US2787336A - Lubricant pump and reservoir - Google Patents

Description

April 2, 1957 T. R. THOMAS LUBRICANT PUMP AND RESERVOIR 6 Sheets-Sheet l Filed Oct. l, 1951 w mw T #R mi c MM m n M l? YN@ m Q En mm www. wWwwW/ww a uw g \.l\ Q mm ww a mm u@ w L :lun Qmx @MN q www1 W mmm w .QQ i-- 1 n 1 E R @Qmwm w www@ h i E* @N April 2, 1957 T. R. THOMAS LUBRICANT PUMP AND RESERVOIR 6 Sheets-Sheet 2 Filed Oct. l, 1951 c/ ATTORNEYS IN VENTO R gli April 2, 1957 T. R. THOMAS LUBRICANT PUMP AND RESERVOIR 6 Sheets-Sheet 3 0 124k, lf3 130 105 Filed Oct. l, 1951 kai INVENTOR Q THOMAS l? THOMAS BY l f wfw ATTORNEYS April 2, l957 T. R. THOMAS 2,787,336

LUBRICANT PUMP AND RESERVOIR Filed OCT.. l, 1951 6 Sheets-Sheet 4 "WIT/0 ATTORNEYS April 2, 1957 T. R. THOMAS LUBRICANT PUMP AND RESERVOIR 6 Sheets-Sheet 5 Filed Oct. l, 1951 S RA E mw #N Tl .mm fm wk. Wn IM A .hm M www April 2, 1957 1'. R. THOMAS 2,787,336

LUBRICANT PUMP AND RESERVOIR Filed Oct. l, 1951 6 Sheets-Sheet 6 30a @d r M l df297' A 2298 305 293/ MV 300 L IIIHIII l. f- 1H 4 329 -r 329 320 5?/ 5/9 afa i?? 523 324 INVENTOR THUMAS l?. THOMAS ATTORNEYS United States Patent C LUBRICANT PUMP AND RESERVOIR Thomas R. Thomas, New York, N. Y., assigner to Auto Research Corporation, a corporation of Delaware Application October 1, 1951, Serial No. 249,076 4 Claims. (Cl. 184-27) The present invention relates to a lubrication installation, and it particularly relates to a central source of lubricant supply and pressure for said centralized lubrication installation.

Although not limited thereto, the present invention will be particularly described in its application to a centralized lubrication installation of the high restriction llow metering type, in which the centralized pump is designed to supply a large number of spaced bearings with relatively minute yet accurately proportioned quantities of lubricant.

It is among the objects of the present invention to provide a central lubricant pump for a centralized lubricating system of the character described, in which it is possible by ready manipulation or adjustment of the pump to achieve continuous or intermittent feed or, if desired, various feed pressures.

Another object is to provide a central pump installation which is capable of feeding at high pressure or at low pressure, continuously or intermittently, and which may be utilized to feed bearings requiring high pressure lubrication at desired intervals and also bearings requiring low pressure feed at all times during operation of the mechanism.

Still further objects and advantages will appear in the more detailed description set forth below, it being understood, however, that this more detailed description is given by way -of illustration and explanation only and not by way of limitation, since various changes therein may be made by those skilled in the art without departing from the scope and spirit of the present invention.

In accomplishing the above objects, it has been found most suitable to provide a pump unit consisting of a cover element with a depending gear pump structure.

The cover element is desirably positioned either to cover a reservoir or a pocket or recess in the mechanism serving as a reservoir.

The cover is designed to carry the drive, which may be continuously driven from the mechanism or machine to be lubricated.

The depending pump structure may consist of intermeshing gears suitably fed from a iilter positioned adjacent to the lower part of the reservoir or the lubricant pocket.

Desirably, the depending structure will carry a vertical drive shaft actuated from a horizontal shaft on the cover, and it will also carry mechanisms giving intermittent, continuous or jet feed, as may be desired.

Desirably, the cover also has connections by means of which suitable branch tubing arrangements may be provided to give cyclic, continuous or jet feed to various parts to be so lubricated.

