US2674949A

US2674949A - jollig

Info

Publication number: US2674949A
Authority: US
Publication date: 1954-04-13
Anticipated expiration: 1971-04-13

Description

April 13, .1954 w. M. J. JULLIG LUBRICANT PUMP WITH REMOVABLE PUMP ELEMENTS Filed May 22, 1951 7 Sheets-Sheet 1 Zhwentor (momma.

April 13, 1954 w. M. J. JULLIG LUBRICANT PUMP WITH REMOVABLE PUMP ELEMENTS 7 SheetsSheet 2 Filed May 22, 1951 April 13, 1954 w. M. J. JULLIG LUBRICANT PUMP WITH REMOVABLE PUMP ELEMENTS Filed May 22, 1951 7 Sheets-Sheet 3 April 13, 1954 w. M. JULLIG LUBRICANT PUMP WITH REMOVABLE PUMP ELEMENTS Filed May 22, 1951 '7 Sheets-Sheet 4 April 13, 1954 w. M. J. Jl'JLLlG LUBRICANT PUMP WITH REMOVABLE PUMP ELEMENTS 7 Sheets-Sheet 5 Filed May 22, 1951 FIG. 9a

FIG. 10

Snnenton attorney.

April 13, 1954 w. M. J. JULLIG LUBRICANT PUMP WITH REMOVABLE PUMP ELEMENTS Filed May 22, 1951 '7 Sheets-Sheet 6 FIG/l FIG. Ila

Junentor:

April 13, 1954 w. M. J. JULLIG LUBRICANT PUMP WITH REMOVABLE PUMP ELEMENTS Filed May 22, 1951 7 Sheets-Sheet '7 FIG/4 FIG/3 -l5m M1) 15k A Patented Apr. 13, 1954 LUBRICANT PUMP WITH REMOVABLE PUMP ELEMENTS Werner Max Josef Jiillig, Atvidaberg, Sweden, assignor of one-half to Robert Vogelgesang, Sodertorns Villastad, Sweden Application May 22, 1951, Serial No. 227,705 Claims priority, applicationsweden July-6, 1950 12 Claims. 1

The present invention refers to lubricant pumps with removable pump elements, and particularly relates to grease lubricating apparatus. Such apparatus are generally constructed with a grease receptacle located at the top and with plunger pumps arranged therebeneath in a circle about a central axis. The grease by reason of its stiff consistency will have to be pressed with some pressure to the inlet apertures of the plunger pumps, and this generally takes place through wing-shaped means rotating in the grease receptacle.

A technical requirement is that the pump elements shall be exchangeable, since in the pumping of grease considerable pressures are frequently produced and the grease always contains abrasive mineral sparticlesso that the pumps will be worn down comparatively rapidly. A number of constructions with exchangeable pump elements have'been proposed, said elements being then generally arranged in a circle approximately midway of the apparatus in the vertical direction thereof while being adapted to be taken out in a radial direction, th connecting screw bonds for the pipe conduits to the places of lubrication being rigidly connected with the pump elements. In an apparatus of this description it is necessary first to disassemble the connecting screw bonds of the pipe conduitsto permit a pump element to be removed. Furthermore, the-elements will have to be pulled out in a radial direction horizontally, it being then conveivable that the apparatus islocated near a wall so as to make the attaching screws of the elements relatively inaccessible.

The above-named disadvantages are avoided in the lubricant pump according to the present invention, which is substantially distinguished by the feature-that the pump elements, with the upper portion of the apparatus removed, are arranged to be disassembled vertically upwards while being secured to a common plane bottom plate, which is rigidly connected with the pump housing and provided with openings having parts of a driving member common to all pump elements and situated underneath the bottom plate extending therethrougn. This brings the advantage that it will b possible to have the elements screwed fast to a horizontal surface from which they may be lifted up vertically to be exchanged.

