GB2199923A

GB2199923A - Friction control for bearing surface of roller

Info

Publication number: GB2199923A
Application number: GB08730264A
Authority: GB
Inventors: Edwin E Rice; Hugh R Norris
Original assignee: Ingersoll Rand Co
Current assignee: Ingersoll Rand Co
Priority date: 1987-01-14
Filing date: 1987-12-29
Publication date: 1988-07-20
Anticipated expiration: 2007-12-29
Also published as: FR2609457A1; IT8723165A0; CA1303659C; GB8730264D0; GB2199923B; IT1224646B; DE3800922A1; FR2609457B1

Description

9 FRICTION CONTROL FOR BEARING SURFACE OF ROLLER 2199923 This invention

relates to the roller element of a Dowered-roller transfer line, and racre particularly to thLe apparatus and method e-,abodizd by a roller having a plurality of lubricant pressure relief areas in or about the bearing surface to provide consistent and increased ro,$'.-ary-poxqer transmission from a powered axle to the roller..

For certain aut-omotive components such as or transmissionz, powered roller transfer lines are used tz nove workpieces through the manufacturing and assembly stations.

Workpieces are mounted on pallets which are carri-ad through the line.by rollers driven by slow but continuously rotating axles..

The rollers have a lubricated bushing-type inner diameter to fit an the axles. To propel the bearing surface adapted pallets, the powered ax-les cause the rollers to rot'--a',,e.1by usirig the friction betfAeen the axle and the bearing surface ---F the roller. At certain positions on the transfer line, ill: is desired to stop the pallets. At these intended stopping points, a stopping nechanism physically restrains the pa-llet. The rollers under the stopped pallet also stop rotating and slip-on the rotating axle5. This slipping is facilitated by the lubricant between the axle and the bearing surface of the roller.

The driving force to accelerate a pallet from a stopping poi-nt or to dri,je a pallet past a ziinor resistance such as a small change in elevation is determined by the coefficient of friction between the ai-,le and the inner diaracter bearing surface of the roller. The --ocffir-ierit of:E--ict,-ion n turn is affected by the lubrication condition existing between the axle and the bearing surface of the roller. The desired lubrication 9 mode for the powered-roller In the transfer line descr-,bed above is boundar-y lubrication.

Under some working conditions however, additional lubricant from the work process or the environment ray gradually enter the bearing gap. The additional lubricant changes the lubricant mode from boundary to hydrodynamic Hydrodynamic -ially reduces the fr- - lubrication substanIL ict4on between the roller and powered axle. Therefore the driving force transmitted from the axles to the rollers is substantially reduced. The reduced driving force provided by the rollers to the pallets causes the pallets to improperly accelerate and nove his is undesirable in automated manufacturing inconsistently. 11. and assembly lines.

An object of this invention lis to maintain at a consistent and acceptable level the drive force transmitted to a roller from a powered axle.

Another object is to maintain an acceptably high coefficient of friction between the powered axle and the roller.

Another object is to prevent additional lubricant in the bearing gap of a roller from causing undesired transition from boundary to hydrodynamic lubrication.

Another object is to relieve lubricant pressure locally from about the bearing surface by providing lubricant pressure relief areas so as to maintain boundary lubrication about the bearing surface and thus maintain a high coefficient of friction between the powered axle and the roller which results in c - 3 consistent rotary power transmission from the powered axle to the intermittently rotating roller.

The objects and advantages of the present inventlon-are attained by having a plurality of lubricant pressure reliet areas about the bearing surface of an annular roller.

An-unexpected advantage of the present invention is the increase in drive force transmitted from the powered axle to the roller element under operating conditions with excess lubrication-present.

other objects, advantages and novel features of the preset invention will become apparerl',-- from the following detailed description of the invention when considered in conjunction with the accompanying d-rawings.

Figure 1 is a partial cross-sectional and a partialelevation of a portion of a transfer line.

Figure 2 is a front view of the roller., Figure 3 is a cross-sectional side view iot the roller of the present invention.

Figure 4 is an enlargement of the circl-i.ed portion of the roller in Figure 3.

