follower member, a crosshead operatively connecting said follower member with said piston, said body having at one end a generally upright auxiliary cylinder bore, a plunger reciprocable in said auxiliary cylinder bore, means operatively connecting said plunger with said crosshead for reciprocation with said piston, means defining an oil inlet passage for said auxiliary cylinder bore having an inlet opening adjacent the lower end of the pump body and openng into the auxiliary cylinder bore approximately midway of the stroke of said plunger, and means defining an outlet passage for said auxiliary cylinder bore opening from the bottom of the cylinder bore and extending upwardly to communicate with the lubricant passages in said shaft.

5. A pump comprising, in combination, an elongated body casting having a series of cylinder bores opening on its narrow end, a piston reciprocable in each cylinder, a shaft extending across the cylinder bores, bearings rotatably supporting said shaft at opposite ends on said casting, means including eccentrics on s id shaft and members rotatably mounted on said eccentrics for reciprocating said pistons in the rotation of said shaft, an auxiliary lubricating pump including a cylinder formed in said casting and having a working piston reciprocable with one of the first mentioned pistons, said auxiliary pump being operable to deliver oil under pressure to a channel encircling said shaft, said shaft having a longitudinal lubricating passage with radial branches communicating with said channel, said bearings and the eccentrics, and a gear wheel on said shaft for rotating the same, said gear wheel being located closely adjacent one of said hearings to receive oil therefrom having radial passages adapted to throw off the oil so received to lubricate adjacent moving parts.

6. A pump as defined in claim 1 including a spool type valve member shiftable axially for controlling operation of the pump, drive mechanism including a cam on the drive shaft and a follower cooperating with said cam to oscillate said valve member about its axis, said drive shaft having an oil conducting passage extending from the outlet of the auxiliary cylinder to said cam.

7. A pump as defined in claim 4 in which said shaft has a plurality of radial passages in communication with the lubricant passage therethrough, and in which communication between the outlet passage for the auxiliary cylinder bore and the lubricant passages through the pump shaft is effected through the medium of an annular chamber in one of the shaft bearings connected to the outlet passage for the auxiliary cylinder bore, and to said plurality of radial passages in said shaft.

8. In a pump having a body casting with a series of upright cylinder bores therein, passages in said body defining fluid inlets and outlets for said cylinder bores, pistons reciprocable in said cylinder bores, a shaft extending across said cylinder bores, bearings mounted on said body rotatably supporting said shaft at opposite ends, and means interposed between said pistons and said shaft operative in the rotation of said shaft for reciprocating said pistons, said shaft having passages therethrough for conveying lubricant to said bearings and to said reciprocating means, the combination of means for lubricating said bearings and said reciprocating means comprising an auxiliary pump formed by three generally upright bores drilled in the pump body and connected by two transverse drilled bores, one of said upright bores defining an auxiliary purp cylinder, another of said upright bores defining an inlet passage connecting said one bore with a fluid reservoir, the third one of said upright bores defining an outlet passage for connecting the auxiliary cylinder with the lubricant passages in said shaft, a check valve in said outlet passage allowing flow only from said auxiliary pump cylinder to said outlet passage, 21 plunger reciprocable in said auxiliary pump cylinder, and means for reciprocating said plunger in response to the rotation of said shaft.

9. A pump as defined in claim 4 in which the lubricant passages in the shaft include an axially-extending passage and a series of radially-extending outlet passages communicating with said axially-extending passage, and a relief valve closing one end of said axially-extending passage.

References Cited in the file of this patent UNITED STATES PATENTS 1,964,245 Benedek June 26, 1934 2,081,224 Coberly May 25, 1937 2,118,180 Ferguson May 24, 1938 2,288,963 Von Tavel July 7, 1942 2,324,291 Dodge July 13, 1943

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