U.S. patent application number 09/945520 was filed with the patent office on 2002-03-14 for lubrication of oscillating head elements, for floor stripping machines.
Invention is credited to Scarlett, Lee A..
Application Number | 20020030399 09/945520 |
Document ID | / |
Family ID | 23627145 |
Filed Date | 2002-03-14 |
United States Patent
Application |
20020030399 |
Kind Code |
A1 |
Scarlett, Lee A. |
March 14, 2002 |
Lubrication of oscillating head elements, for floor stripping
machines
Abstract
Apparatus usable in power-operated floor stripping apparatus
that includes a frame, a drive carried on the frame, wheels
supporting the frame, a handle to guide the frame, and a cutting
blade carried by a head which is pivotally mounted to the frame,
the apparatus comprising a lightweight rugged connecting element
having a first tubular part and a second tubular part, those parts
having spaced, parallel axis, the second tubular part pivotally
connected to the head. There are two axially spaced eccentrics on
the drive shaft, which rotate within two annular bearings carried
by the first tubular part. Spiral grooves are sunk in the external
surfaces of said eccentrics to communicate with said lubricant
receiving space to receive lubricant for distribution along said
eccentrics to the annular bearings.
Inventors: |
Scarlett, Lee A.; (St.
George, UT) |
Correspondence
Address: |
William W. Haefliger
Suite 512
201 So. Lake Ave.
Pasadena
CA
91101
US
|
Family ID: |
23627145 |
Appl. No.: |
09/945520 |
Filed: |
September 4, 2001 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
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09945520 |
Sep 4, 2001 |
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09411001 |
Oct 1, 1999 |
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Current U.S.
Class: |
299/37.1 |
Current CPC
Class: |
E04G 23/006
20130101 |
Class at
Publication: |
299/37.1 |
International
Class: |
E04G 023/00 |
Claims
I claim:
1. For use in power-created floor stripping apparatus that includes
a frame, a drive carried on the frame, wheels supporting the frame,
and handle to guide the frame, and a cutting blade carried by a
head which is pivotally mounted to the frame, the improvement
comprising, a) a connecting element having a first tubular part and
a second tubular part, said parts having spaced parallel axis, one
tubular part having an outside diameter substantially larger than
the outside diameter of the other tubular part, b) a drive shaft
extending within said first tubular part, said shaft operatively
connectible to the drive to be rotated thereby, c) said drive shaft
carrying two axially spaced eccentrics to be rotated by the shaft,
there being a lubricant receiving space located directly between
said eccentrics, d) two annular bearings respectively carried by
and within said first tubular part, said bearings respectively
receiving said spaced eccentrics to oscillate said first tubular
part, said head and said blade as said eccentrics are rotated by
the shaft, e) said head consisting of lightweight metal and having
two flanges interconnecting by a web, the flanges being locally
thickened to substantial extent to define two lugs, f) said second
tubular part extending between said flanges and pivotally connected
thereto in spaced relation go said lugs, g) said connecting element
including two substantially parallel legs extending between said
first and second tubular parts and integrally merging therewith at
locations spaced from the ends of said parts, h) there being spiral
grooves sunk in the external surfaces of said eccentrics to
communicate with said lubricant receiving space to receive
lubricant for distribution along said eccentrics to the annular
bearings
2. The combination of claim 1 wherein the spiral grooves have ends
in communication with outer portions of said lubricant receiving
space.
3. The combination of claim 1 wherein said grooves have entrances
located at opposite ends of said lubricant receiving space, and at
flared end walls of the eccentrics, and wherein each groove spirals
about 360.degree. between its entrance and the end of the eccentric
remote from said lubricant receiving space.
4. The combination of claim 1 wherein each groove has about 1.25
inch width, and about 0.015 inch depth, along the groove
length.
5. The combination of claim 1 wherein: (i) said legs having first
webs defining planes normal to parallel axis defined by said parts,
said planes defined by the webs intersecting said lugs, the webs
having outer edges tangent to the outer surfaces of the tubular
parts whereby said outer edges taper toward the smaller diameter
part, j) second webs normal to said first webs, and defining planes
parallel to said spaced parallel axis defined by said parts, said
second webs also merging with said parts, said first and second
webs extending in intersecting relation at an enlarged central
region of each leg, k) said planes defined by the first webs also
intersecting said eccentrics so that said lubricant receiving space
is centered between said planes.
6. The improvement of claim 1 wherein said planes defined by the
webs intersect said lugs proximate inner edges defined by the
lugs.