Depending upon the particular mechanism and the type of lubrication that is to be achieved, a drive shaft may be actuated from. a suitable part of the machine to be lubricated and connected in any desired manner or through 'any desired reduction to rotating shaft of the machine.

In one form 'of the invention lthe drive shaft extends Patented Apr. 2, 1957 fice horizontally across the top of the cover of the pump unit and it extends into a gear box positioned on top of the cover. This gear box has Worm and wheel connections by means of which any suitable speed and direction of drive may be obtained depending upon the particular type of gearing utilized. t

The vertical shaft which extends downwardly to the gear pump will not only drive the gear pump but will also drive a valving and cam arrangement which may regulate the cyclic feed.

For example, during operation the lubricant may be continuously discharged from the gear pump through an internal bore system and past a series of valves to an externalconnection upon the cover.

From this connection on the cover a branch distributing system with high restriction outlets may extend to the bearings at only continuous or constant feed of lubricant.

At intervals by operation of Va cam and follower theV lubricant flowing to the continuous feed outlet may be discharged intermittently or periodically to an outlet connection in the cover of the pump unit which is connected to a plurality of bearings only requiring lubricant at predetermined intervals during the cycle of operations.

Itis also desirable, in connection with such a cyclic type of lubricant feed, to have an additional manual control which will permit the cycle to be repeated or carried on for any desired period of time regardless of the position of the control cam and follower. Y

ln addition, there may be provided a jetting feed branched external system which also may be operated manually to assure a substantial flow of lubricant at certain periods during the operation of the machine to selected bearings. Y

To prevent excessive internal lubricant pressures from developing during the jetting Icyclic or manual control operations, a safety valve or safety valves may be pro vided to permit flow of lubricant back to the reservoir.V

may be provided to regulate the ow of lubricant permitting a substantial proportion to by-pass back to the reservoir. It is also possible to provide different types of branch systems which will receive lubricant from the pump at different pressures one line for example being loaded to feed at l0 lbs. pressure while another line may be loaded for a continuous or flood lubricant feed.

In the arrangements described, the gearing which connects the horizontal shaft to the vertical drive shaft extending down to the intermeshing pump gears, is also lubricated by a by-pass from the gears of the pump to the gear box on the cove With the foregoing and other objects in View, the invention consists of the novel construction, combination and 'arrangement of parts as hereinafter more specilically described, and illustrated in the accompanying drawings, wherein s shown an embodiment of the invention,

-but it is to be understood that changes, variations andV modification-s can be resorted to which fall of the claims hereunto appended. t

In the drawings .wherein like reference characters denote corresponding parts throughout the several views:

Fig. l is `a side elevational lView in partial section of a type of pump unit according to the present invention having three distributing lines for cyclic, continuous and jetting feed.

Fig. la is a fragmentary sectional View of jet valve piston lupon enlarged :scale as compared to Fig. l,

Fig. 2 is a side elevational view taken from the line 2-2 of Fig. 1,

Fig. 3 is a side elevational view in parti-al section taken from lthe vline 3--3 of Fig. 1,

within the scope Fig. 4 is a top plan view in partial section taken from the line '4-4 of Fig. l,

Fig. 5 is a transverse vertical sectional view taken upon the line 5-5 of Fig. 1,

Fig. 6 is a schematic layout ofthe lubricator of Figs. 1 to 5 in a `simplified larrangement in which the outlet branches for continuous, cyclic and jetfeed and the manual control buttons for instant and jet feeds are all shown inone view with their associated connection-s.

Fig. 7 is .a side elevational view of the top horizontal drive shaft shown in Figs. 1, 2 and 4 upon about the same scale as Figs. 1, 2 and 4.

Fig. 8 is a top plan view of an alternative drive .shaft assembly showing the use of a flat at the drive end of the :shaft instead of a keyway as is shown in 7.

Fig. 9 is a vertical side elevational view partly in section of the vertical drive shaft by itself removed from the assembly of Figs. 1 to 5, showing the worm ldrive gear yfor the timing or cyclic `system and the tongue arrangement for driving the gear pump.

Fig. l0 `is a vertical side sectional View of the outlet valve assembly to be positioned upon the pump cover'.

