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Патент USA US2405626

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I Aug. 33, 1946.
Filed 001;. 24, 1942‘
5 Sheets-Sheet l
Laurence 5. VV/7/iams
Aug. 13, 1946.
Ls; wuLuAMs
Filed Oct. 24, 1942
5 Sheets-Sheet 2
l5 5/
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F257,- Z
Auggls, 1946.
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Filed‘ Oct. 24, 1942
' 5 Sheets-Sheet'{4_
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Aug. 13, 1946.
Filed Oct. 24, 1942
5 Sheets-Sheet‘ 5
Lawrence .S. MY/x'ams ‘
Patented Aug. 13, 1946
Lawrence S. Williams, Toledo, Ohio, assignor to
Toledo Scale Company, Toledo, Ohio, a corpora
tion of New Jersey
Application October 24, 1942, Serial No. 463,264
10 Claims.
(Cl. 235-436)
This invention relates to counting mechanisms
ments the speeds of operation of which vary
having drums or dials bearing ?gures in series of
decimal places, such as units, tens and hundreds,
Such counting mechanisms for the most part
may be classi?ed into two different types. One
of these is the direct gear driven type of counter
wherein one counting drum, for example, the
during their cycles of operations from extremely
high speeds to very slow speeds and in which in
dications must be positive and not liable to be
erroneously read because of intermediately posi
tioned indicators.
Weighing scales are one type of instrument
units drum, is geared to the tens drum by gearing
which fall within this class. In a weighing scale
having a reduction of ten to one and the tens
the ?rst and major part of the movement of the
drum is geared to the hundreds drum by similar l0 mechanism under in?uence of a load being
gearing, etc. Counters of this type have two dis
weighed is very rapid, requiring indicating or
advantages. If the number to be counted is, for
counting means capable of moving from Zero to
example 555, when the mechanism stops the hun
nearly load indicating position in a few seconds.
dreds indicator will be halfway between the “5”
In addition, it is important that the indicating
and “6” positions and the tens indicator will be 15 means be legible with the tens and hundreds
halfway between the “5” and “6” positions. A
?gures in de?nite indicating position whenever
familiar example of this type of counting mecha
he units drum is moving at slow speeds. Finally,
nism having movable pointer indicators geared
when the weighing mechanism comes to rest its
together is the ordinary electric meter in reading
indication must be positive. In retail scales par
which it is customary, whenever an indicator 20 ticularly it is required that the indicating mech
points to the space between two ?gures, always
anism be legible when in slow movement, so that
to read the larger ?gure, or always to read the
merchants can “pour on” material until a desired
smaller ?gure. This, of course, gives accurate
weight is reached.
results in the long run; but, if the wrong ?gure
These requirements would be even more im
were read by mistake, the particular reading 25 portant if the weighing scale incorporated calcu
would be inaccurate. A second serious disadvan
lating mechanism which multiplied the weight of
tage with the gear driven counter is the fact that
the load by a selected price per pound, because
at even moderate speeds of operation, since the
the multiplying ratio would cause the price indi
counting wheels are in constant motion, the ?g
eating or counting mechanism to operate at a
ures cannot be read at all.
30 speed still higher than the speed of operation of
A second type of counting mechanism is the so
the weight indicating mechanism.
called “transfer” type in which the units drum
The limitations of gear type and “carry-over”
only is rotated at constant speed, the tens and
type counting mechanisms have been one of the
hundreds drums being moved intermittently. For
major stumbling blocks that have hampered the
each revolution of the units drum in this type of 35 development of mechanical money value calcu
counter there is a “carry-over” of one increment
lating devices for incorporation in weighing scales.
to the tens drum, and similarly for each rotation
It is an object of this invention to provide a
of the tens drum a “carry-over” of one increment
counting mechanism Which will operate at high
to the hundreds drum. Thismtype of mechanism
speeds without tendency to self-destruction and
eliminates the di?iculty in reading the tens and 40 yet which will exhibit centrally positioned tens
hundreds drums since they are moved from posi
and hundreds ?gures when operating at slow
tion to position instantly at the time of “carry
speed or at the end of the “count.”
over.” However, at very high speed operation,
overs” are made.
It is an object of this invention to provide a
counting mechanism which will operate on the
principle of a direct gear driven counter when
Because of the low speeds at which “carry
over” type counters must be operated to prevent
operating at high speeds and will not, therefore,
be subjected to destructive in?uences.
“carry-over” type counters tend to destroy them
selves due to the rapidity with which the “carry
It is another object of this invention to provide
destructive wear, gear type counters have been
used for most tasks of counting where speed of 50 a counting mechanism for operation at high
operation is more important than ease and accu
speeds which, as it slows down near the end of
racy of reading. The operating limitations, in
the count, operates on a “carry-over” basis.
herent in both gear driven and “carry-over” type
It is still another object of this invention to
counters, have made it impracticable to use either
provide a high speed counting mechanism which
type of such counters in connection with instru 55 will incorporate the desirable features of both
direct, gear driven counter mechanisms and cam
driven “carry-over” mechanisms.
lower mechanism which “follows” a Weighing‘
scale indicator, or it may be driven by the output
shaft of calculating mechanism interposed be»
A further object of this invention is to provide
tween such follower mechanism and the counting
a high speed counting mechanism which will
exhibit figures visible from either side of the U! mechanism. Or, it may be driven by an output
shaft of sensing mechanism which operates to
device and will carry type for printing the
sense the position of the weighing scale mech
amounts counted.
anism after the scale has come to rest. Since fol
A still further object of this invention is to pro
lower, calculating and sensing mechanisms do not
vide a counting mechanism which will operate at
a sufficiently high speed to serve as the indicator 10 constitute a part of the instant invention, and
since their operation is well known in the art, they
of weight being weighed upon an automatic
are not described herein.
weighing scale and which, when approaching a
Theinput ‘shaftvlii is journaled in a bearing l l
balance point or when such point has been
riveted throughrla triangular frame member l2
reached, will centrally position the ?gures borne
which, with a similar frame l3, forms the main
by the counting dials for indicating and printing
frame of the device. The frame members 12 and
I3 are welded to a pair of hollow cross frame mem
More speci?c objects and advantages are ap
bers M which may be mounted for support upon
parent from the description, in which reference is
a pair of rods IS. The input shaft fl] is also
had to the accompanying drawings illustrating
in a bearing it similarly riveted through
preferred forms of counting mechanisms embody
a subsidiary frame member l ‘i, which is welded to
ing the invention.
the hollow frame ‘members M extending parallel
In the drawings:
to, and lying between, the frame members l2 and
Fig. I is a View in elevation, certain parts being
broken away, of a counting mechanism embodying
|A pinion i8 is pinned on the shaft It and is in
the invention.
mesh with a gear l9, which is riveted to the hub
Fig. II is a vertical sectional view, taken on the
of a pinion 29 ?xed en a shaft 2! by means of a
line II——II of Fig, I.
set screw 22. The shaft 2! is jcurnaled in two
Fig. III is a fragmentary sectional view, taken
bearings 23, one of, which is set in the apex of
on the line III-III of Fig. I.
the triangular frame members i2 and L5.
