U.S. patent number 3,868,738 [Application Number 05/392,026] was granted by the patent office on 1975-03-04 for self-propelled automatic bowling lane maintenance machine.
This patent grant is currently assigned to Western Sales and Supply Co.. Invention is credited to Daniel R. Horst, Donald E. Ingermann.
United States Patent |
3,868,738 |
Horst , et al. |
March 4, 1975 |
SELF-PROPELLED AUTOMATIC BOWLING LANE MAINTENANCE MACHINE
Abstract
This invention relates to a self-propelled machine for
automatically oiling and buffing the lanes in a bowling alley and,
more specifically, to a piece of apparatus of the type
aforementioned that includes a novel brake and cam-operated
function control mechanism. The brake is characterized by a
wedge-shaped shoe spring-biased upon deactuation of a solenoid
holding same disengaged into an annular, inwardly-tapered, groove
encircling a drum rotatable with the driveshaft. The cam-operated
control mechanism, on the other hand, includes distance and
function control cams mounted on separate cam shafts operatively
coupled to one another and to the main drive by yieldable friction
clutches for conjoint rotation while, at the same time, permitting
each such subassembly to be adjusted independently and relative to
the other two.
Inventors: |
Horst; Daniel R. (Erie, CO),
Ingermann; Donald E. (Arvada, CO) |
Assignee: |
Western Sales and Supply Co.
(Denver, CO)
|
Family
ID: |
23548955 |
Appl.
No.: |
05/392,026 |
Filed: |
August 27, 1973 |
Current U.S.
Class: |
15/4; 15/98 |
Current CPC
Class: |
A47L
11/4066 (20130101); A47L 11/00 (20130101); A47L
11/4069 (20130101); A47L 11/4055 (20130101); A47L
11/408 (20130101); A47L 11/4041 (20130101); A63D
5/10 (20130101); A47L 11/4011 (20130101); A47L
2201/04 (20130101) |
Current International
Class: |
A47L
11/00 (20060101); A63D 5/00 (20060101); A63D
5/10 (20060101); A47l 011/282 () |
Field of
Search: |
;15/4,98,103.5
;118/202,4,7 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Roberts; Edward L.
Claims
What is claimed is:
1. In combination in an automatic bowling lane maintenance machine:
a carriage; a reversible drive mechanism housed within said
carriage including a drive shaft and surface-engaging drive wheels
mounted on said shaft operative to advance same along a
predetermined course in a forward and reverse direction;
lane-buffing means including a roller and drive therefor, said
roller being journalled for rotation in lane-contacting relation
about a horizontal axis extending transversely of the direction of
machine travel; lane-dressing means detachably connectable to the
lane buffing roller including a reservoir for the storage of a
lane-dressing fluid and fluid transfer means, said reservoir being
mounted adjacent the lane buffing roller for movement relative
thereto between an extended and a retracted position, and said
fluid transfer means being operative in the extended position of
said reservoir to transfer fluid therefrom to the surface of said
lane-buffing roller; cam-controlled means connected to the
reservoir operative upon actuation and deactuation to shift same
between its extended and retracted positions; cam means connected
to the cam-controlled means operative to actuate and deactuate
same; power transfer means connected to the carriage drive
mechanism; and, manually adjustable means operative upon actuation
to vary the distance over the forward and reverse travel of the
machine during which the dressing is applied to the lane surface,
said means comprising a yieldable friction clutch operatively
interconnecting the power transfer means and cam means to define an
adjustable driving coupling therebetween.
2. The combination as set forth in claim 1 in which: the fluid
transfer means comprises a second roller journalled for rotation in
tangential contacting relation to the first of said rollers and
wick means projecting from said reservoir operative to transfer the
lane dressing fluid contained therein when in its extended
operative position to the surface of said second roller.
3. The combination as set forth in claim 1 in which: the
cam-controlled means comprises spring means biasing said reservoir
in one direction, electric servo-motor means operative upon
actuation to shift said reservoir in the opposite direction in
opposition to said spring means, and a servo-motor operating
circuit including a cam-actuated switch.
4. The combination as set forth in claim 1 in which: the second
power transfer means includes a shaft mounting the cam means for
conjoint rotation therewith and a driven member operatively
connected to the carriage drive means mounted on said shaft for
independent movement relative thereto, said friction clutch means
being interposed between said driven member and cam means to define
the yieldable operative coupling between the latter and said
carriage drive mechanism.
5. The combination as set forth in claim 1 which includes:
cam-controlled reversing means connected to the reversible carriage
drive mechanism operative upon actuation to reverse the direction
of the latter; second cam means connected to the cam-controlled
reversing means operative to actuate and deactuate same; and, a
second yieldable friction clutch interconnecting the second cam
means and power transfer means operative to define an adjustable
driving coupling therebetween.