Fig. 1:'1 is a side elevational view `similar to Fig. .2 of an alternative construction showing a continuous type pump with one external tubing line.

Fig. 12 is a side elevational view taken upon the line 12-12 of Fig. 111.

F-ig. 13 is a side elevational view of still another alternative embodiment similar to Fig. 12, with two external tubing lines7 one 4a low pressure or flood line and one a lb. or medium pressurefeed line.

Fig. 14 is atop plan view of the pump unit of Fig. 13 taken from the line 14-14 of Fig. v13.

Fig. 15 is a longitudinal sectional view of one type of iiow metering high restriction outlet fitting which may be Iutilized in connection with the ow metering outlets of the tubing system supplied from the pump of Figs. l to 8.

Referring to Figs. 1 to 6, there is shown a cover unit A having a drive mechanism B and a filter unit G and pump unit C.

The pump unit C feeds .an external continuous feed `system E from the internal pipe system K.

It also feeds an external cyclic feed system P from the interna-l tubing system D. ln addition, the lpump may feed an external jetting system N from the internal tubing `system M.

The external jet. system N is controlled bythe jet feed button H. VTo vgive instant feed to the cyclic system P an instant feed button L is provided which will 'assure lubricant feed to the cyclic system P at optionally/desired intervals.

The cover A, as shown in Fig. 4, is provided with bolt openings Y19 which extend through the corners 2i) of the cover A, which serve to clamp the cover A with an asf sociated gasket (not shown) and the pump mechanism yC together with the lfilter unit G to a reservoir or pocket in the machine to be lubricated.

The drive shaft 21 has a keyway 22 which enables connection to a suitable drive from the machine or mechanism being lubricated. The drive shaft 21 extends through the cap or plate Z3 which is held inposition by Athe -bolts or screws 24 upon the enlarged portion 25 of the drive mounting B uponthe cover A.

The drive shaft as shown in Fig. 7, and also as shown in `assembly inFigs. 1 and 4, has the enlarged portion 31, the Vgroove 32, the enlarged portion 33, -the groove 34, the enlarged .portion 35, the reduced diameter portion 36, the enlarged portion 37, and the reduced diameter extension 38.

In the alternative shaft structure as sho-wn in Fig. 8 where-a flat is provided, correspondingly functioning parts vbe-ing indicated by the same numerals which, however, yare primed, the iiat 22 functions the same `asthe keyway 22.

There is provided an enlargement 31f, thegroove 32,

the enlargement 33', the groove 34', `the enlargement 35', the reduced diameter' portion v36', the enlargement 37 and the reduced diameter end portion 38.

The portion 31 of the shaft of Fig. 7, or 31 of the shaft of Fig. 8, is encircled by a recess 27 as shown in the end plate 23.

The portion 31 of the shaft of Fig. 7 or the portion 31' of the shaft of Fig. 8 are encircled by th@ thrust collar 30 and the thrust washer 29. The `lubricant will flow along the bearing vgroove 405 -of Vthe shaft sections 31 or 3l into the space around the thrust collar v30 and then into the bore 406.

The gear box T `receives the gear connections -between the horizontal shaft 21 connected to Vthe external drive and the vertical shaft 51 which extends down to the gear pump C.

The ends 38 and 38 of the shafts 21 and 21 beyond the enlargements 37 and 37' are provided with the worm 4t) having .hub extension '41Qheld.ontheshaftextension 42 by the pin 43.

The worm 40 meshes with the worm wheel 5ft) which is mounted upon the vertical drive `shaftll (see also Fig. 1).

The vertical drive .shaft $51 is shown byitself in Fig. 9 and -is also shown in the assembly in Figs. V1 and 2. fit `will be noted,-as shown by the arrow in Fig. 4, that the vert-ical drive shaft 51 will be driven counter-clockwise by the worm 40, butby changing the worm 40 and the gear 50 `any speed or direction of rotation o f shaft 21 may be achieved.