Fig. IV is a fragmentary view, taken substan
The shaft 2 l ‘is horizontal and parallel to the rods
tially from the position indicated by the line
if: on vwhich the counting mechanism is supported.
IV—IV of Fig. I.
A tens and units digits drum 255, the periphery
Fig. V is a plan view of the mechanism shown in
which, in the embodiment disclosed, carries in
Fig. I.
Fig. VI is a view, in elevation, showing that side 35 dicia for the tens and. units digits, has a single
web 25 constructed integrally with the periphery
of the mechanism opposite from the side shown
of the drum and riveted to a hub 21% which is fixed
in Fig. I.
to the shaft 2! by a set screw El’. The gearing
Fig. VII is a fragmentary view, taken from the
from the instrument follower mechanism to the
position indicated by the line VII-VII of Fig. II.
Fig. VIII is a fragmentary detailed view, taken 40 center shaft ‘2i through the shaft Ill, pinion l8
and gear I9 is such that the shaft ill makes one
from the line VIII-VIII of Fig. VII.
rotation for each count of 100 and the center
Fig. IX is a projection on the plane of the paper
shaft 2 f makes one rotation for each count of 590.
of the digits carried on the peripheries of the
full capacity of this embodiment of the inven- '
drums of the counting mechanism disclosed in
tion is 9995 by increments of 5.
Figs. I through VIII.
A pair of T shaped brackets 28 and 29 (Figs. I,
Fig. X is an end view, in elevation, of a counting
II, V and VI) is pivotally mounted on the shaft 2!
mechanism embodying a modi?cation of the in
which extends through holes near the lower end
of the Vertical stems of they T’s. The cross arms
Fig. XI is a fragmentary View, in elevation,
taken substant .liy fro-m the position indicated by 50 of the T's of the brackets 28 and 29 are connected
by a pair of parallel tubes 30 and 3! which are
the line XI-—XI of Fig. X.
at the ends thereof and are parallel to the
Fig. XII is an enlarged vertical sectional view,
tubular frame members‘ Hi and the center shaft
taken substantially 0n the line XII-XII of Fig.
RI. The two T shaped members 23 and 2t, and
Fig. XIII is a horizontal sectional view, taken _ the connecting tubes 35} and 3|, form a rocker
frame rockably mounted on the shaft 2 l.
substantially on the line XIII-XIII of Fig. XII.
The pinion 2E} is in mesh with both parts of a
Fig. XIV is a vertical sectional view, taken subtwo-part anti-backlash gear 32', which consists
stantially on the line XIV~XIV of Fig. XII.
of two identical gear parts one of which is riveted
Fig, XV is a fragmentary view, in elevation,
to a hub '33 journaled on a pin 34 supported by the
taken substantially from the position indicated by
T frame 28’, and a‘ Y bracket
depending from
the line XV—XV of Fig. XIV.
the tubes 3% and 3!. The other thin gear part of
Fig. XVI is a fragmentary sectional view, taken
the antiébackla'sh gear is freely rotatable on the
on the line XVI-XVI of Fig. XIV.
hub 33, ' and three’ interposed springs 36 exert
Fig. XVII is a fragmentary view, in elevation,
pressure to urge the teeth of the two identical gear
taken, from the position indicated by the line
parts 36 and Bi’ slightly offset and hence to'enter
the teeth of the pinion 2% without any backlash.‘
These speci?c drawings and the speci?c de
A pinion '39 is securedon: the hub 33 and is in
scription that follows merely disclose and illus
mesh with an idler gear at, which is journaled be
trate the invention and are not intended to im
70 tween‘the Y ‘bracket 35(and a similar bracket I'll
pose limitations upon the claims.
also secured to the tubes as and 3!; The idler
A power input shaft in (Figs. I and III) is
gear, 401s in mesh with a drive gear 62 which is
driven by the output of any device with which
secured upon a countershaft t3‘ journaled in the
the counting mechanismembodying the invention
T shaped brackets 28 and‘ 2e equidistantly between
is adapted to be employed. This shaft It may be
and parallel to the tubes 39' and 3 5. Also pinned
driven, for example, by the output shaft of a fol
5 .
upon the shaft 43 are two pinions 44 and 45. The
former may be undesirable for reasons of space
pinion 44 is in mesh with a large annular driven
and the latter for reasons of legibility. A counter
gear 46 which is adiustably fastened to the web
of convenient size will accommodate one hun
of a hundreds drum 47, the hub of which is jour
dred good sized legible ?gures on its drum. The
naled on the main shaft 2| and the periphery of
device illustrated is designed to have a maxi
which bears indicia for printing and indicating
mum capacity of 9,999 which can be achieved
the hundreds increments of value or weight. The
with only two rows of ?gures on the hundreds
diameter of the drum 4'! is equal to the diameter
drums, i. e., “0” to “99.” The ?gures borne
of the drum 24.
by the center or tens and units drum, depend
The pinion 45 is in mesh with a second an 10 upon the smallest increment which it is desired
nular driven gear 48 which is adjustably fastened
to count. This smallest increment may be one,
to the web of a second hundreds drum 49 lo
cated on the other side of the drum 24 from the
hundreds drum 4'! and equal in diameter to these
two drums.
The gear ratio between the center shaft 2| and
the top pinion shaft 43 is 2:1 and the ratio be
tween the pinions 44 and 45 and the annular
driven gears 43 and 48 respectively is 10:1, re
in which case the center drum would bear in
dicia in series such as “0, 1, 2, 3,” etc., to “99,”
it may be two, in which case the center drum
would bear indicia from “O, 2, 4, 6,” etc., to “98,”
or other increments may be used.
