GB2448616A

GB2448616A - A lubrication distribution device

Info

Publication number: GB2448616A
Application number: GB0807215A
Authority: GB
Inventors: William G Colton
Original assignee: AES Engineering Ltd
Current assignee: AES Engineering Ltd
Priority date: 2007-04-20
Filing date: 2008-04-21
Publication date: 2008-10-22
Anticipated expiration: 2028-04-21
Also published as: GB2448616B; GB0807215D0

Abstract

A lubrication distribution device is provided to lubricate a bearing within a bearing chamber of an item of rotating equipment. The device comprises a flinger disc 20, which has a central hub 21 with one or more radially extending positions 22 which are sufficiently flexible that the device can be inserted through an orifice which is radially smaller than the outermost circumference of the device. The radial protrusions 22 are preferably of a blade-like shape and manufactured from thin spring-like material such a thin metal. The protrusions may either be triangular in shape with a wider portion being secured to the central hub 21 or they may include a helical twist about their longitudinal axis.

Description

Oil Flinger system for bearing lubrication

Field of the invention

The present invention relates to lubncation systems for lubricating bearings, which operate in an oil splash environment within a bearing chamber of an item of rotating equipment.

BackQroUnd to the invention For many years oil splash has been employed to provide Lubrication to rotating Jo equipment bearings in items of equipment such as centrifugal pumps.

Oil Splash environments are typically established within a bearing chamber, by the use of a oil-ring disc, which contacts an oil bath and flicks the oil inside the bearing chamber and hopefully towards the equipment bearing. Unfortunately as oil rings are typically a loose, un-driven fit over the rotating shank they promote very little oil splash to lubricate the bearings.

More recently, rotating discs have been used to encourage the movement of oil splash towards the bearings. Such discs improve the probability of oil splash generation as they are driven and hence physically rotate with the shank, thereby flicking oil on each shank rotation. Unfortunately, as the oil reservoir within the bearing chamber is radially displaced to the physical opening in the bearing housing, through which the rotating disc must pass, it is extremely problematic to install such a device.

An axially split bearing chamber housing is one possible way to accommodate a rotating disc which is of a larger radial dimension that the respective housing opening. However, this approach is commercially unpractical in most applications.

US 6,460,656 (Jones) teaches a lubricant finger system which comprises a flexible cog having of a plurality of arms separated by cutaway portions in the outer circumferential surface. Said arms are somewhat flexible and permit a degree of longitudinal flex thereby permitting the cog, having a relatively large radial dimension, to pass through an orifice with a small radial dimension, thereby allowing installation of the cog in the equipment bearing chamber.

Unfortunately, this device has not won favour in the market place because the plurality of cutaway portions, around the circumference, chum the oil within the bearing chamber, when the device rotates at a high shank speed, doing very lithe to actively direct it longitudinally towards the bearings.

It has been discovered that the rotating cutaway portions of, US 6,460,656, act to splash the oil in a radial motion, given that the plurality of cutaway portions are substantially perpendicular to the shank and act in one longitudinal plane. This means that the vast majority of the oil velocity hits the upper 12 o'clock quadrant of the bearing chamber and falls back into the oil reservoir, herewith termed wet sump. As the multitude of circumferential cutaway portions are formed in a Is singular longitudinal plane, when the shank rotates there is insufficient elapsed time between one cutaway ploughing the oil and the subsequent cutaway ploughing the oil. This means the action of the rotating disc US 6,460, 656 merely creates a spherical ball of oil adjacent to the disc, rather than actively creating oil splash.

US patent application serial no. 10/957,876 (BlochOteaches a flexible circular disc with a series of concentric grooves which enable an operator to trim the disc to suit the bearing chamber. Unfortunately, whilst said concentric grooves facilitate the trimming operation as they act as a circumferential trimming guide, they do very little to promote longitudinal oil splash in the direction towards the longitudinally spaced bearings.