The worm 40 and the worm wheel 50 turn in the recess 52 inside the cup 53 of the gear box T on the cover A. The space 52 within the cup V53 is Vclosed by the upper cup cover 54 which is clamped down against the top of the cup 53 by the bolts55. The'bolts 55 press the gasket 56 against the top ofthe cup 53 and form a lubricant tight connection.

Rcferringto Figs. l-and 2, it will be noted that the shaft 51 extending down from the cup 53 carries the worm 60 which meshes with the gear 61. The gear 61 is carried on the shaft 62. The shaft 62 extends through the bearing structure 63 and lis connected at its other end to the worm 64.

The wheel or gear 61 is held in position on the shaft 62 Vby the collar 65 and the pin 66.

The bearing structure 63 is carried by -the supporting structure or frame W which has an up-flange 67 bolted at 68 to the underside of the cover A.

The worm 64 on shaft 62 drives thegear 75 Vwhich is carried on the-shaft V76. The shaft 76 has .a bearing lat 77 and `a portion of the -structure or frame W. `Theother end 78 `ofthe-:shaft 76 carries the'cam 7 9 havingtherecess or notch `80.

The recess 80 is designed to engage :the nose S1 of the follower lever 82. The follower lever '821:is.mounted on the pin .or stud 84 and Vheld in place by washer 83 and a cotter pin.

The follower lever 82 has a claw or lifter end 5, which may he clevised, whichts vbelow the threaded lco1lar'86 on the vertical reciprocatory shaft or sleeve 87. The collar is held in position by staking or upsetting the threaded portion of `shaft 87 through vthe :hole A83. Normally the nose 81 of the lever 82 will be riding upon the circumference 8920i thecam 79, which will hold .the collar 86 in lifted position. This will be.doneagainst'the'force of the spring 90.

The spring 90 Yreacts at its ,lower end Lupon v.the collar 91 on the 'shaft 87 Aand atits upper end it .reaetsupon .the collar 92. The spring encircles the rod 93. The shaft 87 is tubular 'as indicated at 100 :to receive the `rod v93 and also the 'mushroom button 17,6.

In 'the position, as Vshown in Fig. 3, 'the lower end .100 of `the shaft87 will press down upon head 5101 ofbutton 1576. The head 1-01 will press down upon I'the'ball check 1112 and force it against the annular valve seat 103. This will-.occurV during :that portion :of ithe rotlattionrof the cam arsasse 79 when the nose 81 is received in the recess 80 of the' cam 79.

However, during most of the rotation of the cam 89 the claw 85 will lift the collar 86 and compress the spring 90 and permit the lubricant to ow freely past the ball check 102.

The shaft 51, as shown in Fig. 9, will continue beyond the wor'm 60. The end of the shaft below the worm 60 has a tongue in slot connection 150. Below the gear there will be a sleeve 151 and the extension 152.

The sleeve 151 will terminate in the tongue 153, which will lit into and drive the slot 107 in the gear 105 (see Fig. The llister slot 107 will be positioned in the stud shaft 106 integrally connected with the gear 105 of the gear pump.

The gear 105 will mesh with the gear'108 on the shaft 109, which bears within the recess 110 in the lower part of the supporting frame structure W.

The intermeshing pump gears 105 and 108 are received in the double circular recess 104 in the plate 111 V(see Fig. 3).

The plate 111 is clamped between the top 112 of the lter cup 113 and the base 115 of the depending structure W. The bolts Z114 extend through the plate 111 and screw into recesses in the ange 115 to the bottom of the supporting frame structure W. The heads of the bolts 114 are received in recesses 116.

The opening 117 in the filter cup 113 receives the wire screens 118 provided with the spacer projections 119 and also the strainer material 120.

The strainer material l120 is' held in position by a peripheral ring 121 and the locking wire 122.

The lubricant passes up through the strainer 120, .the screens 118, to one side of the intermeshing gears 105 and 108 forming the gear pump.

As the lubricant is drawn up through the strainer 120 and through the screens 118 by the gears 105 and 108, it will be discharged through the interconnecting counterbores 130 and Vertical passageway 123, which counterbores and passageway are all located in the pump chamber plate 111 (see particularly Fig. 1).