In this embodiment of the invention the count
ing mechanism is constructed to count from zero
to ten thousand in increments of ?ve. Fig. IX
sulting in a ratio of 20:1 between the center tens 20 is a projection on the plane of the paper of the
and units drum and the two outer hundreds
indicia borne by the drums showing the relations
drums 41 and 49. This ratio is established by the
of the various series. The tens and units drum
ratio between the smallest increments countable
24 carries a plurality of series of indicia each
on the two outer drums and the inner drum, in
reading “5,” “10,” “15,” etc., to “95.” The tens
this case, 100:5 or 20:1. If the drum ?xed upon
and units drum 24 has two sets of ?ve series each
the shaft 2| were marked with units digits and
of identical indicia. One of these sets is upright
the drum turned by the gearing were marked by
in Figs. IV and IX and consists of the ?rst two
tens digits, the gear wheels would be made of
columns of ?gures on the left side of the drum
such sizes as to turn the tens drum once for
24 which are designated by the reference nu
ten revolutions of the units drum.
merals 6|. The second set of live series of in
An actuating arm 59 (Figs. II and VII) is
dicia, designated by the reference number 62, is
mounted for rocking motion on a pin 5| which
inverted in Figs. IV and IX and is designed to be
is secured in a cross bar 52 extending from one
read from the opposite side of the counting
of the tubular frame members M to the other
’ mechanism. The drum 24 also carries ?ve series
between the edges of the drums 24 and 49. The
of type, indicated by the numeral 63, which are
lower end of the actuating arm 59 has two legs
through both of which the pin 5| passes. The
raised from the surfaces of the drum for print
ing the indication shown by the sets of visible
indicia 3| and 62. The two hundreds drums 41
upper end of the actuating arm 59 is bifurcated,
the two arms of the bifurcation both lying in the
and 49 each carry a series of hundreds indicia
plane of movement of the actuating arm which 40 from Zero to one hundred, the drum 49 hearing
plane passes between the drums 24 and 49 and is
a series of indicia 64 legible from the same side
at right angles to the main shaft 2|. The bi
of the mechanism as the indicia 6| on the drum
furcated upper end of the actuating arm ex
24, and the drum 4'! bearing a series of indicia
tends around the tube 39 of the rockable frame
65 associated with the indicia 62 on the drum 24
formed by the T brackets 28 and 29 and tubes
and a series of printing type 69 associated with
39 and 3|.
the type 63 on the drum 24.
A ?ve-step cam 53 (Figs, II and VII) is secured
If the mechanism were designed to count in
by means of cap screws to the hub 26 of the
increments of one, the center or tens and units
center drum 24 and located in the same plane
drum would bear two sets each consisting of a
as the upper end of the arm 59. The periphery
single series of indicia from “0” to “99” by one,
of the cam 53 is engaged by a roller 54 journaled
and one series of type corresponding thereto.
in a clip 55 (see also Fig. VIII) which is rock
If two were the smallest increment, the inner
able on a pin 56 extending between the lower
drum would hear two sets of indicia each con
legs of the actuating arm 50 and which clip is
sisting of two series from “0” to “98” by two.
urged to swing the roller 54 toward the edge of
. When employed with calculating mechanism,
the cam 53 by a spring 5'! engaged between the
the indicia carried by the drums would be ar
clip 55 and a second pin 58 extending through
ranged to read in monetary values.
the legs of the actuating arm 59, the second pin
When the input shaft I9 is rotated, (in a
58 also serving as a stop to limit the movement
clockwise direction in Fig. I for example) the
of the clip under the in?uence of the spring,
center shaft 2| to which it is "geared turns and
The entire rockable frame, made up of the
the tens and units drum 24 are turned in a
T shaped frame members 28 and 29 and the tubes
counterclockwise direction, or in the direction of
39 and 3|, is urged to the left in Fig. VI, ‘by a
the arrows shown on such drum in Figs. IV and
spring 59, one end of which is engaged with the
T shaped bracket 29 and the other end of which 65 V.
As the input shaft rotates it drives the center
is hooked to an arm 60 adjustably mounted on
shaft 2| and drum 24, as described, and, through
the triangular end frame l3. The tension of the
the pinion 20, the split gear 32, the pinion 39,
spring 59 holds the roller 54 in engagement with
the idler gear 49 and the drive gear 42, the
the periphery of the cam 53 by means of the con
driven shaft 43 and driving pinions 44 and 45.
nection between the frame and the yoked end of
the actuating arm 50.
The pinions 44 and 45 rotate in a clockwise direc
Although the quantity of individual numbers
tion (Fig. I) and drive the two annular driven
which can be printed around the periphery of
gears 46 and 48, and the two hundreds drums
the counting drums can be increased by making
41 and 49 respectively, in the same direction as
the drums larger, or the ?gures smaller, the 75 the drum 24 is rotated.
The rotation of the drum 24 also rotates the
frame to the right and, since this movement is
cam 53 which isbolted to it (in the direction of
the arrow shown in Fig. VII) and when the mech
anism is operating at low speed the roller 54 is
engaged with the periphery of the cam. The ten
much faster than the rotation of the gear 46
which results from rotation of the drive pinion
M, the gear 46 is moved in a clockwise direction
the distance between successive ones of the in
dicia borne by the drum t1. Thus, when the de
vice is operating slowly the drum 24 moves stead
ily and the hundreds drum Ill and 49 are moved
sion created by the spring 59 pulls the actuating
arm and rockable frame to the left with the roller
54 following the declining face of the cam. In
Fig. VII the roller 55 is shown engaged with a
gently sloping surface ti’? on the periphery of the
action of the cam and actuating arm.