7. The improvement of claim 1 including bearing bushings received
in and carried by said lugs to form bearing openings for a pivot
shaft connected to the frame, said bushings being self-lubricated
adjacent the shaft.
8. The improvement of claim 7 wherein said lugs have lengths
between 3/4 and 11/2 inches.
9. The improvement of claim 8 including said pivot shaft closely
received in said bearing openings.
10. The improvement of claim 1 including a blade holder plate
attached to the head at the bottom side thereof, said flanges
having width that increase in direction toward said plate, two
shafts extending parallel to said head web and through said head
flanges to provide shaft projections exteriorly of said flanges,
and fasteners extending through said holder plate and having
threaded shanks in threaded engagement with threaded openings in
said shaft projections, the fasteners having heads below said
holder plate to be rotated for clamping the blade between the plate
and the head bottom side, said legs merging with said second
tubular part at locations proximate the increasing width of said
flanges.
11. The improvement of claim 10 including said frame, drive,
wheels, handle and cutting blade clamped to said holder plate.
12. The improvement of claim 1 wherein said first and second
tubular parts and said legs are defined by a lightweight metal
casting.
13. The improvement of claim 12 wherein said metal casting consists
of metal selected from the group consisting essentially of zinc,
aluminum and magnesium.
14. The combination of claim 1 wherein said eccentrics have
oppositely facing end faces which flare radially outwardly and
axially away from said space, to urge and guide lubricant toward
said bearings, said grooves intersecting said flared end faces.
15. The combination of claim 14 wherein said bearings comprise
bushings.
16. The combination of claim 14 wherein said end faces intersect
the outer cylindrical surfaces of the eccentrics in planes
extending at angles .alpha. relative to the shaft axis, said angles
.alpha. being less than 90, said grooves having axially spaced
entrance ends on said flared end faces closest to the center of
said space 100.
17. In improved floor stripping apparatus having a connecting
element, a floor stripping blade, and a head, and a drive, the
combination comprising: a) said connecting element having a first
tubular part and a second tubular part, said parts having spaced,
parallel axis, said second tubular part pivotally connected to the
head, b) a drive shaft extending within said first tubular part,
said shaft operatively connectible to the drive to be rotated
thereby, c) said drive shaft carrying two axially spaced eccentrics
to be rotated by the shaft, there being a lubricant receiving space
located directly between said eccentrics, d) two annular bearings
respectively carried by and within said first tubular part, said
bearings respectively receiving said spaced eccentrics to oscillate
said first tubular part, said head and said blade as said
eccentrics are rotated by the shaft, e) there being spiral grooves
sunk in the external surfaces of said eccentrics to communicate
with said lubricant receiving space to receive lubricant for
distribution along said eccentrics to the annular bearings
18. The combination of claim 17 wherein said spiral grooves have
ends in direct communication with outer portions of said lubricant
receiving space.
19. The combination of claim 17 wherein said grooves have entrances
located at opposite ends of said lubricant receiving space, at
flared ends of said eccentrics.
20. The combination of claim 17 wherein each groove spirals about
360.degree. between its entrance and the end of the eccentric
remote from said lubricant receiving space.
21. The combination of claim 17 wherein each groove has about 0.125
inch width, and about 0.015 inch depth, along the groove
length.
22. The method of operating floor stripping apparatus having a
connecting element, a floor stripping blade, and a head, and a
drive, the combination comprising that includes: a) providing said
connecting element to have a first tubular part and a second
tubular part, said parts having spaced, parallel axis, said second
tubular part pivotally connected to the head, b) providing a drive
shaft extending within said first tubular part, said shaft
operatively connectible to the drive to be rotated thereby, c) said
drive shaft provided with two axially spaced eccentrics to be
rotated by the shaft, there being a lubricant receiving space
located directly between said eccentrics, d) providing two annular
bearings respectively carried by and within said first tubular
part, said bearings respectively receiving said spaced eccentrics
to oscillate said first tubular part, said head and said blade as
said eccentrics are rotated by the shaft, e) providing spiral
grooves sunk in the external surfaces of said eccentrics to
communicate with said lubricant receiving space to receive
lubricant for distribution along said eccentrics to the annular
bearings, f) and rotating said grooves eccentrically, by rotating
said eccentrics, to rotate and vibrate lubricant in said grooves,
driving said lubricant toward inner surfaces defined by said
annular bearings.
23. The method of claim 22 including employing pulsing centrifugal
force to urge said lubricant into said grooves.