From the vertical drill passageway. 123 the lubricant under pressure discharged from the gears 105 and 108 will enter the valve chamber 124 (see Fig. 1).

The valve piston unit X, positioned in the upper portion of the valve chamber 124, will be normally held in the position shown in Fig. lby the spring 203 unless it is depressed by the manually controlled jetting button H.

In this normal or up position, as shown in Fig. 1, the lubricant ows from the chamber 124 through the oblique passageway 127 to the valve chamber 128.

The lubricant in the chamber 128 will be subjected to the loading pressure of the spring seated ball check valve 129 which, as shown, maintains a pre-set back pressure of about 13 lbs. per sq. inch in the passageways 130 and 123, the valve chamber 124, the passageway 127 and the valve chamber 12S.

The lubricant under pressure in the valve chamber 128 will then flow through the connecting passageway 132 (see Figs. 2 and 5) to the internal tubing system K, which in turn leads to the external tubing system E through the coupling 155.

Through the coupling 155 to the external system E lubricant will be fed continuously throughout the operation of the pump of Figs. l to 6, and the system E is therefore termed the continuous feed system. This feed to system E is only discontinued upon operation of button H.

ln respect to the cyclic feed system having the internal tubing D and the external tubing P, any lubricant which has bypassed the loading valve 129, as shown in Fig. 1, will ow into the space 133 below the timing valve seat 103. The lubricant `from chamber or space 133 may flow through seat 103, around ball 102 and through bore 210 to tube 136. I

When the notch 80 of the continuously rotating cam 79 aligns itself with the nose 81 of the cam follower 82A, the left hand portion of the cam follower 82 is free to drop. This allows the shaft 87 having the tubular section to bear against the button head 101, seating the valve ball 102 against the valve seat 103 under the load of the timing valve spring 90. The lubricant in chamber 133 is now diverted through the connecting passageway 134 (see Fig. 5) to the tubing D which is connected to the outlet check valve 135 (see Figs. l and 10) The outlet check valve 135 is mounted on the underside of the cover plate A.

Referring to the outlet check Valve 135, as shown in Fig. v l0, it willl be noted that it has a ball check 157 seated by the spring 158, and that the direoiton of flow is indicated bythe arrow 159.

From the outlet check valve 135 (see Fig. 1), there is a direct connection to the external tubing system leading to the cyclic line P, which is shown diagrammatically in Fig. 6 and also shown in Fig. 1, at the tapped recess is the depression coupling connection 160.

Discharge of lubricant into the interior cyclic tubing system D and the exterior cyclic tubing system P will only take place during the period that the cam nose 81 is in the notch 80 of the cam 79, Fig. 3. As the cam 79 continues to rotate, the cam nose will emerge from the notch 80 and willl ride on the circumference 89 of the cam.

During this longer interval, the cam follower end 85 keeps the valve shaft S7 olf of the but-ton head 101, thus permitting the ball 102 to lloat olf of its seat 103.

The lubricant from the chamber 133 will now llow through the seat 103, around the ball 102 and through `a drilled passageway 210 shown in Fig. l, to the vertical tube 136.

rIlhe upper end of this tube 136 connects tothe oor or lower portion 52 of the gear chamber 53, Fig. 4. Lubricant flowing from tube 136 will lilll the chamber 53 until it reaches the level of the hole 137 located in a raised boss.

This lubricant lubricates the gearing 40-50 -in the chamber T and the drive shaft 21.

There is a longitudinal groove 405 located in the bore of the bearing 28 which conducts a portion of the lubricant to the thrust washer 29 and the thrust collar 30 of the shaft and excess lubricant returns through the angular drain hole 406. Overow of the lubricant into holle 137 is'conducted by suitable grooving and drillings to lubrica-te the vertical shaft 51 and the various shafts and thrust surfaces of the reduction gearing driving the cam 79.

A hole 138 located in a boss of higher elevation than hole 137 acts as a safety overow means, should the level rise to that height in the gear chamber. The hole 138 drains directly back to the reservoir.