Furthermore, USSN 10/957,876 has not won favour in the market place because the flexible material of disk member is prone to stretching and tearing under the considerable and prolonged centrifugal forces exherted on it during dynamic operation. A tested version of the design showed that the device literally explodes after only 1 hour running at 3,600rpm on a 43mm shank.

It is considered advantageous if an oil finger disc can be provided, which acts to provide substantial oil splash velocity towards one or more longitudinally displaced bearings.

Furthermore it is advantageous if on oil finger disc can radially flex so that it can be inserted into equipment with a housing orifice which is smaller than the diametrical outside portion of the flinger disk, yet said device resisting material deformation and/or flow from the centrifugal forces when operating dynamically.

It is also advantageous f a finger disk minimises and/or eliminates the oil ball-pooling effect as it travels through said oil, thereby reducing heat generation and/or increased equipment power generation.

Statements of the invention

According to the present invention a lubricant flinger device comprises an annular collar for mounting the device on a rotatable shaft and at least one finger extended radially outward of said collar, the or at least one said finger being moveable, relative to the collar, to reduce the radial extent of the device.

In this way the device may be inserted through an orifice, such as the entrance to a bearing chamber, which is radially smaller than the device in its operable, conformation.

By way of example, the device may be in the form of a disc which has a central hub of continuous solid circumference about a central axis. The hub has a central orifice on its innermost surface so that it may be mounted onto an item of rotating equipment such as a shaft. The hub has one or more radially extending protrusions or, its outermost circumferential surface. The radially extending protrusions may be flexible, or may be mounted for movement relative to the hub, so the disc can be inserted through an orifice which is radially smaller than the disc when it is in its operable conformation.

Preferably, said radial protrusions are of blade-like appearance and manufactured from relatively thin, spring-like material, preferably of metallic construction so to avoid radial distortion/growth under high centrifugal forces. For reference only, said thickness of the material is considered to be between 0.1 mm and 3mm, but preferably 0.6mm.

s Preferably, said blade-like radial protrusions are substantially triangular in plan view, and preferably said wider portion of the blade is secured to the central hub.

In a preferred embodiment of the invention, said radially extending protrusions have a helical twist about their respective longitudinal axis.

Preferably, said helical twist has not more than one spiral.

In a preferred embodiment of the invention, said radial protrusions are is longitudinally separated on two or more longitudinal planes so that during rotation, each blade slices through its own respective wet-sump area. For reference only, said longitudinal displacement is considered to be between 1.0- 1,000mm (0.040"-40.0"), but preferably 10mm-I 5mm (0.400"-0.600") Preferably, in each plane, only one radial protrusion is employed thereby providing the maximum time between each occasion when said protrusion slices through the lubrication media it intends to fling.

Preferably, two radial protrusions are employed, 180 degrees apart in plan view and attached to a central hub, Preferably the central hub has a securing means so that it can be secured to the item of rotating equipment, namely the shank.

Preferably, said securing means are radial setscrews, which transmit the rotational drive from the shank to the central hub and finger disc.

Preferably the radial blade-like protrusions and central hub are secured together so that there are no moving joints or parts which can wear and contaminate the lubrication media.

Preferably, two radial protrusions are employed, each with an opposing helical spiral, so to promote bi-longitudinal directed lubrication splash while the shank rotates undirectionally.

Preferably, a common finger disc can be employed for shanks which rotate counter clockwise or clockwise depending on the orientation of how said finger disc is mounted on said shank.

Preferably at least one rotational arrow is marked on the central hub, to convey the correct assembly orientation of the helical blades versus the shank rotation.

In a further embodiment of the invention, preferably the radially extending protrusions, which are secured to the hub, are round in cross section and made from a substantially thin and flexible metal wire. For reference only, said diameter thickness of the wire is considered to be between 0.1mm and 1.5mm, but preferably 0.5mm.

Preferably, said hub and wire assembly has a spherical-shaped mass secured on the outer most radial portion, which contacts said lubrication media with each shank rotation.