Description
BACKGROUND OF THE INVENTION
[0001] This invention relates generally to floor stripping devices,
and more particularly concerns improvements in the driving and
blade support means for same.
[0002] U.S. Pat. No. 3,376,071 discloses a floor stripping machine
of the type in which the present invention is usable to great
advantage. Such machine incorporates a cutting blade carried by a
head pivotally mounted to a frame. Problems with machines as
disclosed in that patent include failure of rapidly oscillating
head driving connecting rods and associated parts and bearings;
insufficient lubricating of such rods, parts and bearings, undue
wear of the oscillating head at its pivots; unwarranted high cost
of repair and replacement of such elements; and difficulty with
clamping a blade to the bottom side of the head.
[0003] U.S. Pat. Nos. 4,512,611, 4,504,093, 4,483,566, 4,452,492,
4,365,843 and 4,365,842 and 4,512,611 disclose improvements over
said U.S. Pat. No. 3,376,071.
SUMMARY OF THE INVENTION
[0004] It is a major object of the invention to provide an
additional solution to the above described problems and
disadvantages. Basically, the invention is embodied in improved
floor stripping apparatus having a floor stripping blade, a head,
and a drive, and includes:
[0005] a) a connecting element having a first tubular part and a
second tubular part, said parts having spaced, parallel axes, said
second tubular part pivotally connected to the head,
[0006] b) a drive shaft extending within the first tubular part,
said shaft operatively connectible to the drive to be rotated
thereby,
[0007] c) said drive shaft carrying two axially spaced eccentrics
to be rotated by the shaft, there being a lubricant receiving space
located directly between said eccentrics,
[0008] d) two annular bearings respectively carried by and within
said first tubular part, said bearings respectively receiving said
spaced eccentrics to oscillate said first tubular part, said head
and said blade as said eccentrics are rotated by the shaft.
[0009] e) there being spiral grooves sunk in the external surfaces
of said eccentrics to communicate with said lubricant receiving
space to receive lubricant for distribution along said eccentrics
to the annular bearings.
[0010] These and other objects and advantages of the invention, as
well as the details of an illustrative embodiment, will be more
fully understood from the following specification and drawings, in
which:
DRAWING DESCRIPTION
[0011] FIG. 1 is a side elevation showing a floor stripping machine
incorporating the invention;
[0012] FIG. 2 is a top plan view of the FIG. 1 machine;
[0013] FIG. 3 is an enlarged elevation taken on lines 3-3 of FIG.
4;
[0014] FIG. 4 is a section taken on lines 4-4 of FIG. 3;
[0015] FIG. 5 is a section taken on lines 5-5 of FIG. 3;
[0016] FIG. 6 is an enlarged section taken through connecting
structure seen in FIG. 4;
[0017] FIG. 7 is an end elevation view of the FIG. 6 connecting
structure;
[0018] FIG. 8 is a side elevation;
[0019] FIG. 9 is a perspective view;
[0020] FIG. 10 is a fragmentary front elevation, showing the head
of FIG. 8;
[0021] FIG. 11 is a fragmentary plan view on lines 11-11 of FIG. 8,
and FIG. 11a is a view like FIG. 11;
[0022] FIG. 12 is a view like FIG. 10, but showing a
modification;
[0023] FIG. 13 is an elevation showing details of an improved
version;
[0024] FIGS. 14 and 15 are sections on lines 14-14 and 15-15 of
FIG. 13;
[0025] FIG. 16 is a section on lines 16-16 of FIG. 15;
[0026] FIG. 17 is an enlarged view of shaft eccentrics at opposite
ends of a lubricant receiving space;
[0027] FIG. 18 is an elevation taken on lines 18-18 of FIG. 17;
[0028] FIG. 19 is a top plan view taken on lines 19-19 of FIG.
18;
[0029] FIG. 20 is an end view taken on lines 20-20 of FIG. 18;
and
[0030] FIG. 21 is an end view taken on lines 21-21 of FIG. 18.
[0031] FIG. 22 is a section taken on lines 22-22 of FIG. 17, to
show groove configuration.
DETAILED DESCRIPTION
[0032] Referring now to the drawings and initially, to FIGS. 1 and
2, inclusive, for this purpose, it will be seen that one type of
machine in which the invention may be incorporated has been
designated in its entirety by reference number 10. Mounted on the
machine 10 are a pair of rubber tires 12 which permit the machine
10 to be easily transported and maneuvered. The wheels 12 are
carried by an axle 14 which an turn passes through the rear
portions of the base frame 16. Mounted on the frame 16 is an
electrical motor 18. The machine 10 may alternately be powered by
an internal combustion engine. The motor 18 is held in place by
four mounting bolts 19 which pass through slots 20 in the frame 16.