6. The combination as set forth in claim 5 in which: the second
power transfer means includes a first shaft mounting the first cam
means for conjoint rotation therewith, a second hollow shaft
mounted on the first for independent relative coaxial rotation,
said second shaft mounting the second cam means for conjoint
rotation, and in which said second friction clutch is interposed
between the said first and second cam means to define a yieldable
driving coupling therebetween.
7. The combination as set forth in claim 6 in which: the second
shaft is slidable axially relative to the first; and, in which a
spring engages the second cam means and biases same toward the
first so as to squeeze the second friction clutch means
therebetween.
8. The combination as set forth in claim 7 in which: the first cam
means is movable toward the clutch-engaging element of the power
transfer means; and, in which the spring is operative through the
second cam means and a second friction clutch means to bias said
first cam means toward said clutch-engaging means to squeeze the
first friction clutch means therebetween.
9. The combination as set forth in claim 1 which includes: brake
means associated with the reversible drive mechanism operative to
stop same, said means comprising a brake drum with an annular
V-groove in its surface mounted on the drive shaft for rotation
therewith, a wedge-shaped brake shoe mounted for reciprocating
movement between a retracted disengaged position and an extended
engaged position wedged into said V-groove, spring means biasing
said brake shoe in one direction, a second servo-motor means
connected to said brake shoe operative upon actuation to move same
in the opposite direction in opposition to said spring means, and
second servo motor actuating means interconnecting said second
servo-motor means and reversible carriage drive operative to set
the brake and stop the carriage whenever said carriage drive is in
operation.
10. The combination as set forth in claim 1 in which: one of the
clutch engaging elements of the power transfer means or cam means
is adjustable relative to the other such element; and, in which a
spring engages said adjustable element and normally biases same
toward the other so as to squeeze the friction clutch
therebetween.
11. The combination as set forth in claim 2 in which: a second
power transfer means operatively interconnects the reversible
carriage drive mechanism and said second roller so as to define a
driving connection therebetween.
Description
Self-propelled automatic bowling alley maintenance machines of
various types are well known in the art with some of them, like
that forming the subject matter of U.S. Pat. No. 3,604,037, being
quite sophisticated and performing a number of different functions
in sequential relation much in the same way as one would do by
hand. Such units are even capable of substituting one function for
another and performing two or more simultaneously. In bowling
alleys having many lanes, these units are efficient time and labor
savers while, at the same time, enabling the operator to keep his
establishment in top condition. Machines such as that exemplified
by the aforementioned patent are, however, quite expensive and some
operators find it necessary to forego the luxury of owning one or
more of them and they must, therefore, settle for hand labor or, at
least, something less in the way of an automatic or semi-automatic
unit.
There are several features of full-service machines like that
previously referred to which make them expensive, yet which, if
they could be eliminated or at least simplified to some degree,
would lessen their cost of manufacture and bring the price down to
within the range of the smaller bowling alley proprietor. Among
these costly complications are such things as alternative modes of
operation where the operator at his option may choose fully
automatic, semi-automatic or even manual operation for all or some
part of the cycle. Another complex mechanical structure is that of
retractable rollers which extend into operative position only when
performing their respective functions while remaining drawn up
inside the housing at all other times. One particularly
distributing feature is the inability of certain machines during
automatic operation to correct for improper programming in the
event of some malfunction. Probably the worst contributing factor
of all, however, is the complex electrical control system with its
multitude of switches, switch actuators, solenoids, relays and
sensors necessary to initiate and terminate the various automatic,
semi-automatic and manual functions the machine is programmed to
perform as alternatives available to the user.
It has now been determined in accordance with the teaching of the
instant invention that these and other costly features of the prior
art bowling lane maintenance machines can be eliminated or at least
rendered less expensive by the simple, yet unobvious, expedient of
doing away with the manual and semi-automatic options in favor of a
far simpler fully automatic machine which upon being started will
move down the lane, perform its preprogrammed operations, return to
the starting point and shut itself off. The control system also
incorporates a unique arrangement of distance and function control
cams that are operatively interconnected with one another and with
the power take-off from the main drive for conjoint rotation, yet,
are also linked together by friction clutches that define yieldable
couplings permitting each subassembly of the three to turn
independently of the other two. In addition, the braking system is,
likewise, considerably simplified in that it is spring-biased into
engaged position while a solenoid is employed to disengage same.
The wedge and mating groove braking surfaces are self-adjusting for
wear yet provide a positive braking action at all times. Despite
the aforementioned simplifications and the elimination altogether
of the roller retracting functions, the machine retains a good deal
of its multi-functional capability.
It is, therefore, the principal object of the present invention to
provide a novel and improved bowling alley maintenance
apparatus.
A second objective of the within-described invention is the
provision of a unit of the type aforementioned which is fully
automatic and requires manual attention only to plug it in, start
the cycle and move the machine from one lane to the next.