Preferably said finger disc is positively secured to the shank by a clamping mechanism approached from the longitudinal shank access opening.

Preferably said disc is frictionally rotationally driven to the equipment shank.

The embodiments of the invention will now be described with reference to the accompanying drawings.

Description of the drawings:

Figure 1 is a longitudinal cross section of an item of rotating equipment, such as a centrifugal pump bearing chamber.

Figure 2 corresponds to Figure 1 and shows how the finger disc radially flex's, during assembly, to permit it to pass through the smaller orifice of the bearing chamber.

Figure 3 corresponds to Figure 1 and shows a view on arrow A-A, showing the plan view of the first embodiment of the invention.

Figure 4 corresponds to Figure 3 and shows an isometric view of the first embodiment of the invention.

Figure 5 shows an alternate isometric view of the invention, showing by way of example only, a substantially triangular blade-like radially extending protrusion.

Figure 6 shows an alternate longitudinally activated damping mechanism of the invention.

Figure 7A shows multiple radial protrusions longitudinally spaced yet circumferentially balanced.

Figure 78 corresponds to Figure 7A and shows an end-view of the multiple radial protrusions circumferentially equally spaced.

Figure 8 shows an alternate isometric view of the invention, with flexible wire-like radially extending protrusions with spherical mass on the outer most region.

Figure 9 is an isometric view showing one end and part of the side of a further embodiment of a finger device is accordance with the present invention; Figure 10 illustrates the introduction of the finger device of Figure 9 into a bearing chamber; Figure 11 is a side elevation of a finger finger of the device of Figure 9; Figure 12 is an isometric partial view of the finger device of Figure 9 showing the mounting arrangement for a finger finger; Figure 13 is a side elevation of the finger device of Figure 9; Figure 14 is a partial side elevation of the finger device of Figure 9 showing a finger finger in an operable position; Figure 15 is a detailed side elevational view looking on the end of a finger finger; is and Figure 16 illustrates diagrammatically the manufacturer of a finger device according to Figure 9.

Detailed description of the invention:

Referring to Figure 1, an item of rotating equipment 10 comprises of a shank 11 and a bearing housing (or chamber) 12 that encapsulates one, preferably two bearings 13 and 14. Said housing provides a cavity 15 for containment of a chosen lubricant 16, for example oil.

In typical applications said oil will be filled to a level, typically below the outer most radial portion of the bearings 13 and 14, so that said bearings do not plough through the oil during shank 11 rotation.

The bearing housing 12 is then sealed to the rotating shank to prevent egress of the lubricant and ingress of contaminates and moisture. Typically this seal is achieved through the application of a lip, magnetic face seal or labyrinth seal 16, as shown.

Secured to the shank 11 and positioned within the bearing housing 12 is a linger disc 20 of the invention. Said linger disc 20 is preferably secured to the shank 11 by non-permanent means such as radially located setscrews 21 which positively transmit the rotational drive from the shank 11 to the finger disc 20.

In operation, the purpose of the finger disc 20 is to splash the radially displaced lubricant to each longitudinally displaced bearing 13 and 14, thereby cooling and lubricating and extending the bearings 13 and 14 operating life. I0

The reader will note that the outer most radial part of the linger disc 20 is greater in size than the inner most part of the bearing housing 12. Conventionally, this arrangement would not permit the finger disc 20 to longitudinally pass through the bearing chamber 12 orifice1 however an embodiment of the invention is that Is said finger disc has the ability to flex, as shown in Figure 2.

Figure 2 corresponds to Figure 1 and shows how the linger disc 20 radially flex's, during assembly, to permit it to pass through the smaller orifice of the bearing chamber 12.

Figure 3 corresponds to Figure 1 and shows a view on arrow A-A.

From Figure 3, in the first embodiment of the invention, the finger disc 20 comprises of a central hub 21 and at least one radially extending protrusions, herewith termed blade 22.