When the bolts 19 are loosened the motor can be moved forward or
backward on the frame 16 by reason of the slots 20 to adjust the
tension in the drive belt 21. Covering the motor 18 and attached to
the frame 16 is a cover shroud 22. The shroud 22 slides over the
side walls 23 of the frame and is held in place by bolts 24 as can
be seen in FIG. 1. Positioned on the front of the frame 16 is a
nose weight 25. The weight is held in place by means of a
releasable wire clip 26 which fastens the forward edge of the
shroud 22 with the weight 25. The weight provides the necessary
weight on the cutting edge 28 which will later be described.
[0033] The handle bar 25 comprises a pair of elongated tubular
members 30 which are attached at their lower ends to the shroud 22,
and at their upper ends are joined by tubular cross members 31 and
32. Hand grips 33 are used to handle and maneuver the machine
10.
[0034] FIGS. 3 through 5 show the cutter head subassembly 36 in
detail. The frame 16 previously mentioned is substantially U-shaped
with a horizontal web portion 34 and a pair of vertical flanges 35
as can best be seen in FIG. 5. At the forward end of the frame 16
positioned between the webs 35 is the cutting head 38. The head 38
is formed with a web 40 and a pair of flanges 42. The cutting head
is pivotally mounted at the upper end to the frame 16 by a pin 44
which passes through both pairs of flanges 35 and 42. Passing
through the pair of flanges 35 and journalled thereto is a
rotatably mounted drive shaft 46 which is shown in FIGS. 4 and 6.
The shaft 46 is journalled at its outer ends in a pair of roller
bearings 48 which are in turn bolted to the frame flanges 35 by
means of bolts 50. Retaining the cam shaft in the bearings 48 are
pair of locking sleeves 52 which are mounted on the shaft 46
immediately outward of the bearings 48. Keyed to one end of the
shaft 46 is a sheave 54 adapted to carry a V-belt. Mounted on the
shaft 56 of the motor 18 is a similar sheave 58 which lies in the
same plane of rotation as sheave 54. The two sheaves 54 and 58 are
connected by means of a rubber V-belt 21. The tension in the V-belt
21 may be adjusted as previously discussed.
[0035] The shaft 46 extends within a first tubular part 90 of a
connecting element 91, the later also incorporating a second and
smaller diameter tubular part 92. Those tubular parts comprise
steel interconnected by a steel plate 93 welded to outer side
portions of the sections, as at 94 and 95. See FIG. 7.
[0036] Shaft 46 carries two axially spaced eccentrics 96 and 97.
See in FIG. 7 the axis 96c of eccentric 96 offset from the axis 46a
of shaft 46. Each eccentric is cylindrical to rotate within a
bearing, such as a bushing, the two bushings indicated at 98 and 99
and received in counterbores 98a and 99a in the pipe section, and
against step shoulders 98b and 99b. The large space 100 thus
provided between the eccentrics provides a lubricant (grease)
reservoir, for long lasting lubrication of the two bearings, as the
shaft rotates and as the eccentrics oscillate the shaft section 90,
and the element 91 back and forth, as will be described. Shaft
section 46b extends between and interconnects the two
eccentrics.
[0037] Note that the eccentrics have oppositely facing end portions
or faces 96a and 97a, which, due to their flaring eccentricity,
tend to positively displace the grease as the eccentrics rotate.
This serves to urge grease radially outwardly, and to feed toward
the bushings and the bearing surfaces of the eccentrics and
bushings, for enhancement of lubrication as will be referred to.
Note that faces 96a and 97a intersect the outer surfaces of the
eccentrics in planes 96b and 97b that are at angles .alpha.
relative to the shaft axis, angles .alpha. being less than
90.degree.. Grease is introduced to space 100 via a grease fitting
101 in shaft 90, as shown.
[0038] Annular elastomeric seals 102 and 103 are located at
opposite ends of the bushings, and pressed into the shaft
counterbores 102a and 103a, as shown. Those seals exert pressure on
the shaft eccentrics to prevent escape of grease.