Figure 5 is another embodiment of the present invention.

4 A typical powered axle-roller subassembly of a transfer line is shown in Figure 1. The axle 12 is support for rotation by bearings 14 in the frame member 16. A bevel gear arrangement 18 and 20 provides constant rotational power to the axle from a power source, such as a motor, connected to drive shaft 22.

Two rollers 30 are mounted on the axle in the transfer line shown in Figure 1. A spacer 24 and two collars 26 position the rollers on the axle. Other configurations are possible. A front view of a roller is shown in Figure 2. The roller is usually a solid metal annular cylinder having outer and inner diameter surfaces. The outer diameter surface 32 provides the roller contact surface to carry a pallet such as 28 in Fig-are 1. The inner diameter surface 34 provides a bearing surface for the axle 12. The bearing surface 34 is formed by a bore through the center of the roller and is usually concentric with the outer diameter roller surface.

The inner diameter bearing surface 34 is dimensioned such that a small bearing gap exists between the powered axle 12 and the bearing surface. A lubricant is provided in the bearing gap. In a preferred embodiment, the roller is constructed of a lubricant-impregnated sintered material. Alternatively, lubricant may be introduced into the bearing gap by other conventional means such as a lubricant wick or pump. Another known means of providing lubricant to the bearing gap is by a supply passageway such as a supply groove on the axle or the bearing surface of the roller. A lubricant supply groove has large dimensions and is widely spaced on the axle or roller surfaces so as to best perform its supply function.

In normal operation a roller having a i h.

smooth bearing i -1/ Z1 surface operates as follows.. The powered axle 12 rotates continuously. A thin film of lubricant occupies the bearing gap between the axle and bearing surface of the roller. The axle rotational speed and other factors are such that the lubricant effect is in the boundary lubrication mode. The coefficient of friction between the axle and the bearing surface of the roller is high. This is well known from the Stribeck curve which relates lubrication mode to coefficient of friction for sliding bearings. Thus the axle causes the roller to rotate and tangentially propel the pallet forward. The coefficient of friction in the boundary lubrication mode is high enough that the drive force supplied by the axle to the roller can,ove-,come any minor resistance a pallet may encounter on the line.

Furthermore, in normal operation, the lubrication about the bearing surface of the roller allows the roller to slip on the axle if the pallet encounters a stiff resistance such as a stopping mechanism. The lubrication in the bearing gap facilitates the continued rotation of the powered axle relatiie to the stopped roller.

During operation of the line, excess lubrication may gradually enter the bearing gap. The increased lubrication causes the lubrication effect to change from the boundary mode to the hydrodynamic mode. The coefficient of friction between the axle and the roller decreases as the lubrication mdde changes from boundary to hydrodynamic lubrication. Again this is known from the Stribeck curve.

In a hydrodynamic lubrication mode, the drive force supplied by the axle to the roller is not strong enough to overcome minor resistance. Thus the rollers begin to slip on the axles and the pallets in the line are subject to -.6 inconsistent movement. In other words, when excess lubrication enters the bearing gap the rollers tend to slip on the powered axle rather than drive the pallets.

The present invention overcomes the above problem. Even with excess lubrication, the lubricant can be maintained in the boundary lubrication mode by dividing the bearing surface into narrow lands separated by narrow lubricant pressure relief areas. The recessed relief areas bleed off the excess lubricant pressure and prevents transition to hydrodynamic lubrication. In the preferred embodiment of the roller 30A shown in Figure 3, and enlarged in Figure 4, narrow or thin grooves 36 having a substantially circumferential orientation provide localized lubricant pressure bleed off. The grooves preferably are narrow so as not to substantially reduce the bearing area. The bearing lands between the grooves are also relatively narrow but preferably are three to ten times the groove width. This relationship appears important to provide both adequate bearing support area and relief area to bleed off lubricant pressure. It is apparent that these narrow, closely spaced lubricant pressure relief grooves differ substantial in construction, purpose and effect from the large, widely spaced lubricant supply grooves discussed earlier.