The blade 22 is either an integral part of the central hub (no shown), or preferably secured to the central hub 21 by a suitable means. By way of example, this is shown as one or more screws 23.

Preferably, as shown, more than one blade 22 is employed on the assembly. In the preferred embodiment, two blades 22 are employed, circumferentially spaced at 180 degrees apart. This ensures that each balance one another, as the shank 11 rotates at high speed.

Furthermore, preferably, each blade 22 is longitudinally separated. It has been surprising discovered that such longitudinal separation provides each blade 22 to operate in its own lubrication channel, therefore maximising the lubrication displacement velocity upon each shank rotation.

From Figure 4, preferably, each blade 22 incorporates a helical twist 24 which helps to direct the lubrication longitudinally upon each shank rotation.

Figure 5 shows an alternate isometric view of the invention, showing by way of io example only, a substantially triangular blade-like radially extending protrusion 30. Such a triangular shape provides additional stiffness at the radial inward position of said blade 30. This permits two or more securing devices 31 to be employed for connection to the central hub 32.

Figure 6 shows an alternate longitudinally activated clamping mechanism 40 of the invention. From Figure 6, the finger ring 41 is secured to the equipment shank 42 by one or more longitudinally accessible screws 43 which pull a longitudinally floating component 44 with a taper 45 against a longitudinally static component 46 with a corresponding taper 47. Said tapered engagement provides a small radial displacement in one of said components 44 and 46 to provide a frictional drive of the finger ring 41 to the equipment shank 42.

Figure 7A shows a further embodiment of the invention, a multiple-stacked finger disc 50, whereby multiple radial protrusions 51 are longitudinally spaced yet circumferentially spaced, hence balanced when viewed in the end view (Figure 78).

The combined multiple-stacked finger disc may be supplied as one central hub from which the radially extending protrusions ate attached (not shown) or supplied as modular multiple-central hubs 52 which inter-lock together in such a way as provide a circumferentially balanced assembly.

Figure 8 shows an alternate isometric view of the invention, and a further embodiment1 which a mace disc 60. Said mace disc 60 has one or more flexible wire-like radially extending protrusions 61 and 62, each containing a spherical mass on there outer most radial region.

Given the wire protrusion 61 and 62 are flexible, they still permit said mace-disc s to pass through a radially smaller bearing chamber orifice.

The experiencej reader will thereby note that the various embodiments of the invention provide lubricant displacement properties, many fold greater than the pit-or-art disc and oil-ring devices. This means that rotating equipment bearings, as found in centrifugal pumps, may be adequately lubricated in a cost effective and efficient manner.

Furthermore, the invention has a distinct advantage in that it can be fitted through a bearing chamber orifice of smaller radial size.

Referring Figures 9 to 16 of the accompanying drawings, there is illustrated the further embodiment of a finger device in accordance with the present invention.

Referring first to Figures 9 and 10, a finger device 101 comprises a broadly annular metal ring which may be made of, for instance, phosphor bronze. Ring 103 will, in use, fit round a drive shaft 105 which extends into a bearing chamber 107 in rotary equipment. Ring 103 is provided with a shallow circumferential groove 109 in its outer circumferential surface and with a deeper circumferential groove 111 in its inner surface. Provided at opposite diametrical locations are two circumferential slots 113 which extend from groove 109 through to groove 111. Each slot 113 is of a dog leg shape as viewed radially. The slot 113 has a first elongate leg 115 located against one edge 117 of groove 109. The slot 113 has an enlarged central portion 119 and extending therefrom in a direction away from leg 115 a second elongate leg 121 (see Figure 13).

