US2867481A - Lubrication system - Google Patents

Description

Jan.v6, 1959 L. HoRNBosTEL `2,867;481

` LUBRICATION SYSTEM Filed Oct. 17, 1955 5 Sheets-Sheet'z n LLOYD HQRNBosTEL Jan. 6, 1959 l.. HoRNBosTl-:L 2,867,481

LUBRICATION SYSTEM Filed 001'.. 17, 1955 5 Sheets-Sheet 3 TVE1-JEF L oYD HonNB osTEL.

Jan. 6, 1959 l.. HoRNBosTEL 2,867,481

l LUBRICATION SYSTEM Filed oct. 17, 1955 5 sheets-sheet 4 Jan. 6, 1959 L. HORNBo'sTEL 2,867,481

LUBRICA'TION SYSTEM Filed oct. 17, 1955 5 sheets-sheet 5 LLOYD HORN BosTEL 17E/ai we 77W W1/@fw .5.

grail LUBRICATIN SYSTEM Lloyd Hornhostel, Beloit, Wis., assigner to Beloit Iron Works, Beloit, `Wis., a corporation of Wisconsin Application Getober 17, 1955, Serial No. 540,904

8 Claims. (Ci. 308-187) The instant invention relates to an improved lubrication system, and more particularly, an improved lubrication arrangement for use in heavy duty machines such as paper lmaking machines.

Although the instant invention may 'have utility in a number of other fields, it is used to particular advantage in paper making machines or similar heavy duty machines, and the instant invention will be ldescribed primarily with respect to this use. In paper machines the bearings are heavily 'loaded and for this reason they are provided with continuous lubrication, having the oil flow into the bearings and then back out through a main recovery header to the filter and an oil pump (usually positioned in the basement) from which the loil is pumped back up into a main header to supply ea-ch of .the ybearings, gear trains, etc. The flow into and through the bearings is essentially gravity flow and the amount of lubricant flowing into the bearings is ycontrolled by a throttle valve and a ysight feed so that the operator may observe how much oil is being ted to the bearing. This has been .the procedure employed for a number of years in paper making machines, steel mills, and the like 'heavy duty machines, which usually employ lto a substantial extent the `sor-called barrel type roller bearings. Because of the rather complex arrangement in paper machines, it is often difiicult for the operators to obtain access to many of the bearings in the machine and this gives rise to operational hazards, lbecause of pos-sible plugging in the oil lines, etc. 'In most instances the bearings are `so housed that a closed high pressure oil circulating system through the bearings is not practical. Accordingly, essentially a gravity feed of "lubricant through the Ibearings and into the oil return header has been employed in the prior art, with sight `feeding of the oil into the bearing yusing a throttle valve.

Although the oil system is equipped with adequate filter means, there is always a certain amount of material which accumulates in the oil system that may readily cause plugging at valves or similar locations in the system whereat Ilittle or no pressure is involved or whereat flow of oil is intermittently cut off or throttled very substantially. In view of this, the operation of paper making machines lhas been made quite difiicult for a number of years, although no appreciable changes in the overall lubricating system have been `suggested or used during this period of time.

The instant invention resides in the embodiment of certain novel concepts relating to the feeding of lubricant to such bearing systems. For one thing, the instant invention contemplates the elimination of sight feeding by the use of an orifice for feeding lubricant under pressure and by continuously wiping the orifice during this `operation so as to prevent plugging thereof. IEssentially, one of the bearing elements carries `a resiliently urged plunger against another element rotating relative thereto, and the plunger is provided with an orifice for feeding lubricant which is urged against the rotating surface to effect continual wiping of the orifice.

ICC

It is, therefore, an important object of the instant invention to provide an improved lubricating system for paper machines -orthe like.

Ilt is a further object of the instant invention to provide an improved lubricating system for -heavy duty bearings whereby lubricant under pressure is 'metered through an orifice into the bearing while constant wiping of the orifice takes place, so as to obtain an improved lubrication of the bearing.

A further object of the instant invention is to provide a `lubrication system comprising a bearing including a pair of relatively rotatable elements `dening a housing and a third rotatable element Within the housing engaging both of said pair of elements, a conduit carried by one of said pair of elements and engaging another of said elements relatively rotatableithereto to define therewith an orifice, and means feeding lubricant through said or-ifice and into said housing.