cam 53‘. The length of this section 61 on the
periphery of the cam bears a ratio to the length‘
it needs must when the instrument to which it is
of an adjoining steep section 68 equal to the ratio
between the increments measurable on. the hun
rapidly, the increased speed of rotation of the
dreds drums 69 and iii : and the increments
measurable on the tens and units drum 24 less
cam 53 is so high that there is insu?icient time‘
for the spring 59 to overcome the inertia of the
one (that is, in the embodiment shown, twenty
T shaped frame members and the parts movable ~
therewith and act through the actuating arm 50 '
of the increments measurable by the drum 24 are
required to equal one of the increments measur
able on the hundreds drums 1W and (i9 and the
ratio of length between the surfaces iii and 68 is
19:1). During 19420 of the one-?fth rotation of
the cam 53‘, represented by the distance from the
intermittently from position to position by the
When the device is operating at high speed as
attached, for instance a weighing scale, is moving
to swing the T shaped frame members and con
nected parts to the left as each of the surfaces -
5's’ of the cam 53 passes the roller. During such
high speed operation the actuating bar and the
rockable frame move to the limit of their travel
to the right and are held in that position by the
another, the arm 5t gradually swings to the left 25 repeated passage of the high points of the cam
in Fig. VII. Since the driven pinion lid is rotating 7 against the roller 55;. To assist in holding the
actuating arm Eli to the right and to prevent the
in a counterclockwise direction in Fig. VII, and
arm from movingto the left fast enough so that
turning the annular driven gear £56 in a clockwise
the roller 5!; will follow or partially follow the
direction, by moving the pinion E4 bodily to the
surface of the cam 53 and be subjected to de
left, it is “backed up” on the driven gear 5:6 as it '
structive blows from the surfaces E38 thereof, an
tends to move the gear forward. The gradual
air dashpot 59 is connected between the frame
fall in the surface 6? of the cam 53 is such that
start of one of the surfaces 65? to the start of
of the counting mechanism and the T shaped
the movement of the pinion 44 to the left exactly
member 29 of the rockable frame. The air dash
compensates for the rotation of the driven gear
46 to the right which would otherwise result from 35 pot 89 comprises a plunger 70, secured on a rod
it which is pivotally attached to the T shaped
the rotation of the pinion lid and, therefore, the
member 29, and a thimble ‘E2 in which the plunger
gear 46 and the drum £11, to which it is attached,
To is located, which is secured to a bracket 73
remain stationary during this ?rst 19/20 of the dis
bolted to the end frame member 13 of the
tance through which the cam 53 moves to repre
sent one increment on the hundreds drums ill
counting mechanism. The air dashpot 69 acts as '
and 4%.
There are five sets of surfaces El and 68 on the
cam 53, one for each individual series of the sets,
of indicia iii and 62 from “0” to “95.” The tens
and units drum, having ?ve series of indicia each
a damper on the rocking motion of the rockable
frame and does not permit it to move to the left
between the steep sections of the cam.
To further ease the effect of the repeated pas
of which represents the difference between two’
as described, is resiliently mounted in the actuat
ing arm 5d and being light in weight can yield
quickly with the passage of each high point of
the cam without causing the actuating arm and
50 rockable frame to oscillate. The rockable frame
successive indicia on the hundreds drums, turns
through one-fifth of one revolution for each ad
vance of the hundreds drums.
The number of steps, comprising the two sur
faces iil and £58, in the cam varies in accordance
with the ratio between the smallest increment
on the inner drum and the smallest increment
(one hundred) on the outer drums. If, as men
tioned above, the center drum carries indicia
from “0” to “99” by one, the cam 53 would have
only one step and the surface El would extend
through 9?5/100 of the circumference of the cam, the
surface 68 ertending through the remaining 1/100.
In addition to the changes in the indicia borne
by the inner drum and the steps on the cam, the
gearing between the inner and outer drum would
have an overall ratio of 100:1 rather than 10:1.
This would also apply to a monetary counter.
For increments of two, the cam Iéiswould have
two steps, each extending through one-half of the
cam circumference and comprising a surface 8'1
49/100 long and a surface 63 V100 long; or W50 and
1A0 of the step only. In the former case a complete
revolution of the inner drum would take place
before the outer drums changed and in-the latter
one-half a revolution.
When the roller 54 hits the steep section E8~of
the cam 53, the actuating arm ?élis snapped to
the right (Fig. VII) which pulls the rockable
sage of the high points of the cam 53, the roller, _
thus remains at one side of its range of move
ment while the counting mechanism operates as
a direct gear driven mechanism with all of the
drums moving continuously.
As the device to which the counter is attached
approaches the end of its count (as for example
when-a weighing scale approaches balance under
a load thereon), its operation slows down and
the counting device is moved slowly enough so
that the oscillation of the rockable frame takes
place at a slow enough speed not to be clamped
by the air dashpot E9 and the hundreds wheels
are moved from position to position as above de
When - the instrument to which the
counter is attached returns toward zero (for ex
ample when a load is removed from a Weighing
scale) the shaft i0 is rotated in a reverse direc
tion which rotates the various portions of the
counting mechanism in the direction opposite to
that described above. However, when operating
at high speed or low speed, or in one direction or'
the other, the counting mechanism operates .in
the same manner, i. e., while returning toward
zero at high speed it operates as a direct drive
:: counting mechanism and at slow speed it oper—
ates as a cam type carry-over mechanism.
Two viewing screen brackets ‘I4 and 15 (Fig.
nut I05. The gear I03 has an elongated hub I 08
IV) are bolted to the end frame member I3 and
on which is mounted a units drum I01. The gear
carry two viewing screens ‘I6 and ‘II which ex
I03 and drum I 01 are spaced from the plate ‘I3
tend across above the surface of the counting
by a bushing I08.
drums. In each of the viewing screens 76 or 11
The gear ratio between the pinion 89 and
there are four apertures ‘I8 which are located
gear 9| (in the embodiment disclosed) is 1:21/2.
above the series of indicia on the drums which
The ratio between the gears 92 and 95 is 1:2.
are legible from that side of the device on which
Thus the ratio between the input shaft 84 and
the screen is located.
the units drum I0'I is 5:1 50 that each rotation
In Fig. IX the viewing apertures in the screens 1 I of the input shaft 84 rotates the units drum I0‘I
‘I8 and ‘II are shown in dotted lines and desig
a distance equal to two unit increments of value.
nated by the words “Front” and “Back” respec
A gear I09 is also in mesh with the pinion 96
tively. The counting mechanism has been de
and is pinned on a jackshaft IIO which is rotat~
signed so that the series of type 68 and 83, borne
ably journaled parallel to the shaft 9'! in the
by the drums 2'! and 44 respectively, can be
two arms of a U shaped frame III rockably
printed on impression-receiving media located
mounted at the ends of its arms on the shaft 97.
beneath the counting mechanism. The impres
A pinion II2 is also pinned on the shaft II 0,
sion-taking mechanism, since it does not consti
being meshed with a tens drive gear I I3 secured
tute part of the instant invention, is not herein
to a pinion II4, both of which are journaled on
disclosed. The position at which the type to be
the shaft 91.