Another object of the invention is to provide a device for
conditioning and cleaning bowling lanes that can be preprogrammed
as to both the distance it travels and the portion of such distance
the dressing is applied.
Still another objective is to provide apparatus for applying a
dressing to bowling lanes that automatically prevents the oil from
being applied during the return run while the lane is being both
dusted and buffed.
An additional objective is to provide a novel braking system and
unique cam-operated distance and function control system for
bowling lane maintenance machines.
Further objects are to provide a device of the type herein
disclosed and claimed that is simple, efficient, relatively
inexpensive, reliable, easy to service, reasonably compact,
versatile and even decorative in appearance.
Other objects will be in part apparent and in part pointed out
specifically hereinafter in connection with the description of the
drawings that follow, and in which:
FIG. 1 is a perspective view looking down upon the bowling lane
maintenance unit from a point above the left rear corner
thereof;
FIG. 2 is a top plan view with the cover removed;
FIG. 3 is a bottom plan view;
FIG. 4 is a section taken along line 4--4 of FIG. 3;
FIG. 5 is a fragmentary section to a greatly enlarged scale taken
along line 5--5 of FIG. 2 showing the cam-operated control
mechanism;
FIG. 6 is a fragmentary section taken along line 6--6 of FIG.
5;
FIG. 7 is a fragmentary section taken along line 7--7 of FIG.
5;
FIG. 8 is a fragmentary section taken along line 8--8 of FIG.
5;
FIG. 9 is a fragmentary section taken along line 9--9 of FIG.
5;
FIG. 10 is a still further enlarged fragmentary axial section of
the camshafts, cams, clutches and associated drive elements;
FIG. 11 is an enlarged fragmentary section taken along line 11--11
of FIG. 2;
FIG. 12 is a fragmentary top plan view of the brake subassembly to
the same scale as FIG. 11;
FIG. 13 is a fragmentary section taken along line 13--13 of FIG.
11; and,
FIG. 14 is a circuit diagram of the electrical system.
Referring next to the drawings for a detailed description of the
present invention and, initially, to FIGS. 1-4, inclusive, for this
purpose, reference numeral 10 has been chosen to designate the
bowling lane maintenance apparatus forming the subject matter
hereof in its entirety while numeral 12 designates the wooden
bowling lane over which it rides. Reference numeral 14 designates
the gutters alongside the lane and numeral 16 the foul line at its
near end.
The various functional elements of the apparatus which will be
described in detail presently are all contained within a sheet
metal housing that has been indicated in a general way by numeral
18 and which includes right and left side panels 20 and 22, front
and rear panels 24 and 26, a bottom 28 and a two-part hinged deck
30. The rear door 32 of deck 30 covers the main drive mechanism
that has been broadly referred to by reference numeral 34 and the
rear compartment 36 separated from the latter by transverse
partition wall 38 which houses both the buffing subassembly 40 and
the oiling subassembly 42 for the latter. A partition wall 44
extending transversely along the front of the center compartment 46
that houses the drive mechanism 34 separates the latter from front
compartment 48 that contains the dusting subassembly that has been
generally designated by numeral 50. The front door 52 of the deck
30 covers front compartment 48 and is attached to the rear door 32
by a common piano-type hinge 54.
Rear partition wall 38 has an upwardly and rearwardly inclined
extension 56 that defines a control panel to which the various
switches, lamps, fuse holders and footage indicator 58 are attached
as shown in FIG. 1. The rear door has a similarly-inclined step 60
intermediate its front and rear margins that mates with the control
panel and has windows 62 cut therein to receive the various knobs,
bulbs and the like. All of the foregoing elements of the present
unit are found in the machine forming the subject matter of U.S.
Pat. No. 3,604,037 already referred to.
The drive mechanism 34 is, likewise, essentially the same as that
which is revealed in the above patent and, for this reason, will be
given only brief mention for which purpose reference will be had to
FIGS. 2, 3 and 4. A main drive shaft 64 extends transversely across
the center compartment 46 and is mounted for rotation in journals
66 fastened to the side plates. Pillow blocks 68 also journalling
the shaft are provided at various locations intermediate the ends
thereof.
Low-speed gear motor 70 powers the main drive and its output shaft
72 is operatively connected to the drive shaft 64 by a toothed belt
and pulley power transfer mechanism 74. Mounted out near the
extremities of the driveshaft for conjoint rotation therewith are
the main drive rollers 76 which operate through suitably-placed
openings 78 in the bottom 28 of the housing, all of the
last-mentioned elements having been shown most clearly in FIGS. 11
and 12.