Other and further objects, features and advantages of the present invention will become apparent .to those skilled in the art from the `following detailed disclosure thereof and the drawings attached hereto and made a part hereof.

'On the drawings:

Figure l is essentially a diagrammatic -top plan View yof a portion of a paper machine showing ythe lubricant circulating system;

Figure 2 is a fragmentary detail view of a ybearing assembly embodying the instant invention, shown in elevation with parts shown in section and parts broken away;

Figure 3 is a view in section taken substantially along the line III-Hl of Figure 2, Awith parts shown in section and par-ts broken away;

Figure 4 is a fragmentary sectional elevational view of a second bearing assemblyembodying the instant invention;

'Figure 5 is a fragmentary ydetail view taken substantially along the line V-V of Figure 4;

Figure V6 is a detail Isectional elevational view cornparable to Figure 4 but showing a Athird embodiment of the instant invention;

Figure 7 is a fragmentary detail view taken substantially along the line VII-V-Ilyof yFigure 6;

Figure 8 is a sectional elevational View of a fourth embodiment of the instant invention, showing a View lthereof comparable to the View of Figure 6 of lthe third embodiment of the instant invention;

yFigure 9 -is a fragmentary detail view taken substantially along the line lX.-1X of Figure 8;

Figure l0 is a sectional elevational View, in detail, showing a fifth embodiment of the instant invention;

Figure ll is adetail sectional `View taken substantially along the line X11-XI `of Figure l0; and

Figure 12 is a fragmentary detail view taken substantially along the line XII-XII Vof Figure 10.

As shown on the drawings:

In Figure l the paper machine ifi, which is shown only partially in plan View, comprises front 11a and rear 11b upright frames having extending therebetween in succession a press roll 12 for the first press, a press roll i3 for the second press, a press roll 14 for the third press, and successive dryer rolls l5, 16, etc. As will be appreciated, the entire machine 1li is mounted substantially between the frames 11a` and 11b from the head box to the calender, but the mounting generally for heavy duty rolls and bearings is similar and only the portion of the paper machine shown in Figure l is required to show the general concepts of the invention.

As will be noted, the press roll 12 has front andA rear bearings 12a and 12b rotatably supporting the same .and carried by the frames 11a and 11b, respectively, In the `through a pump 2 1 lubricant is pumped to the a suitable storage tank 2t? K and filter 22 into a main lubricant supply header 23, from which the lubricant feeds through inlet lines 24a and 2412 into the bearings 12a and 12b, rsepectlvely. In the prior art, lubricantV was fed into the bearings 12a and 12b by sight feeding using a manually controlled throttle valve to reduce the pressure of the lubricant in the header 23 to substantiallylatmospherxc pressure to permit substantial gravity ow through the bear1ngs'12a and 12b and out the exit lines 25a and 25h, respectively into the return header 26 which feed back'vinto the supply tank 20. As the arrows in the draw'- `ing mdlcate, comparable lubricant feed and return lines are provided for the front and rear bearings 13a and 13b lof the roll 13, and comparable bearings for the remaining rolls. Heretofore, sight feeding was employed using a throttle valve in, for example, the inletV line 24a to effect the necessary pressure reduction from the lubricant pressure in the main header 23 and to permit suitable flow of lubricant to the bearing 12a.

a In the instant invention, an entirely different lubrication system is employed and this is shown in the first described embodiment of the instant invention, indicated generally by the reference numeral 50 in Figure 2. Referring to Figures 2 and 3, it will be noted that a roll shaft 51 (only the upper half of which is shown) corotatably mounts an inner bearing race element in the form of a sleeve 52 corotatably connected to the shaft 51 by a key 23 and having suitable bearing race tracks or grooves 52a and 52b formed therein. A non-rotatable outer bearingrace element 54 defines with the inner race element 52 a housing, wherein the outer race element S4 provides a pair of bearing race tracks 54a and 54b opposing the corresponding inner race tracks 52a and 52b. A cage 55 carrying a plurality of rotary bearing membersor rollers 56a, 56b, etc. is positioned between the inner and outer elements 52 and 54 in the customary manner. Actually, there are two sets of rollers or rotary bearing members here shown, the roller 56a of the first set being shown in the tracks 52a and 54a and the roller 56b in the second set being shown in the tracks 52b and 54h. In each set there are, of course, a number of rollers 56a or 56b which are peripherally spaced by outwardly extending arms 55a` and 5511 on the cage 55. The two sets of rollers areaxially spaced and maintained in such axial spacing by the inner and outer bearing races S2a-54a and 52b-541), respectively.