As seen in Figure 9, extending from central portion 119 of slot 113 is a finger 123 which is made of, for instance, thin spring steel and which is moveable (as will be expiained below) relative to the body of ring 103, between three positions of which one is shown in Figure 9. As shown in Figure 9, 123 is in its operable position so that it will engage oil in the sump of the bearing within which the device is located, Refening now to Figure 11, finger finger 123 is an elongate member having one s end around it and provided with a hole 125 enabling the finger 123 to be mounted on a pin 127 (see Figure 12) which extends longitudinally through ring 103 at central portion 119 of slot 113. Finger 123 has an enlarged other end 127 which is provided with a curved edge 129 whose radius extends from a maximum at one side of the finger to a minimum at a nose portion 131 of the finger 123. In use the finger will rotate in the direction indicated by the arrow in Figure 11 so that nose portion 131 provides the leading edge during such rotation. It has been established that a curved edge of radius diminishing towards the leading edge provides a streamlined design with a relatively low extent of "churning" during use of the device.

Opposite nose portion 131 the finger 123 is provided with a substantially straight radial edge 133 which itself is provided with 2 radially spaced notches 135.

When installed these notches indicate the maximum and minimum oil revels (with the finger located in its lowest position, thereby indicating the desired oil level range forthe bearing).

The finger 123 is also provided with a notch 137 located on the elongated shank portion 139 of the finger, this notch 137 serving to locate an end of the torsion spring 141 (to be referred to below).

It should be appreciated that the length of shank 139 of finger 123 may vary according to the dimensions of the bearing within which the finger device is to operate. Accordingly a finger device may be provided with a range of fingers of different lengths or it may be fitted with fingers with a chosen length according to the known dimensions for the bearing chamber within the device is to be used.

Referring now to Figures 12 to 15, the details of the mounting and operation of the finger fingers will now be described. The finger is moveable, relative to the ring 103, between three positions. The middle position is shown in Figure 9. This ii is the position which the finger will occupy during use of the device. In that position the finger 123 extends radially outwardly from middle portion 119 of slot 113. The other two positions are such that the finger extends at least partly into one or other of the slots 115 and 121. Prior to installation the finger will be located so that its lies partly within slot 121. It is spring urged into this position by means of a compression spring 151 mounted on pin 127. In this position finger 123, which is provided with a recessed portion 153 located in that edge opposite notch 137, is positioned such that recessed portion 153 engages with integral projection 155 of ring 103.

Finger 123 is also spring urged circumferenfially by means of torsion spring 141 which extends between notch 137 on finger 123 and an anchoring surface on ring 103. The effect of torsion spring 141 is to urge finger 123 circumferentially from the position in Figure 12 towards the other leg 115 of slot 113 in ring 103. I5

Pin 127 is loosely mounted in ring 103 for longitudinal movement relative thereto.

At one end of pinl27, the pin is provided with a button 157 which engages also finger 123 as indicated in Figure 12. Depression of button 157 will shift finger 123 longitudinally away from projection 155. When finger 123 has cleared projection 155 torsion spring 141 will cause the finger to rotate to the position shown in Figure 9 where the edge of shank 139 will engage a shoulder of central portion 119 of slot 113. Further depression of button 157 will cause the finger 123 to move beyond the shoulder so that it is then free to rotate further, urged by torsion spring 141, to position shown in Figure 13 when the finger lies at least partly within portion 115 of slot 113. It will be appreciated that the three positions described above allow the finger to be installed with the chamber of a bearing, with the fingers located in the first position, as illustrated in Figure 12. Following depression of button 157 so that the fingers adopt the second position as illustrated in Figure 9, the finger disc will then be operable. For removal of the device from the bearing chamber, the button 157 is further depressed causing the fingers to move to the third position, In this third position the radial extent of the device is again relatively small and the device may be removed.