In FIGS. 2 and 4, it can be seen that main drive shaft 64 is the
source of power used to turn intermediate shaft 80 located in the
rear compartment 36, a belt and pulley power transfer mechanism 82
providing the operative connection therebetween. Shaft 80 is
journalled in brackets 84 fastened to the rear partition wall and
oiler shaft 86 is mounted for arcuate movement about the latter as
an axis and in fixed-spaced parallel relation thereto by a pair of
arms 88 connected therebetween. Both shafts 80 and 86 are
journalled within arms 88 for relative rotation. Oil transfer
roller 90, on the other hand, of the oiler subassembly 42 is
fixedly mounted on shaft 86 for conjoint rotation. Still another
toothed belt-and-pulley power transfer mechanism 92 defines a
driving connection between intermediate shaft 80 and oiler shaft
86.
Mounted for rotation in rear compartment 36 beneath oil transfer
roller 90 is the main buffer drum 92, the stub shafts 94 projecting
from its ends being housed in journals 96 fastened to the
sideplates. Drum 92 is covered by a tubular buffer element 98 (FIG.
4), the two of which cooperate with one another and shaft 94 to
produce the buffing subassembly 40. Buffer element 98 forms the
subject matter of assignee's copending application Ser. No.
326,762, filed Jan. 26, 1973, and entitled TUBULAR BUFFER ELEMENT.
The buffer is exposed to the surface of the lane through the open
bottom of the rear compartment 36 as shown in FIGS. 3 and 4.
The buffer drive and control therefor will be described presently,
however, in the meantime, the remaining novel features of the oil
transfer subassembly 42 will be set forth in detail with particular
reference to FIGS. 2, 3 and 4. Mounted on the inside of the rear
housing wall 26 for tiltable movement about a transverse axis,
defined by stub shafts 100 located adjacent the bottom wall thereof
is an oil reservoir 102. An elongate upwardly opening slot 104 is
provided in the front of the reservoir adjacent its upper edge.
Extending down into the oil lane dressing in the bottom of the
reservoir is a felt wick 106, the upper part of which emerges from
the slot and wipes the rear surface of the oil transfer roller 90
with oil preparatory to transferring the latter to the buffer which
is in rolling tangential contact therewith. The wick picks up the
oil by capillary action in the well known manner and, in addition
to wetting the transfer roller therewith, it exerts a wiping action
thereon adapted to spread it out into a thin uniform film.
A compression spring 108 interposed between the inside of the rear
housing wall 26 and upstanding bracket 110 mounted atop the oil
reservoir is effective to bias same forwardly and hold the wick in
positive engagement with the oil transfer roller. This same spring
functions through the medium of the reservoir to bias the oil
transfer roller down on top of the buffer as shown in FIG. 4. While
the weight of the roller 90 out on the ends of pivoted arms 88 is
ordinarily sufficient to hold it in firm rolling contact with the
buffer, spring 110 provides a positive biasing action supplementing
the latter gravitational effect. Spring 112 serves still another
function and that is to return solenoid 114 (FIGS. 2 and 14) to its
retracted position upon deactuation. The push rod 116 of this
solenoid engages the front of bracket 110. While on the subject of
solenoid 114, it would be well to point out in connection with
FIGS. 2 and 4 that it functions upon actuation to tilt the
reservoir rearwardly into the broken line position of the latter
figure. As it does so, the wick moves rearwardly out of contact
with the oil transfer roller which, obviously, means that no more
oil is deposited on the surface of the latter.
As previously noted, the main drive shaft 64, intermediate shaft 80
and oiler roller shaft 90 are all turned relatively slowly by gear
motor 70, however, this is not true of the buffer subassembly 40
which must rotate quite fast. It, therefore, has its own separate
drive motor 118 mounted on the bottom wall of the center or main
housing compartment 46 as shown in FIGS. 2 and 4. A simple
V-belt-and-pulley power transfer mechanism 120 provides the
operative connection between said buffer drive motor and the buffer
itself. A slot (not shown) is provided in rear partition wall 38
for the passage of the V-belt between the middle and rear
compartments.
Brief reference will next be made to FIGS. 2, 3 and 4 for a
description of the duster subassembly 50 housed in the forward
compartment 48. A supply roll 122 is journalled for rotation in the
top of the forward compartment near the rear thereof. A pair of
inverted, generally L-shaped brackets 124 are mounted for pivotal
movement on opposite sides of the housing about an axis defined by
the supply roll 122. A rubber-covered dusting roller 126 is
journalled for rotation in the bottom of the forward compartment at
the ends of the downturned legs of the L-shaped brackets as shown
in FIG. 4. Take-up roll 128 is, likewise, journalled for rotation
between the L-shaped brackets but forwardly of the supply roll and
above the dusting roller. The web of dusting cloth 130 passes off
of the supply roll, underneath the dusting roller, up around a
stationary idler roller 132 journalled between the sideplates of
the housing forwardly of the brackets, and back onto the take-up
roll 128. Tension springs 134 connected between the L-shaped
brackets and sideplates normally bias the dusting roller down into
contact with the surface of the lane. The yieldable mounting of the
three rollers 122, 126 and 128 on the L-shaped brackets 124
cooperate with the stationary idler roller 132 to permit the
dusting subassembly 50 thus formed to ride up over obstructions
while keeping a constant tension on the dusting web. Note that the
motor 136 that drives the take-up roll through suitable reduction
gearing 138 is mounted on one of the L-shaped brackets as shown for
movement therewith and with the other elements of the yieldable
subassembly.