Other conventional features of the bearing assembly l) include a felt seal 57 retained by a washer 58 in the outer element 54 for affording a seal between the outer element 54 and the inner element 52; and a second felt seal 59 retained by a washer 60 for the same purpose at the opposite end of the bearing assembly Sil. Also, a grease seal 61 carried by the outer element 54. cooperates with a grease seal 62 carried by the inner element 52 within the housing, and on the opposite side a grease seal 63 carried by the outer element 54 cooperates with the grease seal 64 carried by the inner element 52 in the usual manner. The foregoing structural features of the bearing assembly 50 are well understood by those skilled in the art and need not be further described in detail.

An oil inlet aperture 65 at the top of the housing 59 is also customarily provided with internal threads 65a at the mouth thereof for receiving in threaded engagement an oil inlet line (the end 65b of which is shown in position). Heretofore, however, the oil fiowed through the inlet aperture 65 at substantially atmospheric pressure and passed on through the bearing housing 50 substantially by gravity flow and theV oil also passed onto the return lead line h (of Figure 1) through a suitable aperture in the bearing 50, preferably an aperture (not overall lubricating system, bearing 12a and 12b from shown) at the lower portion of the bearing assembly Sii.

In the practice of the instant invention, a sleeve 67 is held against axial movement in the oil inlet aperture 65,

.4 as by shoulders C. The sleeve 67 has annular inwardly turned shoulders 67a at the rear or upward portion thereof and a spring or comparable resilient means 68 is urged against the shoulder 67a. Within the sleeve 67 there is positioned for axial movement a plunger 69 (in the form of a concentric sleeve) which abuts against the spring 68 and is urged downwardly by the spring 68.

The spring 68 resiliently urges the plunger 69 against a rotating circumferential surface of the cage element S5. As will be seen, the cage element 55 defines a shallow groove 74B which is annular or circumferential and which is continuously opposed to the mouth 69a of the plunger 69. Actually, the cage element 55 is made up of two symmetrical portions which cooperate to define the groove 70 along contiguous faces thereof, but the cage element 55 could be an integral unit. In the instant embodiment lubricant flows into the groove 70 and then over the top of the cage element 55 and also to an appreciable but controlled extent between the contiguous faces of the cage portions and then outwardly 'toward the roller 56a and the roller 56b between the cage element 55 and the close running contiguous face portion 52e of the inner race element 52. This provides for metered flow of lubricating oil into the housing. In fact, the plunger mouth 69a and the groove 70 cooperate to define a flow orifice which is so restricted that lubricant under pressure fed into the aperture 65 and through the sleeve 67 and plunger 69 is reduced substantially in pressure and a metered or controlled amount of the lubricant flows into the housing. As has been mentioned, bearing housings of this size Iare not ordinarily provided with seals which will withstand extremely high pressures in the lubricating oil retained within the housing. Instead, essentially gravity flow of lubricant through the bearing is most practical. In this instance, lubricant is fed under pressure down to the orifice defined by the plunger mouth 69a and the groove 70 and there, with constant wiping between the elements 69 and 55, the orifice defined therebetween effects an appreciable pressure drop in the lubricant. Because the orifice defining members 69 and '55 rotate relative to each other, there is a constant wiping action at the orifice and any tendency to cause plugging at this point because of impurities in the oil is substantially avoided. However, it has been found to be further advantageous to provide the rotating element 55, or the groove 70 therein, with a -recess (best shown in Figure 3) indicated by the reference numeral 71 which is substantially greater in depth than the shallow groove 70 but is limited in the peripheral dimension of the groove 70, so as to permit additional flushing of the plunger mouth 67a each time the recess 70 is moved opposite this lubricant inlet aperture 69a or plunger mouth 69a. The recess 71 can be used to additional advantage if it is desired to employ one or a plurality of such recesses in the groove at spacedV locations to receive predetermined amounts of lubricant, because such recesses 71 can be used to effectively meter lubricant into the housing. In other words, each time the recess 71 passes the plunger mouth 69a an amount of lubricant substantially equal to the volume of the recess 71 is immediately pumped into the recess 71 and thence into the housing while only a relatively limited amount of lubricant may be continuously pumped into the housing through the groove 70. This provides for an additional control element in the metering of the lubricant into the housing and also provides for repeated flushing of the plunger mouth 69a.