[0039] At the opposite end of element 91 is a bearing shaft 68
journaled via bushings 66 to the pipe section 92. Shaft 68 is in
turn mounted to cutting head 38. When shaft 56 is rotated, element
91 is oscillated back and forth to cause head 38 to move back and
forth about the axis of pipe 44, as indicated by arrows in FIG.
3.
[0040] At the lower extremities of the cutting head 38 the flanges
42 become wider to accommodate the cutting blade shoe 70. The shoe
70 is adjustably held against the cutting head by two pairs of
bolts 72 and 74. The bolts 72 pass through openings 75 in the rear
of the blade shoe 70 and are threaded into the ends of the
connecting rod shaft 58. The bolts 74 pass through openings 76 and
are threaded into the ends of shaft 77. The purpose of the blade
shoe 70 is to rigidly hold the cutting blade 78 in its cutting
position. Located on the back edge of the blade shoe 70 are a pair
of adjusting bolts 80 and locking nuts 81 which allow for
adjustment of the position of the blade stop 82 which in turn
adjusts the amount of blade edge exposure. The front edge 83 of the
blade shoe 70 is tapered to provide a maximum amount of rigidity to
the cutting blade and yet permit a shallow angle of slope between
the cutting blade 78 and the flooring surface being stripped.
[0041] FIGS. 8, 10 and 11 show a modified head 138 consisting of
lightweight metal such as aluminum, or aluminum alloys, or
magnesium, or magnesium alloys. The head has two elongated flanges
142 interconnected by a web 140. The flanges are locally thickened
near upper ends of the flanges to define two widened lugs 242 that
form widened bearings openings 150 for a pivot shaft 144. The
latter is connected to the frame flanges 135 (corresponding to
flanges 35 in FIG. 5). The bearing openings (and the lugs) have
lengths "l" in access of 3/4 inch, and preferably are between 3/4
an 11/2 inches in length. As a result, destructive wear of the head
metal surrounding the openings 150 is eliminated, and in particular
or heavy duty operation where stripping forces are extensive.
[0042] The openings are sized to closely receive the pivot shaft
144, and define a common axis 144a. FIG. 11a shows modification,
with a steel tube 344 received in openings 150, and in turn
receiving the shaft 144. Tube 344 helps distribute loading to
insure against destructive wear of the lightweight metal lugs
242.
[0043] FIGS. 8 and 9 also show the use of the modified blade holder
plate 170 attached to the head 138 at its bottom side 138a. Blade
178 is clamped against that side, by the plate. Two shafts, 177 and
168 extend parallel to the web 140 and through flanges 142 to
provide shaft projections 177a and 168a at the exterior side of
each flange. Two pairs of fasteners 200 and 201 extend in parallel
relation through suitable openings in the holder plate and in the
blade, at opposite ends of the shafts, respectively. The fasteners
have heads 200a and 201a that clamp split washers 202 and 203
against the bottom of the holder plate. Also, the fasteners have
threaded shanks 200b and 201b received in threaded engagement with
threaded openings 177b and 168b in the shaft projections 177a and
168a. Accordingly, tightening of the blade in position as shown in
FIG. 9 may be accomplished using one hand 210 only, i.e. by
manipulation of the wrench 204 in grip engagement with the fastener
heads, and the blade may be held and positioned by the other hand
211.
[0044] The operation of the stripping machine 10 varies with the
type of floor being removed. The steeper the angle of the blade 78
with the floor the deeper the blade will dig. The angle can be
varied by lifting the wheels 12 off the floor. The angle can also
be varied by extending the blade 78 further past the edge of the
shoe 70. When removing a plywood or particle board floor an extra
long blade which extends an additional four inches or more past the
edge of the shoe 70 has proven very useful. The longer the blade 78
is extended out of the shoe the less the angle between the cutting
blade and floor. The amount of Weight applied to the cutting edge
28 is also variable depending upon the flooring being removed. The
weight can be varied by the amount of pressure applied by the hands
to the handle bar 29. Generally, the machine best operates when the
handle bar 29 is lifted up until the wheels are one-half-inch off
the floor. When an exceptionally tough flooring is being removed, a
blade with teeth formed on the cutting edge has been found to be
very effective.
[0045] FIG. 12 is a view like FIG. 10, with corresponding elements
having the same identifying numbers. It differs from FIG. 10 in the
provision of bushings 280 and 281 fitted and retained in bores 282
and 283 in lugs 242. The bushings may endwise fit against stop
shoulders 284 and 285 in the lugs. The bushings may advantageously
be self-lubricated, as provided by annular material 280a and 281a
carried in metallic (as for example bronze) sleeves 280b and 281b
press-fitted in bores 282 and 283. Material 280a and 281a may for
example consist of molybdenum disulfide. One example of such
bushings are known "OILITE" bushings.