A thread-like helical groove on the inner diameter bearing surface of the roller, as shown in Figures 3 and 4, is the preferred embodiment for providing lubricant relief areas for the bearing surface of the roller. The groove has a groove root width of about.00511, a thread pitch between. 01511 and.05011, and a thread depth between.00311 and.00611. The groove sidewalls have a 600 included angle. A helical thread configuration is preferred due to ease of machining.

Unexpectedly, it was found that dividing the bearing L.

2 1 Q 1 7 surface into narrow lands surrounded by lubricant pressure relief areas such as circumferential grooves machined into the bearing surface increased the drive force transmitted to:the rollers when excess lubricant is present. For example, A-new roller having a smooth, ungrooved bearing surface was found to initially generate about 25 lbs. of drive force on a pallet with 450 lbs. of weight. When excess lubrication was introduced into the bearing-gap the drive force was reduced to 4-7 lbs.

In the above situation, installing rollers with circumferential grooves machined into the bearing surface as provided by the present invention produced 28-30 lbs. of---drive force. When excess lubrication was introduced into the bearing gap, the grooved roller produced 25-30 lbs. of force, about 4 times the drive force transmitted by the smooth ungrooved bearing surface with excess lubricant.

Other configurations of lubricant pressure relief areas are possible and are considered within the scope of this_ invention. Thin axial grooves on the roller inner diameter would also allow the excess lubricant pressure to bleed off. Alternatively, as shown by Figure 5, axial 1 or circumferential grooves 38 can be provided on the axle 12A,,,,opposite the bearing -surface of the roller inner diameter.

X 5.

8

Claims

CLAIMS:

A roller comprising an annular roller element having an outer diameter roller surface, a lubricated inner diameter bearing surface and means for maintaining an acceptably high coefficient of frictinn at said inner diameter bearing surface.
2. A roller according to claim 1, wherein the friction maintaining means comprises a plurality of lubricant pressure relief areas about said bearing surface.
3. A roller according to claim 1, wherein the is friction ma in t a ini rig mearis c(--) iriptr is -- s a p 1 U r _ 1 i tll c f narrow, closely spaced circumferential grooves in said bearing surface.
4. A roller according to claim 1, wherein the friction maintaining means comprises a narrow, helical groove in said bearing surface.
A roller according to claim 4, wherein the groove has a groove root width of.005" (0.0127 cm), a thread pitch between.015n (0.0381 cm) and.050n (0.127 cm), a thread depth between.00Y' (0.0076 cm) and.00C (0.0153 cm) and groove side walls having a 600 included ang le.
6. A roller assembly comprising a powered axle; an annular roller having an outer diameter roller surface, a lubricated inner diameter bearing surface adapted to t 9 - fi I! 3- be mounted on said powered axle, and means for maintaining boundary lubrication about said inner diameter bearing surface.
7. A roller assembly according to claim 6, wherein the boundary lubrication means comprises a narrow, helical groove on the bearing surface of the roller.
8. A roller assembly according to claim 6, wherein the boundary lubrication means comprises a narrow, helical groove on the axle.
9. A roller, substantially as hereinbefo.re described with reference to Figures 1 to 4 or Figure 5 of the accompanying drawjng,.
10. A method for transmitting the rotational drive force of a continuously rotating axle to an intermittently rotating roller having an. inner diameter bearing surface mounted on the axle, comprising lubricating the bearing surface of the roller and maintaining an acceptable high coefficient of friction about the bearing surface of the roller.
11. A method according to claim 10, wherein the step of maintaining a high coefficient of friction further comprises the step of relieving lubricant pressure about the bearing surface.
12. A method for transmitting the rotational drive force of a continuously rotating axle to an intermittently rotating roller, substantially as hereinbefore described with reference to Figures 1 to 4 or Figure 5 of the accompanying drawing.

Pub!16h.td 1988 at'IT"he Patent Office, State House. 6671 High Holborn, Lond-!n WCIR 4TP. Further copies may be obtained from ThePatent Office. Sales Branch. S, Mary Cray. Orpingi, n Zent BR5 3!--,D Pr-ated by Multiplex techniques ltd. St Mary Cray. Kent Con 118-7.