Referring now to Figures 4 and 5 which show a second embodiment 10G of the invention, it will be appreciated that only the essential features lof the bearing assembly are shown in these views and the associated conventional housing features shown in Figure 2 have been omitted. In this respect, it should be noted that Figure 2 shows a pair of relatively rotatable elements, one of which elements includes the shaft 51 and the lsleeve 52 col'otatably mounted thereon and the other of 'which elements includes the overall stationary housing 54 which includes within its structure the bearing track-defining annular member 5411. The third rotatable element within the housing dened by the rst two mentioned rotatable elements includes the rollers `5611, 56b as well as the cage 55. In the embodiment 50 of Figures 2 and 3, the groove 70 opposing the plunger mouth or conduit 6911 is carried by the third rotatable element within the housing which engages both of the first mentioned pair of rotatable elements, which in this case is the cage 55.

As will be seen, in the embodiment 100 of Figures 4 yand 5 a different arrangement is provided including inside 101, middle 102 and outside 103 concentric relatively rotatable elements defining a bearing. The inside member 101 comprises a centrally located annular member 104 spacing apart a pair of annular members 105 and 106 which provide bearing tracks 10511 and 10611 on the outer peripheral faces thereof. The annular members 104, 105 and 106 are all corotatably mounted on a shaft 107 in the usual manner.

The middle rotatable element 102 is defined by a first series of rollers 10311 (only one of which is shown) carried by a cage 10911 and a second series of rollers 108b (only one of which is shown) carried by a suitable cage 109b. The outside rotatable element 103 comprises a housing portion shown only partially at 110 and an annular race element 111 presenting on its inner periphery a pair of tracks 111a and 11111, opposing the tracks 10511 and 10611, respectively, and the opposed tracks 10511 and 11111 mount therebetween the roller series 10811, while the opposed tracks 10611 and 11111 mount therebetween the roller series 108b. The foregoing features of the assembly 100 are conventional. A suitable aperture 112 is provided in the housing element 110 for supplying lubricating oil through the race element 111 and between the inner 101, middle 102 and outer 103 bearing elements. The aperture or conduit 112 is provided with shoulder portions 11211 against which abut a sleeve 113. The sleeve 113 is also provided with shoulders 11311 against which abut a spring 114 urging resiliently (downwardly) a plunger 115. The plunger 115 is in the form of a hollow sleeve so that flow of lubricating oil from the main conduit 112 through the sleeve element 113, the spring 114 and the plunger 115 down to the mouth 11511 of the plunger is permitted. The spring 114 urges the plunger 115 downwardly against a rotating surface 10411 of the annular member 104, which is actually an annular projection on the shaft 107 as indicated in Figure 5. The member 104 is provided with a circumferential groove 1041) which is aligned to continuously oppose the mouth 11511 of the plunger 115 during rotary movement of the member 104. The mouth of the plunger 115 cooperates with the groove 104b to define an orifice which controls the flow of lubricant into the bearing assembly 100. The lubricant ows over the circumferential surface 10411 and down onto the bearings (or down to the bottom of the bearing assembly 100 to form a pool of liquid lubricant through which the rotary members must pass). At the restricted orifice between the groove 104]) and the aperture 11511 a pressure drop in the lubricant system is effected so as to obtain substantially atmospheric pressure within the bearing assembly 100, although relatively high pressure can be maintained in the lubricating system feeding the orifice. It will also be noted that the groove 104b is provided with a local recessed portion 116 which is `a drilled hole that is aligned with the mouth 11511 of the plunger 115 once for each rotation of the element 104; and each time the recess 116 is aligned with the plunger mouth 11511 a surge of lubricating oil into the recess 116 is permitted so as to flush out the mouth 11511. Continual wiping between the mouth 11511 and the circum ferential surface of the rotary member 104 serves to 5 keep the plunger mouth 11511 open, but the recess 116 serves additionally in this respect to vassure repeated thorough flushings of the plunger mouth 11511. As mentioned previously, the recess 116, or a plurality thereof peripherally spaced, may serve as a metering device for rnetering a given amount of lubricant into the system for each revolution of the element 104. The spring 114 urging the plunger against the circumferential surface of the rotary member 104 assures uniformity of the orifice size notwithstanding possible wear at the plunger mouth k1151/. The plunger 115 is preferably made of a soft metal.