Directing the attention next to the remainder of the apparatus
housed in the central compartment 46, reference will next be made
to FIGS. 2 and 4 through 10, inclusive, for detailed description of
the cam-actuated control system which has been broadly designated
by reference numeral 140. Output shaft 72 of the main drive motor
70 carries a second belt and pulley power transfer mechanism 142 of
the toothed type which drives worm shaft 144 journalled for
rotation across the lower end of control box 146 fastened to the
underside of the control panel 60 by suitable brackets. This worm
shaft carries a worm 148 that, in turn, drives a worm gear 150
within the hub of which is journalled inner cam shaft 152. Inner
cam shaft 152 has a pointer 154 attached thereto for conjoint
rotation relative to a footage scale 156 on the face of the control
panel or dashboard.
A pair of microswitches 160 and 162 are mounted inside the control
box in position to be engaged and actuated by flat-sided
switch-actuating cams 164 and 166, respectively. Of the two, only
cam 166 is mounted for conjoint rotation with the inner cam shaft
152. In the particular form shown, cam 166 is not fastened directly
to shaft 152 but, instead, is fixedly fastened to hub 168 which is,
in turn, similarly fastened to shaft 152. Still another element is
fastened to inner cam shaft 152 for conjoint rotation and that is
clutch plate 170. Accordingly, when the inner cam shaft 152
rotates, clutch plate 170, hub 168, cam disc 166 fastened to hub
168, and pointer 154 turn together relative to distance scale 156
and to stop pin 172 adjustably mounted relative to the footage
scale in arcuate slot 174.
Cam 166 is actually the so-called "distance" cam that determines
how far the machine will move along the lane before it stops,
reverses direction and returns to its starting point. If, for
example, the operator wants the unit to move 45 feet down the lane,
stop and come back, he sets the stop 172 opposite 45 feet on the
distance scale. Then, with pointer 154 set to indicate zero footage
on the distance scale, cam 166 will be adjusted on shaft 152 so
that it just releases switch 162 controlled thereby into its open
or deactuated condition.
When the machine is started, therefore, pointer 154 will read 45
feet on the distance scale, the rolling contact of switch 162 will
be riding on the high side of the cam 166, and switch 162 will be
closed to actuate the drive motor 70 in a direction to advance the
machine forwardly along the lane from the foul line toward the pin
deck. The inner cam shaft will begin to turn counter-clockwise as
viewed in FIG. 6 along with worm gear 150 which is operatively
connected thereto by means of friction disc 176 interposed between
it and the clutch plate 170 that forms a yieldable driving
connection therebetween. Once the shaft 152 has rotated the pointer
back to zero indicating the machine has advanced 45 feet down the
lane toward the pin deck, the rolling contact on the switch arm of
switch 162 will fall off the high side of the cam 166 which, by the
way, is the function about to take place in FIG. 9, and actuate the
motor reversing circuit in a manner to be described in detail
presently. Then, the machine will back away from the pin deck and
toward the foul line until feeler switch 178 on the side thereof
reaches the end of the gutter and actuates to shut the unit off.
During the return trip, shaft 152 is turning clockwise and switch
162 is again closed while its rolling contact rides on the high
side of cam 166. By adjusting stop 172 along the distance scale,
the operator need only grasp pointer 154 and rotate it over against
the latter to reset cam 166 for a different distance of travel. Due
to the yieldable friction coupling defined by clutch disc 176, cam
166 can be reset (rotated) relative to worm gear 150 without having
to loosen the cam on shaft 152.
In a similar fashion, oiler cam 164 is adjustable relative to worm
gear 150. To do so, a hollow outer cam shaft 180 is telescoped over
the inner cam shaft 152 for independent rotational movement
relative thereto in coaxial relation. Cam 164 is fastened to this
outer cam shaft for conjoint rotation as is a pointer 182 that
sweeps across the same distance scale 156 as pointer 154 but is
mounted inside the latter. An arm 184 is also mounted on the inter
cam shaft for rotation therewith relative to a fixed limit stop 186
fastened to the control box as shown. Arm 184 is adjustable on
shaft 180 by merely loosening its set screw and resetting same.
Now, the driving connection between the inner and outer cam shafts
is produced by a friction disc 188 interposed between the opposed
faces of the cams 168 and 166 that lie side-by-side and by
compression spring 190 that is connected between the control box
wall and cam 164 so as to continuously bias the latter against its
companion cam as shown in both FIGS. 5 and 10. Thus, the inner and
outer cam shafts are operatively linked together by friction clutch
188 so as to rotate together.