Associated with the cyclic feed system, consisting `of the interna-l tubing D and the external tubing P, is an instant feed or manually operated feed arrangement, which permits lubricant to be fed through the internal tube D and the external tube P regardless `of the relative position of the cam notch 80 and the follower nose 81.

This device is operated through the manual push button arrangement or instant feed button L. This instant feed button L is shown in Figs. l and 4 in outside view and in Fig. 3 in side sectional view and also in Fig. 6.

The external push button element L, best shown in Fig. 3, is normally held in elevated position by the spring 139 which is received in the recess 165 of the sleeve 166. Tlhe sleeve 166 is mounted by the shoulder 167 upon the underface of the cover, and it projects through t-he opening 168 in the cover. The spring reacts against the bottom of the cup or sleeve 166 and also against the nipple 169 on the bottom interior of the button 170. The nipple 169 is press-fitted upon the upper end 171 of the push rod 93. The rod 93 carries the pin 172 which acts as a stop against the bottom of the cup 166.

The -rod 93 extends down through the coil spring 90 '7 and also through the valve shaft 87. The rod 93 termi nates as indicated at 175 "above the extension or mushroom button 176 projecting upwardly from the head 101 which contacts the top of the ball 'check 102.

lf the button L is depressed it will move the rod 93 downwardly and the lower end 175 of the rod shall contact the stud 176 and press the head 101 against the ball check 102.

As a result, the ball check 102 will be pressed against the annular seat 103 and the lubricant pressure in the chamber 133 will be diverted into the cyclic branch D from whence it will ilow into the external line or tubing P. This flow will ycontinue as long and as frequently as the button L is depressed regardless of the position of the cam notch 80.

The externally threaded collar S6 of Figs. l, 3 and 6 may be adjusted in relation to cam follower tip 35 for initial setting of the pump Iarrangement as shown to assure proper cyclic delivery.

The jet feed branch with the internal tubing M and the external tubing N is only operated by manual actuation of the push button H. The push button -H is shown in side view in Figs. 2, 3 and 6 and in section in Fig. l.

The button or cup 130 is mounted at its inverted base 181 to the reduced end portion 182 of the yrod 133. The rod 183 slides through the sleeve 184, which is mounted by enlargement 185 against the bottom of the cover 54 of the gear box T.

The rod is provided with a spring ring 186, to keep it in place, below the sleeve 184. The rod 183 abuts the reduced upper portion 192 of jetting rod 191 which extends through the opening 187 in the lower part or bottom portion 103 of the gear box T.

The shoulder 189 of rod 191 carries the stop ring 190 which abuts the bottom of the portion 188 0f the gear box T. The ilower end of rod 191 carries the jet valve arrangement X which is reciprocated within the chamber 193.

The jet valve arrangement X has an upper safety valve unit 196 and a lower cross valve unit 126. The safety valve unit has a ball check 194 with a spring 195 reacting against the upper valve unit 196 having a cen.- tral passageway 197. The central passageway 197 empties into the chamber 198. The chamber 198 feeds the transverse passages 199 which permit the lubricant to flow back into the reservoir.

The lower portion 126 of the jet valve X has va central axial passage 200 and a cross passage 201 communicating therewith. The cross passage 201 commun-icates with the annular groove 141 `in the exterior of the lower portion of the jetting valve X.

In the position shown, the transverse passage 142 in the valve block Y will be cut off from the passage 201 and the sleeve extension 202 will be in upper position with the spring 203 reacting against and pressing upwardly upon the jetting valve X.

When the button H and the jet valve X are depressed in the chamber 193 until the extension 202 contacts the pump gear chamber plate 111, the passageways 127 and 132 opening into the lower portion 124 will be cut off by the sleeve extension 202. The annular groove 141 will then be in communication with the drilled passageway 142 shown in Figs. l `and 5.

As a result, the total discharge from the gears 105 and S will llow from the passageway 123 into the passageway 142, the internal tubing M and the external connection N.

The connection between the internal line M and external line N are made by means of the coupling connections 205 and 206.

In order to prevent excessive internal lubricant pressure from developing during the jetting, cyclic or instant feed operations, the pre-set blow-off safety valve is incorporated in the upper part of the jet valve X.