printed are located when printing takes place
A tens idler gear “5 is mounted on a spacing
is shown in Fig. IX and indicated by the word
bushing II6 journaled on the shaft IGI and is in
mesh with a pinion II'I, journaled on the shaft
The embodiment of the invention which is dis
I04, on which is secured a tens drum H8. The
closed in Figs. K through XVII operates accord
ratio between the pinion 96 and gear I09 is
ing to the same principles as the embodiment
1:5, and the ratio between the pinion H2 and
already described but is provided with four sepa
tens drive gear II3 is 1:2. Thus the total ratio
rate digit bearing drums, one each for units, tens,
between the pinions 9B and H4 is 1:10, and the
hundreds and thousands.
ratio between the units drum I01 and tens drum
The main frame of the counting mechanism Iii) I I8 is 1:10.
comprises two end plates 18 and 19 which are
A gear II9, substantially identical to the gear
assembled by means of. two parallel tubes 80 and
I09, is pinned on a hundreds jackshaft I20 which
two parallel rods 8|. The tubes 80 are each
is rotatably journaled in the arms of a U shaped
located at one of the lower corners of the plates
frame I2I substantially identical with the frame
‘I8 and ‘I9 and are welded thereto. A pair of
III but extending from the shaft 91, on which it
rods 82 may be inserted through the tubes 80
is rockably mounted, in a direction opposite to the
for mounting the counting mechanism. The rods
direction in which the frame I I I extends. A pin
ion I22 is also pinned on the jackshaft I29, being
8| are each located in one of the upper corners
of the plates ‘I8 and ‘I9 and are secured to these
in mesh with a hundreds drive gear I23 rotatably
plates by means of oval-headed machine screws 40 journaled with a pinion I24 on the main shaft 97.
83 which extend through holes in the plates ‘I8
An idler gear I25 is rotatably journaled by a
and ‘I9, and are threaded into the ends of the
spacing bushing I23 on the shaft IiiI and meshed
rods 8 I.
with a pinion I2‘! which rotatably mounts a hun
An input shaft 84 is journaled in a pair of
dreds drum I28 on the shaft I04. The gear ratio
bearings 85 which are staked in holes bored in I between the pinions I I4 and I24, and thus be
the plate ‘I8 and in a triangularly-shaped plate
tween the drums H8 and I28 is 1:10 in accord
88, which, with two similar plates 81 and 88, is
ance with the ratio between the tens values and
welded to the tubes 80 parallel to and between
hundreds values.
the plates 18 and ‘I9. A pinion 89 is secured on
A gear I29, also in mesh with the pinion I24, is
the shaft 84 between the plates 18 and 86, its
pinned on a thousands jackshaft I 30 which, simi
elongated hub 90 serving as a bushing to prevent
larly to the jackshafts III! and I29, is journaled
axial movement of the shaft 84. The pinion 89
in the two arms of a rockable U shaped frame |3|
is in mesh with a gear 9| which is one of a pair
which extends in the same direction from the
of integral gears 9| and 92 rotatably journaled
shaft 91, on which it is mounted, as the frame
on a shouldered stud 93 extending through the '
I I I. A pinion I32 is also pinned on the jackshaft
plate ‘I3 and held thereon by a nut 94. The
I38 and is in mesh with a thousands drive gear
smaller gear 92 of the integral pair of gears is
/ I33 which, with its associated pinion I34, is jour- ‘
meshed with a gear 95 which is assembled to a
naled on the shaft 91 between the arms of the
pinion 96 journaled on a shaft 91. The shaft
frame I3I. A thousands idler gear I35 is in mesh
91 is mounted in the apices of the triangular
plates 86, 81 and 88 extending parallelly to the
tubes 80 and rods 8| through the plates ‘I9 and
‘I8, being held in place by a nut 98 secured on
its end. The pinion 96 is in turn in mesh with
an idler gear 99 which is rotatably journaled by
means of a shouldered bushing I00 on a second
shaft |0I extending parallel to, and above, the
shaft 91 between the plates ‘I9 and ‘I8, being
stationarily secured to the plate ‘I8 by means of
a nut I02. The idler gear 99 is in turn meshed
with a small driven gear I03 of the same num
ber of teeth as the pinion 96 and journaled on a
third shaft I04 which is mounted at the top
center of the plates ‘I8 and ‘I9 parallel to the
shaft 91 and I0| and held against rotation by a
with the pinion I 34 and is rotatably journaled by
a bushing I33 on the shaft IOI. The gear I35
drives a pinion I31 by which a thousands drum
I38 is rotatably journaled on the uppermost shaft
I04. The gear ratio between the drums I23 and
I38, and their respective pinions I24 and I34, is
1:10 corresponding to the ratio between hundreds
and thousands.
The pinions 98, I14 and I24, in addition to
mounting the gears 95, II3 and I23 respectively,
also mount three cams I39, I40 and MI (see also
Fig. XIV). The periphery of each of the cams
I39, I40 and MI has a long slowly rising surface
I42 which extends through nine-tenths of thecir
cumferential distance around the cam, and. a
short abrupt surface I43 which extends through
the remaining one-tenth of» the distance. The
peripheries of the camsISB,vv MI) and-IIII are each
engageable by a; ball bearing roller-1M lournaled
been stored by the “backing up” of the'pinion I I2
' during the ?rst nine-tenths of a rotationof‘the
cam I39. This, in turn, sharply‘ rotates the gear
ing connecting the gear II3 to the tens drum I I 8
which advances a distance corresponding ‘to a
in one of three bifurcated rocker arms M5, M6
and I4’! respectively. The rocker arms I45, M5
count of one digit thereon or a value of ten.
and» I4‘! are each mounted on one of three studs
, I48 (Fig. XVI) which are riveted to the triangular
' Because each rotation of the cam I39 causes an
oscillation not only of the light arm I45 butalso
of the heavier frame III and the gears mounted
plates 8B, 87 and 88 respectively.
Through the outermost end-of the rocker arm
I45 there is threaded a shouldered pin I139, the M) therein, when the counting mechanism is operat~
ing at high speed there is insufficient time during
two shoulders of' which extend through the two
each rotation of the cam I39 for this oscillation
longer arms of a double L ‘shaped connection
. member I56 .(Fig. XV). The upper end of the
to be completed and provision must be made to
prevent the mechanism from destroying itself.