A form of embodiment of the invention will be described hereinbelow'by way of example with reference to the accompanying drawings, wherein Fig. 1 illustrates a vertical section through the apparatus. The left hand side of Fig. 2 is a view of the apparatus upon removal of the receptacle, and the right hand'side of Fig. 2 shows the worm gearing housed in the base of the apparatus. Fig. 3 is a perspective view of *the'apparatusupon removal of the receptacle. Fig. 4 is a perspective view of the central shaft with a helical gear arranged thereon. Fig. 5 is a perspective view of the operating plate with appertaining pressure rods. Fig. 6 is a perspective view of the disk for parallel movement. Fig. '7 is a perspective view of the pressure plunger with a set screw. Fig. 8 is a perspective View of the pump element. Figs. '9, 9a,, 922 show a pressure plunger. Figs. 10, lOa show a plunger with a set screw and ball arresting means. Figs. 11, 11a. and 12 show the set screw to a larger scale. Figs l?-15 show the pump element to a larger scale.

It will appear from Fig. 1 that the apparatus is composed of three principal parts, that is to say the upper part situated above the line A-A and having the low pressure portion built into the same, the intermediate part located between the lines A-A and B-.B and containing the high pressure portion, and the lower part situated underneath the line B--B and containing the worm gearing for the operation of the apparatus.

The upper part This part consists of the bottom it of a receptacle, which is rigidly connected with the wall it of the receptacle, covered at the top by a lid L2. The upper part is attached by means of screws I3 onto the intermediate part. and is tightened by means of a rubber ring. The bottom H] of the receptacle has a round aperture provided at th centre thereof, said opening being terminated at the bottom by a perforated supporting plate 8 having a fine strainer l lying thereabove. The supporting plate 8 is rigidly connected with the bottom it of the receptacle by means of screws 9. Mounted at the centre of the supporting plate 8 is a hub 5 carrying an oblique pin i,.on which a conical body I is rotatably mounted. 'Thisbody engages the supporting plate "8 through the

pins

2 and 3 in a simple gear engagement so as to perform. a rolling movement, as soon as the hub 5 with the oblique pin l is brought into a rotary movement. A wing, not shown, is rigidly connected with the hub '5 and ensures that the grease is fed in beneath the body I, which by its rolling movement presses the grease through the strainer 1 and large openings in the supporting plate 8 to the inlet openings of the pump elements.

The intermediate part attaching screw 4 6. For each element there is provided in the housing 14 a channel bore Hid establishing communication between the cylinder I space of the pump element and the outlet screw plug 17. In the present instance this screw bond has a check valve (ball, spring and plug) built into the same, which parts, however, are not necessary in principle for the functioning of the apparatus, inasmuch as the inlet and the outlet of the cylinder ar positively governed by the mode of operation of the plunger to be described in the following. The ball valve only has for its object to relieve the pump, in order to increase the life thereof.

Mounted between the central aperture of the pump housing and the central aperture of the base 26 is a central shaft 21 formed at the middle portion thereof into an eccentric having the operating disk 25 mounted thereon. A disk 36 for parallel movement (see also Fig. 6) ensures that the operating disk cannot turn about its own axis but is only permitted to perform a circular translatory movement. gages, on the one hand, with the pump housing l4 through two guide rollers 23, and also engages the operating disk 25 through two guide rollers 24 (see also Fig. 5). Each point of the operating disk thus performs a translatory circular movement with a radius of the magnitude of the eccentricity of the eccentric 21. The pressure rods 2! rigidly connected with the operating disk also participate in this movement. The shape of the rods 2| will appear from Fig. 5. These rods are provided with slits in their top portions, said slits being engaged by the eccentric shaft portion I 827 of the plungers (see Fig. 7) The planetating'motion of the pressure rods imparts to the plungers a rotary movement tc and fro as well as a reciprocating axial movement. The first movement serves to govern the opening and closing of the inlet and outlet bores of the cylinder, in a manner such that the groove I80 (Fig. 9) of the plunger is alternately brought into communication with the induction bore its and the outlet bore ltd of the pump element (Fig. 14). The bore I 5e (Fig. 14) has no function to fulfill, but is produced in the making of the bore i503. On the other hand, said bore I56 1 is not detrimental, since the groove 180 of the plunger is never brought into communication with the same. The outlet bore Hid communicates through the bore l5 with the bore i5?) (see Figs. 1 and 14). The bore hif is terminated outwardly through the screw leg shown in Fig. 3. Pressed into a recess [5a on the lower side I bit of the element (Fig. 13) is a ring i5 from hard copper (Fig. 13), which projects somewhat beyond the lower side of the element and has for its object to tighten the outlet passage of the element against the plane I of the housing M (Fig. 1).