As previously indicated, Figures 2 and 3 show an arrangement 50 comprising'a rotatable inner bearing race element 5211, 52h, a non-rotatable outer bearing race 'velement 5411, a cage 55 carrying a plurality of rotary bearing members 56a, tbrpositioned between the inner 5211, 52h and outer 5411 elements,l and a plunger 69 having an axial bore connected to a source of lubricant carried by the outer element 5411 and resiliently urged against the cage 55 defining therewith an orifice feeding lubricant into the assembly 50. In contrast, in Figures 4 and 5 the cage portion is split into two elements 10911 and 109b that are spaced from each other and the plunger 115 passes therebetween and is resiliently urged against the inner bearing element 104 which is, of course, provided with an annular groove 10411. In Figures 6 and 7 there is shown still another assembly wherein a plunger 151 is carried by anon-rotating housing member 152, but is urged against the rotating shaft 153 and spaced from the bearing race elements per se.

In Figures 6 and 7, there is shown an assembly 150 that includes a first rotary element in the form of the shaft 153 corotatably mounting an inner race element 154 presenting axially spaced roller tracks 15411 and 154b. The race element 154 abuts a shoulder 153 on the shaft 150 and is retained in position by means of a locking ring 154 and spacer 155 in the customary manner. The housing element 152 is actually a non-rotatable outer bearing member which mounts an annular outer bearing race element 156 which is retained in position against a shoulder 15211 in the housing by a suitable retaining ring 157 and which provides on the inner periphery thereof roller tracks 15611 and 15611 which are opposed to the tracks 15411 and 154b, respectively. A first series of rollers 15811 is positioned between the tracks 15411 and 15611 and a second set of rollers 15811 is positioned between the tracks 154b and 156]; in the customary manner.

The housing 152 threadedly receives an apertured plug 159 which connects to a source of lubricant under pressure (not shown) for feeding the same into the housing 152. An axially movable plunger 151 is carried in the housing beneath the plug 159 and isresiliently urged downwardly by a spring 160 which abuts the bottom of the plug 159 and a shoulder portion 15111 in the axially movable plunger 151. The plunger 151 has an axial bore 151i: which permits the liow of lubricant through the apertured plug 159 and through the plunger 151 against the rotating shaft 153. The shaft 153 is pro- 4 vided with a groove 153b which continuously opposes the axial bore 151b of the plunger 151 as the shaft 153 rotates so as to define with the axial bore 151b a restricted orifice limiting the ow of lubricant into the housing 152. As is also shown, the groove 15311 is provided with the recess 161 in the form of a drilled hole of predetermined size for receiving a metered amount of lubricant each time the recess 161 is moved into opposition with the axial bore 151b. The recess 161 also provides for repeated ushings of the axial bore 151b, as hereinbefore described.

In the embodiments 50, 100 and 150 hereinbefore described, it will be noted that the annular groove in each case is provided on a circumferential surface of a rotary part. It is distinctly advantageous to employ the groove on the rotary part rather than on a non-rotary part, so

fthat lubricantmay be Vpiped to a plunger carried by the lnon-rotary part, althoughit is not impossible to make a lubricant connection to a rotary part so as to reverse the positioning of the elements herein. Also, it is not necessary to employ a groove on a peripheral surface of either a rotary or non-rotary element, and instead an .annular groove may be provided at the end face of one of the elements, as shown in Figures 8 and 9.