[0046] Pivot shaft 144 (typically steel) is received in, and has
low friction running fit in, the bores of the annuli 280a and 281a,
for long lasting, low wear operation.
[0047] FIGS. 13-16 show an improved form of the head 338 and
connector 391. (Elements corresponding to those of FIGS. 1-11 have
the same numbers, with "3" preceding each number).
[0048] Connector 391 is a casting made of lightweight metal such as
zinc or aluminum, and has first and second tubular parts 390 and
392, the outer diameter of part 390 for example being about 15/8
inches, and that of part 392 being about 11/4 inches. Self
lubricated bushings or bearings 398 and 399 are press fitted into
bores 398a and 399a of part 390. Shaft 346 is as described before,
and as shown in FIG. 6, where it bears number 46.
[0049] The connector 391 also includes two legs 400 and 401 which
extend substantially parallel between tubular parts 390 and 392 and
merge therewith, at the opposite ends of the legs, at locations
spaced from the opposite ends of the tubular parts 390 and 392. The
legs have first webs 401a and 401b which define planes 402 normal
to parallel axis 403 and 404 defined by parts 390 and 392. Those
planes also intersect the enlarged, heavy duty lugs 442 integral
with head 338, for maximum strength.
[0050] The legs also have second webs 401c and 401d defining planes
405 normal to planes 402, and parallel to spaced parallel axis 403
and 404. Second webs 401c and 401d merge with the tubular parts or
elements 390 and 392 along the sides thereof facing one another, as
shown. Webs 401a and 401b intersect webs 401c and 401d at
mid-region 406 (see FIG. 16), and all four webs taper outwardly,
away from that region, as shown to form a cross. Accordingly, a
high strength, low weight, connection of parts 390 and 391 is
formed, utilizing a light-weight, unitary metal casting. Mid-region
406 is enlarged, for added strength, and webs 401a-401d maximally
resist relative bending of parts 390 and 392.
[0051] The flanges 342 have widths "w" that increase in dimension
in direction toward the plate 370 and blade 378, as shown in FIG.
15, and the tubular part 392 is confined between those flanges,
with the webs 401a-401d merging with part 392 between the flanges
of increased width near plate 370.
[0052] Self-lubricated bushings are employed at 380 and 381, in the
two lugs 342, to receive tubular shaft 344. "OILITE" bushings may
be used for this purpose.
[0053] The head 338 may also consist of the same lightweight metal
as connector 390, whereby a very lightweight assembly is provided
for minimum vibration transmission to the user.
[0054] Referring to FIGS. 17-22, they show preferred forms of the
shaft 46 and eccentrics 96 and 97 in greater detail. Grooves are
sunk in the outer surfaces 200 and 201 of the eccentrics, the
grooves indicated at 202 and 203. Each groove spirals along and
about the length of the eccentric, and typically about 360.degree.
around and along the eccentric body. The grooves have grease
entrance ends 202a and 203a at axially spaced locations closest to
the center of 100, in communication with outer portions of the
lubricant receiving space 100, at its opposite ends. Each groove
typically extends from its entrance end at one end wall of the
eccentric to the opposite end at the opposite end wall of the
eccentric. A single spiral, or about such a single spiral, from end
to end of the eccentric maximizes grease exposure to different
areas of the bearings, while minimizing groove length.
[0055] Grease is urged, under centrifugal pressure, into and along
the spiral length of the groove, for distribution to the bearing
cylindrical surfaces 98a and 99a that extend about the outer
surfaces of the two eccentrics, for assured optimum lubrication.
Each groove typically has width "w" which is about 0.125 inch, and
depth "d", which is about 0.015, as indicated in FIG. 22. Seals 102
and 103 at the ends of the eccentric block leakage of grease from
the lubricated spaces between the eccentrics and bearing bushings,
to which lubricant such as grease is pressure fed via the spiraling
grooves. The eccentric shaft end portions are indicated at
46b-46c.
[0056] The spiraling grooving extends eccentrically relative to the
shaft axis of rotation; and rotation of the grooving about the
shaft axis effects pulsing centrifugal force application to the
eccentrically rotating lubricant in the groove and outward
vibration or pulsing of the lubricant in the grooving toward the
surrounding surface of the bearing, enhancing the lubrication
distribution effect and effectiveness.
* * * * *