It is for this reason that the apertures I53,v in
which the pin M9 is engaged, are elongated.
This permits thearm I45 to oscillate with respect
to the frame I I I. When the arm'I 45 is oscillating
connection member I5Il is similarly connected by
‘means of a shouldered vpin I5I to an ear I52,
formed, in, and extending rearwardly from, the
cross arm of the rockable frame Hi. The aper
tures in the connection member I50, through
- which the pin-I49 extends, are in the‘form of ver
tically elongated slots I53 (Fig. XVII).
H A small coi1 spring I54 is engaged between the
at high speed, the frame “I is "held, stationary
I so that the spring I54 will ‘not cause it to'move
1 along with the arm I65 by email‘ dashpotiltt
bolted to the rod iii, the plunger of which, is con
nected to the connection member I5II. The op
eration at high speed is as follows: rI‘he arm M5
is thrust downward rapidly, which originally pulls
‘one of the short'arms'of the connection -memw ~
the frame III, connection member I55] and
be!‘ I59 (Fig'XV) and a ?attened pierced ear I55
plunger of the dashpot I58 downwardly. The
on a'stud I51 extending through one of the rods
arm M5 moves upwardly a short distance as its
SI. The‘spring 1'55 urges the rocker arm 145 up
roller I654‘) takes off from the high end of the sur
wardly, tending to hold its roller I44 in contact
M2 and almost at once returns to the limit
with the periphery of the cam I39. 'Thus, the
ends of the pins'I49 and I5I,'thus tending tohold
the pin‘ I49 at the-top of the slots I53. A weaker
coil spring I55 is engaged between the outermost
of its downward movement because the cam I42
spring I54 normally vkeeps the pin ‘I49 at the top
is rotating too fast to permitthe roller I44 to
follow the surface M3. The inertia of the rock
able frame III, plus the damping action of the
dashpot I58, sumces to hold these members sub
stantially motionless and the rocker arm I45
vibrates rapidly in the slotsI 53 without changing
the position of the remaining members. The arm
is so light in weight that it can thus vibrate with
out injury. Therefore at high speed, the mecha
nism ‘connecting the units drum I I8 is not
aiiected by the cam‘ use and there is a direct 1:10
gear ratio between the two drums.
The rockable arms Hit and I4‘! operate in con
junction with their cams I40 and MI and with
of the slots I53, holding ‘the 'arm M5 and rock
able frame III operatively together so that the
movement‘ of the rockable- arm Hi5, caused by its
roller runningon'the periphery of the cam I39,
is participated in byithe rockable frame II I.
The counting vmechanism is connected to the
device with’ which‘ it is employed so that when the
device is accumulating value, i. e., when the value
being‘measured thereby is increasing the input shaft- 84 is rotated in a counterclockwise direc
tion (Fig. XIV). This movement, through the in
termediate gears 9| and" 92, rotates the gear‘ 95,
pinion» 9B and cam "I39 in a counterclockwise di
rection. The idler gear 98 transmits the counter- >
clockwise rotation‘ of the pinion‘ 96 to the pinion
- connection members I59 and I50, the "dashpots
IE2 respectively,’ in a mannersidentical
to the above described operation of the arm M5
and its associated parts.
At high speed, the arm I45 is certain to move
downwardly and remain there and the arm, I45
isquite certain to do so, but it'may be that the
speed is not high enough to rotate the thousands
cam MI with su?icient rapidity ‘to move the
IIl3~and units drum IB'I which also rotate in a
counterclockwise direction. Thevgear ‘Hi9 and
pinion I.I2 are‘ rotated in a clockwise direction
' which rotates'the gear H3 in a counterclockwise
As ‘the cam I39 rotates in a counter
clockwise-direction, the gradually rising surface
I I42 slowly. moves'the rocker ‘arm I45 downwardly,
pulling idownwardly, through the spring Iiill,
rocker arm HM downwardly. - In that event, the
'. against the bias of the spring ‘I55 and pulling ‘the
units, tens-and hundreds wheels will operate as
direct ‘gear driven counter wheels and the
thousands wheel will be cam driven. In any
rockable frame III downwardly. Since the pin
ion I I2 is rotating in a clockwise direction, mov
ingv it: downwardly bodily revolves it around the
event, variations in speed of operation will be
gear H3 and “backs it up” on the gear which it
is'driving. Therefore ‘there is no net movement -‘
automatically compensated for by the separate
rcckable carry-over mechanisms and their high
speed disengaging means to preventthe counting
mechanism from destroying itself.
The four counting drums III'I, Ht; I28 and I38
are located parallel and adjacent at the upper
of the gear I I 3, the rotation of the pinion I I2 be
ing compensated for by its bodily movement and
during the count of the ?rst nine digits, the gear
- II3 not being rotatecL'the tens drum I I8, which it
ultimately‘ drives, ‘remains stationary.
However, when‘ the ‘cam I39 has turned through
nine-tenths of a rotation, and the arm I ‘135 and
frame III have been moved downwardly (to the
position'occupied by the arm M5 and frame IZI
in Fig; XIV), the spring ‘I iiii'has been greatly ex
tended and, as the roller Isis-moves over the sur
.face 143 of'the cam I39, the spring I55 snaps the
yarm'ifl? and frame III sharply upward. This
bodily moves the pinion I I2 forward on the Eta]?
H3, applying thereto the movement which had
‘ portion of the machine and their peripheries may
be viewed through a screen I63 (Figs'XI and
XIV) in which arelocated'view-ing openings I54,
one over each‘ counting drum.