Button 157, provided on pin 127, may be provided with circumferential groove 161 which may serve to provide a sight line showing the position of the pin 127 relative to the ring 103.

s In a preferred aspect of this embodiment, the fingers 123 are set at an angle to a radial plane. This slightly twisted orientation of the fingers is found to give a particulaily effective radial and longitudinal movement of the oil in a direction towards the bearing. The extent of "twist" of finger 123 may vary but is preferably between 2 and 10 degrees. As illustrated in Figure 15, the finger 123 is located in the plane 171 which is at an angle of 5 to the radial plane 173. This twist of the finger 123 is achieved by means of the compression spring 151 urging the finger against surfaces of slot 113 which are appropriately angled relative to the corresponding radial planes.

is Referring to Figure 16 of the accompanying drawings, there is illustrated apparatus for the manufacture of the ring 103 forming part of the above described finger device. Shown in this Figure are parts of cutting tools 181, 183 and 185 which can simultaneously produce the drcumferentially grooved ring. There is also shown a milling tool 187 which is operated to produce the slot 113. Further tools introduced from the end of the ring shown in Figure 16 or radially into the edge of the ring will produce longitudinal holes 187 and radial holes 189. These operations are all conducted on the end of a metal tube which, when the operations have been concluded, may then be radially cut to release the required thickness of ring 103. In other words, all the operations required to produce the ring may be performed on the end of the tube, that is to say, from one longitudinal direction or radially. Once the ring is cut from the tube no further operations are required on the other side of the ring.

The following claims relate primarily to the embodiment or embodiments of Figure 1 to 8. It should be appreciated that further claims will be filed which are directed to the embodiment of Figures 9 to 16.

Claims

Claims I. A lubrication distribution means comprising a flinger disc,

which has a central hub of continuous solid circumference about a central axis, said hub has a s central orifice on its inner most surface so that it may be mounted onto an item of rotating equipment such as a shank, said hub has one or more radially extending protrusions on its outermost circumferential surface and said radially extending protrusions have a flexing means so that said hub with radial protrusions can be inserted through an orifice, which is radially smaller than said discs outer most circumference.
2. A lubrication distribution means, in accordance with claim 1, whereby said radial protrusions are of blade-like shape and manufactured from relatively thin, spring-like material, preferably of metallic construction
3. A lubrication distribution means, in accordance with claim 2 whereby said blade material thickness is considered to be between 0.1mm and 3mm, but preferably 0.6mm.
4. A lubrication distribution means, in accordance with claim 2, whereby said blade-like radial protrusions are substantially triangular in shape and preferably said wider portion of the blade is secured to the central hub.
5. A lubrication distribution means, in accordance with claim 2, whereby said radially extending protrusions have a helical twist about their respective longitudinal axis.
6. A lubrication distribution means, in accordance with claim 2, whereby said radial protrusions are longitudinally separated on two or more longitudinal planes.
7. A lubrication distribution means, in accordance with claim 6, whereby said longitudinal displacement is considered to be between 1.0-1,000mm (0.040"- 40.0"), but preferably 10mm-I 5mm (0.400-0.600").
8. A lubrication distribution means, in accordance with any previous claim, whereby, in each plane, only one radial protrusion is attached to the central hub.
9. A lubrication distribution means, in accordance with any previous claim, whereby two radial protrusions are employed, and circumferentially spaced at degrees apart in the end view and attached to a central hub,
10.A lubrication distribution means, in accordance with any previous claim, whereby the central hub has a securing means so that it can be secured to the item of rotating equipment, namely the shank.
11. A lubrication distribution means, in accordance with any previous claim, whereby said securing means are radial setscrews, which transmit the rotational drive from the shank to the central hub and finger disc.
12.A lubrication distribution means, in accordance with any previous claim, whereby two radial protrusions are employed, and positioned against to the two bearings in the item of rotating equipment, one blade having a right hand helical and the other blade having a left hand helical.

13.A lubrication distribution means, in accordance with any previous claim, whereby the radially extending protrusions, which are secured to the hub, are round in cross section and made from a substantially thin and flexible metal wire.

14.A lubrication distribution means, in accordance with claim 13, whereby said diameter thickness of the wire is considered to be between 0.1mm and 1.5mm, but preferably 0.5mm.

S

15.A lubrication distribution means, in accordance with claim 13 and/or 14 whereby said hub and wire assembly has a spherical-shaped mass secured on the outer most radial portion, whith contacts said lubrication media with each shank rotation.