Referring to Figures Sand 9, Vit willV be seen that the assembly )Y shown therein comprises an inside rotary element 291 which includes a rotatable shaft 292 carrying an annular bearing race element 203 clamped in position against a shaft shoulder 202er by a ring 204 and spacer 205 and corotatably mounted on the shaft 202.k providing peripherally spaced roller tracks 203@ and 20312. Peripherally spaced sets of rollers 29611 and 2Mb are seated in the tracks 203:: and 203]), respectively and retained therein by an outer bearing race element 267. The outer bearing race element 297 is an annular member retained in position by a ring 208 urging the member 207 against a shoulder 209m of the housing proper 209. The housing 209 extends down over the end face 202b of the shaft 202 and is provided with a lubricant that the spring 210 resiliently urges the plunger 211 against the end face 2021;. The plunger 2li is provided with an axial bore so that lubricant may flow through the lubricating aperture 2091; and the plunger 2X1 axially movable therein and out through the mouth of the axial bore 211b against the end face 202]. The shaft end face 202i) is provided with an annular concentric groove 212 which is aligned to continuously oppose the mouth 2Mb of the plunger 211 as the shaft 2M rotates. In this manner, the groove 212 and the mouth 21117 of the plunger 2li cooperate to define a restricted orifice for owing lubricant into the housing 209. The groove 21l2 is also provided with the recess 213 in the form of a drilled hole of substantially greater depth than the depth of the groove which functions to flush the mouth of the plunger 211i once for each rotation of the shaft 202 in the manner hereinbefore described.

Referring now to Figures 10, ll and l2 which show Vstill another embodiment 259, it will be noted that the assembly 259 comprises a rotary shaft 251 corotatably mounting an inner bearing race element 252 retained against a shaft shoulder 25M by a lring 253 and spacer 254. A non-rotatable housing 255 carries an annular outer bearing race element 256 and the outer bearing race element 256 and the inner bearing race element 252 mount therebetween two sets of axially spaced bearing rollers 257 and 257b in the customary manner.

The housing 255 encloses the `bearing means 252, 257a, 257b and 256 and also the shaft 251 being provided with an end or head portion 255g opposing an end face 253th of the shaft 251. The housing end 255g is provided with a lubricating oil receiving aperture 255b which is axially aligned with the shaft 251 and which slidably receives a plunger 258 having an axial bore 258:1. At its outer end the plunger 258 is provided with threads 258]? to receive a suitable lubricant conduit connector (not shown). The axial bore 258g in the plunger 258 does not, however, extend clear to the opposite face or endi258c of the plunger 258. Instead, a short angularly aligned bore 25Sd provides communication between the axial bore 258 .and the face 258e of the plunger 258. The angularly spaced from the center of the shaft end face 251b (or` spaced from the axis of the shaft 251). The shaft face 251b may be provided with an annular groove (such as the groove 213) which is aligned to continuously oppose the opening of the'angular bore 258]) into' the plunger face 258e so as to define therewith an orifice for restricting the flow of lubricating Huid. But in this embodiment the groove is omitted. A lock pin 260 is carried by the housing end 255e and threadably engages the back of the plunger face portion 258C to prevent rotary movement thereof; and a spring 261 abutting the inside of the housing end 255g and the back of the face portion 253e of the plunger V253 resiliently urges the plunger face 253C against the shaft end face 251b. As is best seen in Fig'- ure 12, the shaft end face 25ib is provided with a recessed or drilled portion 262 at a specific point and the recessed portion 262 is employed to permit repeated ushing ot' the angular bore 2586i with each rotation of the shaft 251, in the manner hereinbefore described. The enlarged face portion 253e of the plunger 25S is provided with a semi-annular recessed portion on the face 258C. This recessed portion 263 is best shown in Figure ll and it extends from a bottom outlet 263a upwardly on both sides of the center of the plunger 258 to be closely adjacent the opening in the face 258e provided by the angular bore 25Sd. In this manner lubricating oil owing out of the angular bore 258C! and into the recess 262 (whereat the orifice is defined) rnay then flow back out of the recess 262 (after the land area of the face 258e passes) and into the recessed portion 263 in the plunger head and then down and out through the bottomY outlet 263a for the recessed portion 253. Lubricating oil will then collect in the bottom of the housing 255C and may be maintained at a level L therein by the use of an outlet drain 264 in the housing end 255er. In this way oil is continuously supplied to the rotary bearing elements passing through the pool of oil in the bottom 255C.