' I)
Counting mechanisms having higher capacities
may easily be constructed by adding additional
groups of digit mechanisms each comprising a
rockable frame, the two gears journaled thereby,
a rocker arm, an (for example, tens of thousands)
‘- increased capacity drum and cam and the asso
ciated gears and parts. This mechanism-would
be incorporated in the counting device in position
to be driven from the last pinion I34 in the illus
movement around said driven gear while in mesh
therewith, a cam driven synchronously with said
divisional - indicia - bearing
trated gear train.
means for driving said rockable frame from said
Operation in reverse is substantially as de in cam and for limiting the force transmitted from
scribed with repect to the embodiment disclosed
said cam to said frame, said cam having a long
in Figs. I through IX, except for differences in
sloping surface and a short oppositely directed
parts, the two modi?cations of apparatus em
sloping surface corresponding to each of the se
bodying the invention having identical principles
ries of divisional indicia borne by said divisional
of operation.
if) indicia-bearing member, said cam causing said
Because the counting mechanisms herein de
frame to rock and slowly move said pinion about
scribed operate at high speed as direct driven
said driven gear in a direction opposite to the
mechanisms and at low speed as cam type carry
over mechanisms, they have the advantages of
both types of counting mechanisms and the dis
advantages of neither. They can be operated at
extremely high speeds without destroying them
selves, at which speeds it is impossible to read the
indicia borne by the counting drums even if they
were being moved from position to position. At
low speeds, when it is desirable that such indicia
be visible, the counters operate as cam type carry
over mechanisms and the hundreds indicia, in the
embodiment of Figs. I to IX, or thousands, hun
dreds and tens indicia, in the embodiment of Figs.
X to XVII, are moved from position to position for
accurate reading. A counter of this type is par
ticularly advantageous when attached to a weigh
ing scale because it permits the rapid operation
necessary to allow the scale to come to rest with :21)
in a few seconds after a load is applied thereto
direction of rotation of said driven gear when
said resilient driving means for said frame en
gages said long sloping surface on said cam and
to sharply move said pinion and rotate said
driven gear when said frame engages said short
oppositely directed surface on said cam, and
means for limiting the velocity of said rockable
frame during high speed operation of said count
ing device.
3. A counting device comprising, in combina
tion, a major—indicia-bearing member, a divi
sional-indicia-bearing member, said divisional
indicia-bearing member hearing at least one se
ries of divisional indicia equal in total to the
difference between successive ones of the indicia
borne by said maior-indicia-bearing member, a
gear train operatively connecting said members,
said gear train including a pinion meshing with
a driven gear for operating said major-indicia
bearing member, a cam driven in synchronism
and yet gives positive indication when the scale
has come to rest. Similarly, it is possible to “pour
on” material being weighed and, as the desired
with said divisional-indicia-bearing member, said
weight is approached, to pour material on the
scale more slowly and thus get a positive ac
oppositely directed sloping surface adjacent
curate indication of the Weight, or, if money value
calculating mechanism is employed, of the selling
cam having a long sloping surface and a short
thereto for each of the series of divisional indicia
borne by said divisional-indicia-bearing member,
a rockable frame, said pinion being rotatably
,iournaled in said frame for bodily movement
The embodiments of the invention that have lg around said driven gear while remaining in mesh
been disclosed may be modi?ed to meet various
therewith, a roller resiliently mounted in said
rockable frame and engaging said cam, the rela
Having described the invention, I claim:
tive lengths of adjacent long and short surfaces
1. In a counting device, in combination, a ma
jor-indicia-bearing member, a divisional-indicia
bearing member bearing at least one series of
divisional indicia, a gear train operatively con
necting said members, said gear train including
a drive pinion meshed with a driven. gear, a rock
able frame for mounting said pinion for move
ment around said driven gear while in mesh
therewith and a cam driven synchronously with
said divisional-indicia-bearing member, resilient
means for driving said rockable frame from said
cam and limiting the force transmitted from said
cam to said frame, said cam having a long slop
ing surface and a short oppositely directed slop
ing surface corresponding to each of the series of
on said cam being equal in ratio to the relative
value of all of a series of divisional indicia from
first to the penultimate indicia and the value
of such indicia between the penultimate and ul
tirnate indicia of such series, rocking of said
frame under influence of the sloping surface of
said cam bodily moving said pinion in a direction
opposite to the direction of movement of said
driven gear by said pinion if not translated and
under influence of the short surface of said cam
bodily moving said pinion in the same direction
as such movement of said driven gear.
4. In a counting mechanism, in combination,
a maior-indieia-bearing member, a divisional
indicia-hearing member, said divisional-indicia
divisional indicia borne by said divisional-indi
cia-bearing member, said cam causing said frame
to rock and slowly move said pinion about said
bearing member bearing at least one series of
divisional indicia equal in total value to the dif
ference between successive ones of the indicia
driven gear in a direction opposite to the direc
tion of rotation of said driven gear when said re
silient driving means for said frame engages said
borne by said major-indicia-bearing member,
long sloping surface on said cam and to sharply
move said pinion and rotate said driven gear when
said frame engages said short oppositely directed
surface on said cam.
2. In a counting device, in combination, a ma
jor-indicia-bearing member, a divisional-indicia
bearing member bearing at least one series of
divisional indicia, a gear train operatively con
meeting said members, said gear train including
a drive pinion meshed with a driven gear, a
rockable frame for mounting said pinion for
said series of divisional indicia comprising divi
sional increments of value, a gear train opera
tively connecting said maior-indicia-bearing
member and said divisional—indicia-bearing mem
her, said gear train including a driven gear asso
ciated with said major-indicia-bearing member
and a pinion for driving said gear, a rockable
frame, said pinion being journaled in said frame
for bodily movement around said driven gear
while remaining in mesh therewith, a cam driven
in synchronism with said divisional-indicia-bear
ing member and having a pair of‘opp'ositely- di
rected operating surfaces corresponding to each
*movem’ent of vsaid frame in one direction under
influence of said cam rolls said pinion around said
' gear connected to each of said major-increment
f'serlesl of i indiciav borne by’ said divisional-indicia
“bearing member; said rockable frame‘ being in
resilient engagement with said cam, whereby
indicia-bearing wheels and pinions meshed with
each of said gears, a rockable frame for rotatably
journalling said pinions and for “backing up”
said pinions around said gears in a direction
opposite to the direction of rotation of said gears
when rocked, a cam driven in synchronism with
said minor-increment-indicia-bearing wheel, a
sulting from rotation of said pinion during ac
lever attached to said rockable frame and hav
cumulation of value corresponding to the value
‘of a ‘series of indicia borne by said divisional 10 ing a resilient portion engaged with the surface
of said cam, said cam having a set of oppositely
indicia-bearing member less one increment there
directed sloping surfaces for each series of in
of and movement of said frame in the opposite
dicia borne by said minor-incre1nent»indicia
direction rolls said pinion around said driven gear
bearing wheel for slowly swinging said lever and
in the direction of movement of said driven gear
during accumulation of value equal to the last 15 said rockable frame to “back up” said pinions
‘ driven gear in a direction opposite to and a speed
~ equal to'the movement of said driven gear re
' vincrement of such series of indicia borne by said
idivisional-indicia-bearing‘ member, and means
1 for restraining said rockable frame from follow
- ing‘ said‘ cam‘ during 'high speed operation of said
‘counting mechanism.