Oiler cam 164 controls the oiling cycle of the unit in much the
same way as the distance cam governs the distance it travels.
Initially, arm 184 would be set on outer cam shaft 180 so as to
engage stop pin 186 when the pointer 182 is at that footage on the
distance scale where the oiling operation is to cease. Cam 164 must
be set so that it closes switch 160 actuated thereby when pointer
182 returns to zero on the distance scale. If, for example, the
operator wants to oil the lane for 15 of the 45 feet the machine is
set to travel, he will set the arm 184 to engage stop pin 186 when
the pointer reads 15 on the distance scale.
As the unit is set in motion at the foul line, worm gear 150 will
turn the inner cam shaft 152 counterclockwise as viewed in FIG. 6
and clutch disc 188 together with spring 190 will cooperate to turn
outer cam shaft 180 in the same direction and at the same speed.
Pointer 182 will begin moving downscale towards zero while the
roller on the switch arm of switch 160 is riding on the low or
"dwell" side of cam 164 leaving switch 160 in its normally open
condition instead of closed as was the case with switch 162. This
means that spring 112 is biasing the oil tank out away from wall 26
and holding the wick 106 against intermediate roll 90. As
previously noted, oil is transferred to the lane and buffed onto
its surface during this operation.
As the unit advances 15 feet down the lane, pointer 182 returns to
zero at which point the roller on the switch arm of switch 160
rides up onto the high side of cam 164 and closes it. Once switch
160 closes, solenoid 114 energizes to move oil reservoir 102 into
its retracted inoperative position, whereupon, the transfer of oil
to the lane stops. As long as switch 160 remains actuated, no more
oil will reach the lane. Also, the distance cam 166 will allow
switch 162 to reopen and actuate the motor reversing circuit before
switch 160 leaves the high side of cam 164 and is allowed to reopen
thus deenergizing solenoid 114 and permitting the oiling cycle to
commence again. As will be seen presently, once the return trip of
the unit commences, the control circuit sets itself so that the
oiler subassembly remains inactive. This becomes important in case
the operator inadvertently sets the oiler pointer 182 farther up
scale than the distance pointer 154. What happens is that when the
distance set on the distance pointer is reached, cam 166 will
actuate switch 162 to reverse the polarity to drive motor 70 thus
starting the machine back to the foul line and, at the same time,
deactivating the oiler subassembly until the complete cycle is
commenced over again.
To change the oiling distance, the operator must loosen arm 184
from the outer cam shaft and reset it to engage the stop pin 186
when pointer 182 reads the proper distance on scale 156. This, of
course, is somewhat different than the way the inner cam shaft stop
pin was adjusted but, obviously both could be set the same way. At
the beginning of any operating cycle, the operator need only grasp
the pointers 154 and 182 and turn them clockwise against their
stops to ready the unit for operation. If, for some reason, either
cam has moved relative to the other or to the worm drive, all of
which they are free to do because of the yieldable friction
clutches, they can be returned instantly to their predetermined
positions by following the reset procedure just mentioned.
Also, if, perchance, a switch malfunctions or something else
happens of a similar nature, the drive can keep running without
tearing up the cams, cam shafts and the like even though the arms
are against their stops. This feature is, of course, not present in
those machines like that forming the subject matter of assignee's
issued patent that have only solid mechanical connections and no
yieldable ones.
Before turning to the circuit diagram of FIG. 14 for a description
of the operation of the unit, reference will next be made to FIGS.
2, 11, 12 and 13 for a description of the brake subassembly
illustrated therein and broadly designated by reference numeral 192
mounted on the main drive shaft 64 for rotation therewith is a
brake drum 194 encircled by an inwardly tapered annular groove 196.
A solenoid 198 is mounted on the bottom wall of the housing with
its plunger 200 movable in a direction normal to the axis of drive
shaft rotation. Tension spring 202 connected between the front
partition wall 44 and the plunger normally biases the latter into
extended position; whereas, upon actuation of the solenoid, it
overcomes the spring bias and retracts.
A generally L-shaped extension 204 is attached to the end of the
plunger with the horizontal leg 206 thereof housed for
reciprocating slidable movement in tunnel-forming guide member 208
fastened to the bottom of the housing in alignment with groove 196
in the drum. A relatively narrower neck 210 projects from the
horizontal leg 206 of the L-shaped extension defining a further
extension thereof to which is attached the wedge-shaped brake shoe
212. The shape of this shoe is complementary to the shape of the
groove 196 and, upon deactivation of solenoid 198, spring 202
functions to pull said shoe into tight frictional engagement with
the drum as shown in FIG. 12. As the shoe wears, it merely seats
deeper in the groove and is, therefore, self-adjusting.