The pump elements are retained in the apparatus by means of a plug-18a (Figs. 1 and 8) engaging into a radially directed bore in the ring Ma (Fig. 1), which is rigidly connected with the hub Mb of the pump housing Id. The plug 58a is accurately fitted into the element, and the inner end thereof is somewhat upset, whereby an efficient tightening effect is obtained for the pressure liquid in the cylinder space. between the element and the plug is only a friction bond, however, which would not be capable per se to take up the relatively high liquid pressures frequently present in the cylinder. On the other hand, this is not necessary, inasmuch as the plug has an axial support by the hub Mb of the housing 14. thus conveyed from the pressure rod 2| over To attain this, it en The bond- The operating pressure is the plunger l8, the enclosed liquid and the plug 18a directly onto the hub Mb, without exert ing any greater axial force on the element l5 than the corresponding force for overcoming the friction between the element [5 and the plug I 8a. By a ball-shaped configuration of the outer end of the plug (see l8a in Fig. 8) the element may be swung upwardly as shown in Fig. 3, when the attaching screw I6 is removed.

The pump element is also retained by means of the screw I6, which powerfully presses the packing ring I5 (Fig. 13) against the plane Me of the housing (Fig. 1). The head of the screw is fits with a small clearance into the bore I576 of the element (Fig. 15) but has a large clearance in the bore |5m of the element (Fig. 15) as well as in the packing ring I57. The bore [46 in the plane Me of the housing I4 (Fig. 1) is so large at the top that an annular space is produced between the bore and the screw, said annular space communicating with the bore Md leading to the outletscrew bond.

The attaching screw 26 thus fulfills two objects, first to retain the pump element and, sec- 0nd to tighten the channel connection between the element and the pump housing.

The pressure plunger and the set screw are shown in Figs. 7, 9, 10, 11 and 12.v The plunger i8 is formed as a crank with the crank pin lab. The plunger head contains a smooth bore having the set screw 2!] mounted therein. The set screw has a single thread with a great pitch, which is formed as a helical groove, the bottom of which has milled into the same a number of spherical recesses 26a, 20b, 200. The plunger head con-I tains a spring-loaded ball H), which is fitted into.

the largest recesses, which thus serve as holding catches. The helix has a single convolution, the pitch of which is equal to the length of stroke of the pressure plunger. By turning the set screw one revolution, the Whole length of stroke may thus be transformed into an idle movement. The outermost ball recesses 20a and 200 (Fig. 12) are milled to such a depth that the ball l9cannot rise to the cylindrical surface of the stem portion of the screw. Hereby these ball recesses form limiting means for the turning movement.

The remaining recesses are more shallow, so that a certain torque is required to turn the set screw to and fro, without preventing, however, a turning movement of the screw when applying a greater force. The length of the set screw is so adapted that, should the set screw be screwed out as far as it goes (that is to say, until the ball 19' is received in the ball recess 290), the head of the set screw is caused to touch the inner wall of the housing I4 (Fig. 1). This abutment, which is known per se, has for its object to prevent a pump from sucking a larger quantity of liquid than the adjusted one, which might take place without this abutment on account of jolting or by too large a superatmospheric pressure on the suction side originating from the low pressure contrivance.

A coaxial arrangement of the pump plunger and the set screw ensures that the set screw does not perform any oscillatory movements, for instance as in the older construction described in the aforementioned patent.

If all of the lubricant cutlets I! are not to be used, the pump elements [5 associated with the non-used outlets can be installed without their plungers such as indicatedby pump element l 59: in Fig. 2 and the outlet sealed by a plug 34.

Coupling between the upper part and the intermediate part Such coupling is effected by a resilient strap 2M (Figs. 1 and 4), which is mounted in two apertures in the central shaft The strap engages a groove on e lower side of the hub (Fig. l). The str p as well as the groove are situated somewhat eccentrics iv so to ensure that coupling is possible only in a definite relative position between the low pressure and the high pressure mechanisms. is necessa to warrant that the conical body l exerts its greatest pressure on the grease, when the pump performs its suction stroke, so that a filling of the plunger space as complete as possible will be obtained.

worm gearing 2 3, 29 adapted to transmit the rotary movement of the outer driving shaft 3i onto the central shaft The is equipped at the top with a sliding surface so that the operating disk will be guided between this surface and the lower side l if of the housing M. The lubricant pump described above and illustrated in the drawings only constitutes example of embodiment of the invention and be varied in its construction and details, with-- out the principle of the invention being departed from.