5. In a counting device, in combination, a ro
' on‘ said gears during vthe counting of value rep
resented by the major part of a series of indicia
‘borne by said minor-increment-indicia-bearing
w eel and for-‘sharply swinging said lever and
vsaid frame to move said pinions forward around
20 said gears when'the value counted reac es the
total of a series of indioia borne by said minor
tatable major-indicia-bea'ring member, a rotat
‘increment-indicia—bearing wheel, and means for
able divisionaleindicia-bearing memben said
preventing said lever from following said cam
members being mounted adjacent and coaxial,
a gear‘train connecting ‘said members, said gear 25 during high speed operation of said device.
'7.‘ In a counting mechanism having high- and
train including a driven gear connected to said'
low-order indicia~bearing members, in combina
‘majordndicia-bearing member and mounted con
tion, a transfer mechanism for indexing said high
centrically therewith’and a driving pinion, in
order indicia-bearing' member in accordance with
~mesh With saiddriven gear, a rockable frame
~ mounted coaXia'lly with said members for jour 30 av count accumulated on the low-order indicia
bearing member, said transfer mechanism com
- nailing said pinion and when rocked for rolling
prising a gear train, an oscillatable frame carry
said pinion around‘ said gear while in mesh there
ing said gear train a'nd'a cam rotating with said
- with, a cam driven ‘in 'synchronism with said divi~
low-order indicia-bearing member for oscillating
sional-indiciaebearing member, the'indicia borne
said frame, said cam having a sloping portion ex
by said divisional-indicia-bearing member com
tending part way which oscillates said frame‘ to
prising at“ least one'series equal in value to the
cancel the motion transmitted through said gear
difference between successive ones of the indicia
train, and another sloping portion which oscil
borne by said major-indicia-bearing member, a
lates said frame to add to the motion transmitted
roller resiliently mounted on said frame and en
gaged with 'said cam, said cam having one set 40 through said gear train, the slope of said por
tions allowing said cam to operate in either direc—
‘of oppositely directed ‘sloping surfaces for each of
such series of‘ indicia borne by said divisional
8. In a counting mechanism having high- and
indicia-bearing member, such sloping surfaces
low-order indicia-bearing members, in combina
serving to rock said frame and thereby roll said
tion, a transfer mechanism for indexing said high
pinion ~around said gear and means for restrain
order indicia-bearing member in accordance with
ing movement of said frame such that said frame
a count accumulated on the low-order‘ indicia
remains nearone end‘ of its path of rocking move
bearing member, said transfer mechanism com
ment with said roller‘momentarily contacting
prising a gear train connecting said members, a
said cam during high speed operation of said
50 frame carrying a portion‘ of said gear train, means
counting device.
for oscillating said frame to supplement uniform
6. In a counting device, in combination, a
motion through said gears and thereby produce
-minor-increment-indiciaébearing wheel hearing
intermittent motion of'said'high-order member,
at least one series of indicia legible from one side
said means comprising a cam having oppositely
of said wheel and bearing a corresponding series
directed sloping surfaces rotating with said low
of minor-increment-indicia legible from the op
order member, a'cam follower resiliently mounted
posite side of said-device, av major-increment
‘indi'cia-bearing 'wheel coaxially' journaled with
said minor-increment-indicia-bearing wheel and
bearing a~series of indicia representing incre
‘ments of value each equal to the total value of
a series of indicia borne by said minor-increment
~ indicia-bearing wheel legible from one side of said
vclevice‘in association with one of the series of
indicia borne by saidminor-increment-indicia
bearing wheel, a second coaxially journaled
major-increment-indicia-bearing wheel bearing
indicia corresponding to the indicia borne by the
?rst mentioned major-increment-indicia-bearing
wheel and legible from the opposite side of said
on said frame and riding on said cam and other
resilient means urging said frame in such direc
' tion as to cause said follower to engage said cam.
9. In a counting device employing ind'ci- -bear
ing counting wheels and transfer mechanism for
advancing a high order wheel according to a count
accumulated on a lower order wheel, in combina
tion, a gear train operatively connecting adjacent
counting wheels, a frame mounted for rocking
oscillation about the axis of the counting wheels,
the frame journaling part of the gear train and
adapted to oscillate the journaled part of the gear
train to produce intermittent movement of the
- device in association with the other series of in
high'order counting wheel, a cam rotating in syn
dicia borne by said minor-increment-indicia
bearing wheel, a gear train driven by said minor
chronism with the lower order counting wheel,
the cam having oppositely directed sloping sur
faces adapted ‘to produce to-and-fro motion of
the frame, a follower for the cam, and a preloaded
increment~indicia-bearing wheel and driving both
said major-increment-indicia-bearing wheels in
synchronism, said gear train including a driven
spring mounted between. and engaging the fol
lower and the frame for transmitting force from
the follower to the frame, the spring having suffi
cient resiliency to permit the frame to remain
substantially at rest during high speed operation
means for urging the frame in such direction
of the device.
10. In a counting mechanism having high and
low-order indicia-bearing members, a transfer
frame, the cam being provided with follower
engaging surfaces which have opposite slopes
relative to the direction of movement of the fol
lower, one surface being sloped so that the tend
mechanism for indexing the high-order member
as to cause the follower to engage the cam, with
a force insufficient to de?ect the preloaded re
silient connection between the follower and the
ency of the cam to cause movement of the high
in accordance with a count accumulated on the
low-order member, the transfer mechanism com 10 order member cancels the tendency of the gear
train to cause movement of the high-order mem
prising, in combination, a gear train connecting
ber, and the other surface being sloped so that
the members for driving the high-order member
the tendency of the cam to cause movement of
from the low-order member, a frame which sup
the high-order member adds to the tendency of
ports part of the gear train and which is rock
ably mounted so that oscillations of the frame 15 the gear train to cause movement of the high
order member thereby moving the high-order
tend to produce corresponding oscillations of the
member at substantially the same rate as the
high-order member, a cam operating synchro
low-order member.
nously with the low-order member, a follower
which has a preloaded resilient connection with
the frame and is movable with the frame, and 20
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