This safety valve action is accomplished by lifting the ball check 194 against the spring 195 when, for example,"

the pressure exceeds 270 lbs. per square inch. I

When this high external pressure vdevelops the'lubricant will pass the ball check 194 through the passageway 199 and back into the reservoir. i Y

The loading valve 129, which is positionedin the chamber 128, is set, for example, at 13 lbs. so that lubricant will not pass from chamber 123 to chamber 133 until the pressure of 13 lbs. is reached. When this occurs the lubricant will pass into the chamber 133.

lf the button L is not depressed and the mushroom head 101 is lifted from the ball check 102, the lubricant will then 'llow through the bore 210 into the vertical tube 136 to lubricate the gear box T. However, if the button L is depressed, or if the nose 81 is in the notch 80, as shown in Fig. 3, the ball check 102 will .be closed against the seat 103. Then the lubricant will tlow from the chamber 133 through side hole 134 into the tubing D through thc outlet check valve into the cyclioline P.

It is thus apparent that the embodiment of Figs. 1 to 6 has provided a reliable pump construction which may be readily adapted to give continuous, cyclic or jet feed in different systems or lines and the pump is provided with manual controls such as the button H or button L respectively giving instant or jet feed control.

The loading valve 129, the cyclic check valve 102, the jetting valve X and the safety blowoff valve 194 will control the operation in the manner desired.

In the embodiment of Figs. l1 and l2, the lubricator shown is of the constant feed type deliveringV lubricant when the pump is operating.

As shown in Figs. 1l and l2, the drive shaft 225 has a bearing in the structure 226 similar to that shown in Figs. l to 6, and it drives the vertical shaft 227 through the gear box 22S. The gear box 228 is mounted upon the cover 229.

The depending pump unit has afilter or strainer element 230 and a pump plate 231 carrying the gears.

The valve unit 232 is mounted by the base plate 233 upon the pump plate 231.

The lubricant passes from the gears by means of the vertical drill passageway 234 into the downwardly oblique passageway 235.

This passageway 235 opens at 236 into the chamber 237.

The chamber 237 is threaded at 233 and it is seated by the threaded portion 239 of the high restriction flow metering fitting 240 which is of the same function as the flow metering unit of Fig. l5. v

The `lubricant from thek chamber 237 will pass through the meter unit 240 into the chamber 241. From the chamber 241 it will pass into a horizontal bore 242. From the bore 242 it flows into the vertical tube 243.

The tube 243 receives a filler pin 244 which reduces its void and permits more rapid filling and discharge of lubricant therefrom.

The upper end of the tube 243 is connected to the Sleeve 245 in a lubricant tight fashion by the gasket 246. The sleeve 245 has the side openings 247 and the top opening 248 permitting lubricant to flow into the gear box or chamber 228.

This lubricant will lubricate the main drive shaft 225, the vertical drive shaft 227 and the intermediate gearing in the box T.

Additional lubricant will liow from the chamber 237 through the bore or mill passageway 249 to the vertical pocket or chamber 250. This pocket 250 is plugged at its upper end by the pressed-in needle valve body 251.

The needle valve adiustments 252 wiil regulate the flow out of the chamber 250 back into the reservoir. The

residual lubricant which does not by-pass through the needle valve 251 and which does not pass through the ilow restriction metering fitting 240, will cw outwardly through the horizontal passageway 253. This passageway 253 is connected by the compression coupling 254 to the tube 255. The tube 255 leads to the T adapter 256 which arenas@ is connected to the outlet valve 257 and the safety blowoff valve 258.

The lubricant entering the adapter 256 will normally flow through the outlet valve 257 to an external tubing system which is connected to the outlet tapped recess 259.

The blow-oli' valve 258 is normally set for about 270 lbs. per sq. inch, and if the pressure exceeds this amount the lubricant will be by-passed into the reservoir.

The pump unit as shown in Figs. 11 and 12 gives a substantially continuous feed while the machine is Working and driving the shaft 225.