16.A lubrication distribution means, in accordance with any previous claim, whereby said finger disc is positively secured to the shank by a clamping mechanism approached from the longitudinal shank access opening.

17.A lubrication distribution means according to Claim I and substantially as herein described.

18.A lubrication distribution means substantially as described herein with reference to Figures 1 to 4, any of Figures 5 to 8 or Figures 9 to 16.

Amendment to the claims have been filed as follows Claims 1. A lubrication distribution means comprising a flinger disc, having a central hub of continuous solid circumference about a central axis, said hub having a central orifice so that it may be mounted onto an item of rotating equipment such as a shank, said hub having one or more fingers on its outermost circumferential surface, at least one of the fingers being movable relative to the hub from a first position to a second position, the radially outer extension of said finger from the hub being greater in said first position than in said second position.

2. A lubrication distribution means, in accordance with claim 1, whereby said fingers are of blade-like shape and manufactured from relatively thin, spring-like material, preferably of metallic construction Co 3. A lubrication distribution means, in accordance with claim 2 whereby said CO blade material thickness is considered to be between 0.1 mm and 3mm, but preferably 0.6mm. Co

4. A lubrication distribution means, in accordance with claim 2, whereby said blade-like fingers are substantially triangular in shape and preferably said wider portion of the blade is secured to the central hub.

5. A lubrication distribution means, in accordance with claim 2, whereby said fingers have a helical twist about their respective longitudinal axis.

6. A lubrication distribution means, in accordance with claim 2, whereby said fingers are longitudinally separated on two or more longitudinal planes.

7. A lubrication distribution means, in accordance with claim 6, whereby said longitudinal displacement is considered to be between 1.0-1,000mm (0.040"- 40.0"), but preferably lOmm-l5mm (0.400-0.600").

8. A lubrication distribution means in accordance with any previous claim, whereby, in each plane, only one finger is attached to the central hub.

9. A lubrication distribution means, in accordance with any previous claim and S having, two fingers which are, and circumferentially spaced at 180 degrees apart in the end view and attached to a central hub, 10.A lubrication distribution means in accordance with any previous claim, whereby the central hub has a securing means so that it can be secured to io the item of rotating equipment.

11.A lubrication distribution means, in accordance with any previous claim, whereby said securing means are radial setscrews, which transmit the rotational drive from the shank to the central hub and flinger disc.

C 12.A lubrication distribution means in accordance with any previous claim, CO whereby two radial protrusions are employed, and positioned against to the C two bearings in the item of rotating equipment, one blade having a right hand CO helical and the other blade having a left hand helical.
13.A lubrication distribution means in accordance with any previous claim, whereby the fingers, are round in cross section and made from a substantially thin and flexible metal wire.
14.A lubrication distribution means in accordance with claim 13, whereby said diameter thickness of the wire is considered to be between 0.1 mm and 1.5mm, but preferably 0.5mm.
15.A lubrication distribution means, in accordance with claim 13 and/or 14 whereby said hub and wire assembly has a spherical-shaped mass secured on the outer most radial portion, which contacts said lubrication media with each shank rotation.
16.A lubrication distribution means according to claim 1 wherein the or at least one finger is mounted on said hub for pivotal movement about an end of said finger.
17.A lubrication distribution means according to claim 16 wherein the or at least one finger is spring urged towards said first position.
18.A lubrication distribution means according to claim 17 wherein means are provided to enable the or at least one finger to be held in said second position.
19.A lubrication distribution means, in accordance with any previous claim, whereby said flinger disc is positively secured to the shank by a clamping mechanism approached from the longitudinal shank access opening.
20.A lubrication distribution means according to Claim 1 and substantially as herein described. Co
21. A lubrication distribution means substantially as described herein with CO reference to Figures ito 4, any of Figures 5 to 8 or Figures 9 to 16. \\