Finally, reference will be made to FIG. 14 for a detailed
description of the control circuit. As soon as the machine is
plugged in, pilot light 214 lights to indicate its "on" condition.
Presumably, the distance-control and oiler-control stops have been
pre-set and the operator need only turn the pointers operatively
associated therewith against same to program the unit to perform as
intended. To start the unit, its main "on-off" switch 216 and
interlock switch 218 are simultaneously actuated into closed
position. This is accomplished by a common switch actuator (not
shown) that operatively interconnects them together for
simultaneous actuation. When switch 216 closes, its two normally
open contacts 216(1) and 216(2) close also. Power then is connected
through terminal board connector TB5 and contacts 216(1) to the
buffer motor 118. Power from this same connector is connected to
terminal board connector TB9 through the other pair of contacts
216(2). The duster motor 136 is, likewise, energized through
contacts 216(2) and terminal connector TB9.
Special function switch 220 will be described in detail presently
but, for the time being, it will be noted that a current path is
established via TB9, through its normally closed contacts 220(1)
and momentary interlock switch 218 to the coils of relays 222 and
224 which are connected in parallel with one another. As relay 224
is actuated, its normally open contacts 224(1) will close
establishing a path through normally closed cam-actuated switch 162
that holds around interlock switch 218 that has reopened.
When the coil of relay 222 is energized, its normally-open contacts
222(1) close and brake solenoid 198 is energized to disengage the
brake 212 and release the main drive shaft. A current path to the
starting winding of main drive motor is also established through
the closing of normally open contacts 222(1), 222(2) and 222(3).
When the starting winding drops out, the main winding of drive
motor 70 is kept energized through the closure of normally open
contacts 222(1) and motor leads "A." Thus, with the brake
disengaged and the main drive motor 70 started and running in the
forward direction, the machine moves off the foul line and down the
lane toward the pin deck.
If we assume an automatic lane dressing function is to be
performed, then triple-pole double-throw switch 226 and double-pole
double-throw switch 228 will be actuated as shown. TB9 is, of
course, hot at this point and the center terminals 226(0) of switch
226 are connected thereto. Now, with relay 224 actuated, a current
path will be established to pilot light 230 via TB9, contacts
226(0) and 226(1) of switch 226, cam-actuated switch 160, the
normally-open contacts 224(2) of relay 224 which are now closed,
and contact 228(1) of switch 228. Pilot 230 is lit whenever the
unit is oiling and it will be remembered that the oiler subassembly
is operative whenever solenoid 116 is deenergized which is the case
by virtue of the position of cam-actuated switch 160 on its contact
160(1) as shown. When, however, the cam 164 ceases to hold switch
160 onto its normally open contact 160(1) and releases it onto its
normally closed contact 160(2), solenoid 116 will energize to
retract the reservoir and shut off the oil supply to the buffer via
the current path through 226(0) and 226(1). As switch 160 is
actuated, however, the circuit to pilot light 230 is broken and it
goes out.
At this point, the machine is no longer applying oil to the lane
but it is still moving forwardly toward the pin deck with both the
duster motor 136 and the buffer motor 118 still energized along
with the main drive motor 70. Next, the machine will have traversed
the pre-set distance and the distance cam 166 will have released
the cam-actuated reversing switch 162 controlled thereby so as to
return to its normally closed contact 162(2) from the normally open
contact 162(1) it has been held against. When this switch opens,
the holding contacts 224(1) of relay 224 will reopen thus
deenergizing the coil and dropping out the relay. Even with relay
224 deenergized, a current path still exists to solenoid 116 via
TB9, 226(0), 226(1) and contact 160(2) of cam-actuated switch 160
that keeps the oil reservoir retracted. When the main drive motor
70 reverses direction in a manner which will be explained
presently, it will reverse cam 164 and eventually reactuate switch
160 again over onto its normally open contact 160(2). Even so, the
oil reservoir retraction solenoid 116 remains energized via TB9,
226(0), 226(1), normally closed contacts 224(3) of deenergized
relay 224, and normally closed contact 160(2) of switch 160. With
the oiler subassembly thus deactivated, pilot 230 remains
extinguished as the only path thereto is through normally open
contact 224(2) which is open.
When cam-actuated distance switch 162 opens, the coil of relay 222
is also deenergized returning its contacts to their normal
condition. Actually, a mechanical delay (not shown) is incorporated
into the reversing unit which delays the energization of the main
drive motor in the opposite or reverse direction for a second or
two while the machine is braked to a complete stop. Then, the
starting winding is again energized but in the opposite direction
by means of the current path established via TB9 again and normally
closed contacts 222(3), 222(4) and 222(5). When the starter winding
drops out, the main winding remains energized through 222(3) and
leads "A" as before. This same set of normally closed contacts
222(3) energize the brake solenoid 198 to keep the brake 212
disengaged. As soon as the machine starts on its return trip back
to the foul line, cam 166 will, once again actuate distance switch
162 over onto its normally open contact 162(2); however, in so
doing, it does not reenergize relay 224 or, for that matter, relay
222 connected in parallel therewith because normally open contacts
222(1) remain open and interlock switch 218 is still open.