The lubricant which passes through the liow metering restriction 240 is used to lubricate various associated parts in and about the pump unit. The shaft 260 may be used for regulating the needle valve and will be accessible from the interior of the gear box T.

In the embodiment shown in Figs. 13 and 14, the lubricator unit is of the constant feed type with two ex ternal tubing lines. As shown in Figs. 13 and 14 the horizontal drive shaft 280 has a bearing in the bearing block 281 and extends into the gear box 282 with the cover 283.

The gear box 282 is mounted upon the main cover for the unit 284. The shaft 280 drives the vertical shaft 285 through gearing in the box 282. The lubricant is picked up through the strainer unit 286 and passes into the gear plate 284 and is then regulated in the valve block 288. The valve block 288 is mounted at its base 289 to the pump plate 284,

The lubricant from the pump liows into the chamber 290 and it may liow out through the outlet 291, the bore 292 to the tubing 293. The tubing 293 is connected to the 13 lb. outlet check valve 294 which will regulate the pressure in the chamber 290.

There is also a check valve 295 which is screwed at 296 directly into the upper portion of the chamber 290.

This outlet check valve 295 connects to the tubingV 297 which leads tothe outlet adapter 298 in the cover 284. This will feed an external system with lubricant pressure under lbs. per square inch from the chamber 299.

The flood line which is connected to the outlet connection from the outlet valve 294 and the socket 299 will flood lubricant into a distributing system without flow metering fittings of the type shown in Fig. 15.

The lubricant will normally flow into the chamber 290 through the vertical bore 304, the oblique bore 305, the chamber 306 and the middle passageway 307. From the chamber 306 a metered portion of lubricant may flow from the fitting 300 lthrough the bore 308 into the vertical tube 301 and past the outlet fitting 302.

The ller rod 303 will nearly fill the tube 301 so as to permit more rapid filling and discharge of lubricant into gear box 282 to lubricate drive shaft 280 and gear reduction.

The lubricant metering fitting as shown in Fig. 15 may have a body 315 with threaded ends 316 and 317. It may also take the form as shown at 300 in Fig. 13.

It has a central passageway 318 substantially completely lled by a pin 319 which gives a high iiow resisting effect or obstructing elect. The inlet end at 316 receives :a strainer 320 with a backing screen 321. The outlet end has an annular valve seat element 322 upon which is pressed the plastic polymerzed valve face 323 and the backing plate 324. The backing plate 324 is acted upon by a coil spring 325 held in position by the cup shaped retainer 326.

The pipe threaded end 317 may be screwed into a bearing.

The inlet end 316 receives a compression coupling nut 327, a double tapered compression sleeve 328, a bevel sleeve 329 which form a lubricant tight connection in respect to the tube 330. The tube 330 may form a terminal of a lubricant distributing system.

' As many changes could be made in the above lubrication and many widely different embodiments of this invention could be made without departing from the scope of the claims, it is intended that a'll matter contained in the above description shall be interpreted as illustrative and not in a limiting sense.

Having now particularly ascertained and described the nature of the invention, and in what manner the same is to be performed, what s claimed is:

1. In a central lubricant gear pump-reservoir combination, a reciprocable valve to permit a high flow jet supply of lubricant to 4a bearing, said pump being of the type having a plurality of intermeshing gears, with inlet and outlet ow passageways and a check valve controlled return passageway back to the reservoir from said outlet ow passageway and an outlet tubing connection from said outlet ow passageway, said reciprocable valve having a reciprocable bored member Ito connect the outlet ow passageway to the outlet tubing connection and to the return flow passageway.

2. The arrangement of claim l, said bored member including the check valve to permit part yoi? the lubricant to flow lto the return passageway when the bored member is connecting the outlet flow passageway and the outlet tubing connection.

3. The arrangement of claim 1, said reciprocable valve having a manual actuator to change its position Ito connect the outlet tubing connection and the outlet flow passageway and having a return spring lto return it after said manual actuation.

4. The arrangement of claim 1, said reciprocable valve having 1an actuating connecting rod and said rod having a. manually actuated push member outside of said combination.

Johnson Feb. l1, 1941 Kocher Apr. 7, 1942

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