What I claim is:

1. In a pump adapted to pump lubricants and the like the combination comprising a pump housing having a plane transverse bot W... plate, a plurality of pump elements arranged. rad'ally on said bottom plate about a common verti axis, means releasably securing said pump elez 0 its in place on said plate such that upon the of said securing means said pump elements may released vertically upwards, each said pump element comprising a body portion including a cyl inder arranged radially of said vertical axis having an inlet port communicant with a source of the lubricant and an outlet port communicant with. a channel in said plate leading to the exterior of said pump housing and a plunger element slidable in said cylinder, and eccentric driving means for the plungers of all said pump eleme' Us, said driving means comprising driv elements in releasable driving relation respectively wit e radially outward end of each plunger, said (3 iving, elements extending upwardly through said plate, and eccentrically movable means disposed below said plate and connected with said draing elements for driving the same simultaneously.

2. A pump as defined in claim 1 wherein the releasable securing means for each of said pump elements includes a plug individual to and. closing the radially inward end of the cylinder of each pump element, the portion of said plug within said cylinder being cylindrical and of substantially the same diameter as that of the cylinder and the plug portion outside of said cylinder including a ball-shaped end seated in a socket provided in a hub portion of said plate.

3. A pump as defined in claim 1 wherein the body portion of each said pump element decreases in width in a radially inward direction with the top and bottom faces thereof located in parallel planes, and the pump elements are disposed in closely spaced side-by-side relation.

4. A pump as defined in claim 1 wherein the releasable securing means for each of said pump elements includes a single attaching screw extending through a bore in the body of said pump element into said plate.

5. A pump as defined in. claim 4 wherein the bore in the body of each pump element for the attaching screw constitutes also a portion of the outlet port of each pump element, the diameter of the screw being smaller than that of said bore to permit of the lubricant in the annular space thereby provided between the screw and wall of the bore.

6. A pump as defined in claim 5 wherein the channel in said plate leading to the exterior of the pump housing from each pump element in cludes an inlet end concentric and communicant with the screw receiving bore in the pump element, and a packing ring sealing the joint therebetween and which is compressed by said screw.

7. A pump as defined in claim 1 wherein the plunger of each pump element is provided with a stroke regulating member adjustable longitudinally of the plunger and arranged coaxially therewith and which engages the associated driving element of the driving means.

8. A pump as defined in claim 7 wherein the stroke regulating member for each plunger is constituted by a screw having a disk-shaped head and a single thread in the form of a helical groove of semi-round cross section and a pitch equal to the maximum of the plunger stroke, said groove having space recesses therealong and a springloaded retaining ball mounted in a recess in the plunger and selectively engageable with one of the recesses in said groove.

9. A pump as defined in claim 8 wherein the recesses in the helical groove of each plunger stroke regulating screw are comprised of a recess at each end of the groove and a plurality of other recesses distributed in uniformly spaced relation over the length of the groove.

10. A pump as defined in claim 9 wherein the recesses at the ends of the helical groove of each plunger are of such depth that the retaining ball cannot rise upwardly upon continued rotary movement of the screw and thereby serve as limit means for the rotary movement of said screw.

11. A pump as defined in claim 1 wherein the driving means of said plungers is comprised of a disc mounted horizontally in said pump casing below said plate and means effecting an eccentric motion of said disc in a horizontal plane about the said vertical axis of the pump, the driving elements for the plungers of the pump elements being secured to and along the periphery of said disc for effecting a corresponding translatory motion of said driving elements.

12. A pump as defined in claim 1 wherein at least one of said radially arranged pump elenients has the plunger removed therefrom and further including means sealing the lubricant outlet associated therewith.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 1,645,834: Voreaux Oct. 18, 1927 1,742,770 Kamrath Jan. '7, 1930 1,843,733 Powell Feb. 2, 1932 2,504,543 Le Clair Apr. 18, 1950 FOREIGN PATENTS Number Country Date 533,405 Great Britain 1941 627,329 Great Britain 1949 926,830 France 1947