Finally, when the machine returns to the foul line, feeler 178
(FIG. 1) on the start-stop switch 216 that has been riding in the
bottom of the gutter alongside the lane will reach the shoulder
(not shown) at its lead end and be raised up thereby reopening
same. This completes the automatic operating cycle. If, perchance,
the cam stops have been improperly set so that the machine is
programmed to oil for a greater distance than it is set to travel,
actuation of cam-actuated distance switch 162 will be effective to
terminate the oiling operation prematurely by deenergizing relay
224 through its normally open holding contacts 224(1). Again, as
these contacts reopen, a current path to oil reservoir retraction
solenoid 116 is instantly established via TB9, 226(0), 226(1),
normally closed contacts 224(3) and normally-closed contact
160(2).
Not infrequently, a condition exists where the lanes require
buffing and dusting but no dressing applied thereto. To completely
de-activate the oiler subassembly, one need only actuate the
triple-pole double-throw switch 226 into its alternate position
while leaving double-pole double-throw switch 228 as it was. This
by-passes cam-actuated switch 160 completely and energizes oil
reservoir retraction solenoid 116 directly via TB9, normally open
contact 226(2) of switch 226 which is now closed, contact 228(2) of
switch 228 and normally closed contact 160(2) of switch 160. The
circuit to the pilot light 230 is also open at this point.
The alternative condition is one in which oil is to be applied to
the alley in both directions of machine travel and over the full
distance of travel. Here both the triple-pole double-throw switch
226 and double-pole double-throw switch 228 are shifted out of
automatic mode into their alternate positions. Now, a current path
to pilot 230 is set up via TB9 through 226(3) and 228(3). Switch
228 is open at 228(2) and switch 160, even when on its normally
closed contact 160(7) will be ineffective to energize the oil
reservoir retraction solenoid 116 because contacts 226(1) are open.
Thus, as soon as start switch 216 closes to put current at terminal
board connector TB9, the oiler unit will start oiling and continue
to do so until the feeler 178 reopens switch 216.
Finally, with regard to switch 220, it is a special function
switch, the purpose of which is to precondition the buffer
preparatory to placing same in contact with the lane. When the
machine has been standing idle for some time, the oil left on the
surface of the buffer will have migrated to the bottom and
collected there. Accordingly, it is desirable to start the buffer
together with the oiling subassembly therefor in advance of placing
the unit on the lane being worked upon. To do so, the operator
actuates switch 220 and holds it actuated until the buffer is
thoroughly oiled. As the normally open contacts 220(2) close, the
coils of relays 222 and 224 will both be energized via TB5. Switch
216 will be closed to energize the buffer motor 118 via TB5,
216(1), and TB6. The coil of relay 224, upon energization, will
close the holding contacts 224(1). Since switch 218 only closes
momentarily and the coil of relay 224 is ordinarily kept energized
through contacts 220(1) which are now open, another current path to
holding contacts 224(1) must be established. With the coil of relay
224 directly energized as previously mentioned, jumper "B" from
this coil up to contacts 224(1) hold the latter closed even though
switch 218 is open. Thus, a current path is established to main
drive motor 70 via TB5, 220(2), the coil of relay 222, the coil of
relay 224, jumper B, contacts 224(1), contact 162(1) of switch 162,
222(1), 222(2) and 222(3) to the starting winding. This same
current path through 222(1) to the main winding of drive motor 70
through conductors "A" keeps it running when the starting winding
drops out. It is, of course, necessary to have the main drive motor
running to operate intermediate roller 90 which is driven
thereby.
Cam-controlled switch 160 will be on its contact 160(1) and
switches 226 and 228 will be actuated into the automatic mode
illustrated thus deenergizing solenoid 116 to leave the oiler
subassembly operative. A current path via TB9, 226(0), 226(1),
160(2), 224(2) and 228(1) to pilot lamp 230 will light same
indicating the operative condition of the oiling subassembly.
Lastly, the same current path through 222(1) to the windings of the
drive motor has a parallel branch to solenoid 198 that energizes
same and disengages the brake 212. Accordingly, as long as switch
220 is held actuated onto its normally open contacts 220(2), the
machine will be fully operative in its forward mode. Since the main
drive is operating, the cams controlling switches 160 and 162 will
also be turning while the preconditioning of the buffer takes
place. As a result, the distance pointers will have to be reset by
turning the arms associated therewith against their respective
stops at the entrance to the lane.
* * * * *