As will be noted the land area of the face 253C (Fig.

ure 1l) and also of the face of the plug 151 (Figure 7) is greater than the diameters of the recesses 213 and 61, respectively, so that oil `cannot pass through the apertured plug, the recess and then out into the housing, when rotation has stopped with the apertured plug aligned with the recess. This prevents continuous oil leakage during shutdown. In the device 250, the land area 258e in this position closes off the recess 262.

It will be understood that modifications and variationsV may be effected without departing from the spirit and scope of the novel concepts of the present invention.

I claim as my invention: p

l. A lubrication system comprising a bearing including a pair of relatively rotatable elements defining a housing and a third rotatable element within the housing engaging both of said pair of elements, a conduit carried by one of Said pair of elements, another of said elements rotatable relative to said one element providing an annular groove opposing said conduit and defining therewith an orifice, and means feeding lubricant through said orifice and into said housing.

2. A lubrication system comprising a bearing including a pair of relatively rotatable elements deiining a housing and a third rotatable element within the housing engaging both of said pair of elements, a conduit carried by one of said pair of elements for flowing lubricant into said housing, another of said elements rotatable relative to said one element providing an annular groove opposing said conduit and defining therewith an orifice restricting the ilow of lubricant therethrough, and means resiliently urging said conduit toward said groove.

3. A lubrication system comprising a bearing including inside, middle and outside concentric relatively rotatable elements, and a resiliently mounted plunger carried by the outside element and resiliently urged against another of said elements, said another of said elements providing a circumferential groove opposed to said plunger, said plunger having an aperture therein owing lubricant into said groove and said groove and said plunger defining a restricted orifice for ow of lubricant therethrough.

4. A bearing arrangement comprising a rotatable inner bearing race element, a non-rotatable outer bearing race element detining with said inner race element a housing, a cage carrying a plurality of rotary bearing members positioned between said inner and outer elements, and a plunger having an axial bore connected to a source of lubricant carried by the outer element and resiliently urged against the cage, said cage having an annular groove therein opposing said plunger and deiining therewith an orifice feeding lubricant into the housing.

5. A bearing arrangement comprising a rotatable inner bearing race element, a non-rotatable outer bearing race element defining with said inner race element a housing, a cage carrying a plurality of rotatary bearing members positioned between said inner and outer elements, and a plunger having an axial bore connected to a source of lubricant carried by the outer element and resiliently urged vagainst the inner element, said inner element having an annular groove therein opposing said plunger and defining therewith an orifice feeding lubricant into the housing.

6. A bearing arrangement comprising a rotatable inner bearing race element, a non-rotatable outer bearing race element defining with said inner race element a housing, two sets of axially spaced rotary bearing members positioned between the inner and outer elements, a cage mounted between said two sets maintaining peripheral spaclng between the members in each set, and a plunger having an axial bore connected to a source of lubricant carried by the outer element and resiliently urged against the cage, said cage having an annular groove therein opposing said plunger and defining therewith an orifice feeding lubricant into the housing.

7. A lubrication system comprising a bearing including inside, middle and outside concentric relatively rotatable elements, and a resiliently mounted plunger carried vby the outside element and resiliently urged against another` of said elements, said another of said elements having a recess therein repeatedly opposing said plunger as the recess is rotated past an extremity of the plunger, said plunger extremity having an aperture formed therein controllably flowing lubricant into said recess, and said plunger being provided with a land area of sufficient size to close of said recess each time the recess is stopped opposite the aperture, so as to prevent ilow-of oil directly through the aperture and said recess.

8. A lubrication system comprising a bearing including inside, middle and outside concentric relatively rotatable elements, and a resiliently mounted plunger carried by the outside element and resiliently urged against another of said elements, said plunger having an aperture therein communicating with a source of lubricant and extending to a surface thereof engaging said another of said elements, said another of said elements having a shallow annular groove therein continuously opposing said aperture during rotation thereof `to deline therewith a restricted orice limiting flow of lubricant, and said groove having a recess of predetermined size therein for receiving a metered amount of lubricant each time said recess is moved into opposition with said aperture.

References Cited in the file of this patent UNITED STATES PATENTS 2,204,171 Atwater June l1, 1940 2,551,660 Feilden V May 8, 1951 2,770,506 Derner Nov. 13, 1956 FOREIGN PATENTS 25,755 Great Britain of 1910 297,324 Great Britain Oct. 24, 1929 467,576 Canada Aug. 22, 1950

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