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Патент USA US2111127

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March 15, 1938.
'
I
F. Q. RAST
WEIGHING
AND
INDICATING
2,111,127
MECHANISM
Filed May- 7, 1935
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ATTORN EY
March .15, 1938.
2,111 ,127
F. Q. RAST
WEIGHING AND INDICATING MECHANISM
Filed May 7, 1935
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INVENTO
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BY
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‘
ATTORNEY
March 15, 1938.
E Q‘ RAST
2,111,127
WEIGHING AND INDICATING MECHANISM
Filed May 7, 1935
4 Sheets—Sheet 5
ATTORNEY
March 15, 1938.
'
E Q. RAST
2,111,127
WEIGHINGIAND INDICATI‘NG MECHANISM
Filed May ‘7, 1935
F IG.4.
4 Sheets-Sheet 4
43
ATTORNEY
7 2,111,121
Patented Mar. 15‘, v1938
UNITED STATE 5
‘PATENT 1‘ OFFICE
HANISM
Frederick Q. Rast, Binghamton, N. Y.. assignor
to International Business Machines Corpora
tion,‘ New York, N. Y., a'corporation of New.
'York /;
Application May ":1, 1935, Serial No. 20,138
1i Claims.
. (Ell. 265-5)
chart 26, the rim of which is graduated in pounds
and ounces, with the pound graduations marked
by the corresponding ?gures. The chart is viewed
through sight window fl (Fig. 3) in the front of
casingiii- and indexed by sight line 29.
For purposes of‘ the disclosure, it will be as“
This case relates to a scale with weight record
ing, indicating, exhibiting, or manifesting means.
The object is to provide simple means to obtain
a value manifestation or record in a lower order
denomination of a load value without directly set
ting such means by the load force.
sumed the scale has a capacity of (l to 69 pounds, ‘
More speci?cally, the above object is to provide
means for obtaining’ fractional pound readings,
preferably in ounces; without direct setting by
the load force.
I
'»
‘
.
making seventy pound divisions. The left side
of chart 26 (as viewed in Fig. 2) rigidly carries
notched disk 30 having seventy notches 3i, one
for each pound graduation of chart 26. At the
.
"Further, ‘the object is to look a load set mem
right of chart 26, its. shaft 22’. carries a tens order
ber and by such looking to set a value manifest
ing means mounted for movement independently
of the load set member.
Still further, the object is to set a load respon~
.
‘ sive member in an even load. position and by
such action to set a fraction load value manifest
ing means.
-
The object is also to effect the load setting of
a higher order value manifesting means while it
is free of means to supplement the load setting
and to then operate the latter means to’second
arily set the higher order manifesting. means at
an integral load position and by so doing set a
lower order or lower orders of value manifesting
means.
_
‘
_
/
Other objects will appear. from-the following
parts of the description and from the drawings.
Inthe drawings:
so
Fig. 1 is a vertical end section through one end
of the machine,
‘
-
1
Fig. 2 is a section along line 2—-2 of
i,
Fig. 3 isvan end-section through the machine
showing the parts in initial positions,
.Fig. 4 is a view similar to Fig._ 3 but
in operated‘ positions,
1
with parts
'
Fig. 5 shows the operating motor and clutch
control,
‘
‘
.
.
Fig. 6 is the circuit diagram, and
Fig. '7 is the timing diagram;
' -.
The weighing means comprises platform to legs
ll. of which are supported by ?rst principle. loase
levers l2 and?S. lever I2 is connected
the
stepped disk 32 and a units order stepped disk
Disk 32 has steps 34 of di?erent radial
3?).
heights to represent tens of pounds values 0, 1,
2-6. Each step ttcovers a range of ten pound
divisions of chart 265. Disk 33 has a series of ten
steps 35 each series coextensive with one of the
steps it of disk
>
_
,
The steps 3?» of a series differ in‘ height to repre 20
sent values 0 to 9 in the units. of pounds order and
each step covers a! single pound division of chart
it. To indicate the value represented by .a step
36 or 35, the digit indicating the value will be
appended to the common reference ‘character.
Thus with .a load on the scale of 45 lbs., steps
34-Q and 359-5 will be set in control positions.
Between frames it and 25 is a third frame 36
(Fig. 2) with a ball bearing 3“! for‘the. left end of
a sleeve shaft 38 surrounding but not touching 30
weight shaft 22. The right end of shaft 38 is
journalecl in bearing ill’ carried byv frame 25.
Operation of shaft/t2 under. a load has no effect
upon shaft 33.
Shaft 38 carries,‘ to the right of disks 32 and it, as,
the t-ens‘order ounce disk 39 andithe units order
' ounce disk fit. The outside peripheries of disks
39 and it are each at a radius equal to that of a
zero step St or
and therefore represent zero
values in the tens and units ounce orders. Disk
39 has a single step iii-l representing value i in
the‘tens ounce order. Disk W has a series of
nine steps t’i-—i, 2, 3,-4.9 coextensive with an arc
of disk 39 just preceding step tl-—i. Following
power end‘ to linkfld, actuating a third lever it. ~ the series of nine steps t2-i to E9, disk iii has a
= The power end or" lever i5 is connected by tape it
of steps ll2—@, i, 2, 3,—-@ representing
to a sector ll on shaft i8 carrying pendulum M series
values 0 to 6 in the units ounce order and lying
and rack sector 2d. Sector 20 meshes with pinion A
along an arc coextensive with step iii-l of disk
it on weight shaft 22-to rotate the latter clock- '
A combination of the disk steps 4i and (it
wise (as viewed in Fig. 1) or counterclockwise (as represents the ounce value of a load. Thus, step 50
50 viewed in Figs. 3 and 4) when a load is applied‘
to the platform.
As indicated in Fig. 2, shaft 22 extends to the
right of platform It and is journalecl at opposite
ends in bearings carried by frame plates or stand»
55 ards 24 and 25.-_ Shaft‘ 22 _ carries cup-shaped
[ii-t (the outside periphery of disk t9) and step
lit-8 represent 8 ounces, step ill-i and step '
tiZ-ii of the'second series represent 10 ounces,
and steps iii-‘J and @2-3 represent 13 ounces.
When a load is placed on platform it, the base 55
9,111,127
levers l2, l3, and I! are rocked to pull down on
tape l6 causing gear sector 23 to rock clockwise
(Fig. 1) and similarly rock shaft 22 with its chart
26 and stepped disks 32 and 33 according to the
load. For example,‘ a load oi‘ twenty-?ve pounds
and eight ounces will bring the corresponding
251/2 lbs. graduation of chart 26 to sight line 23
result, the tooth movement will not eifect move
ment oi’ disk 30 but on the contrary will lock it
in- its even pound position.
Should the tooth 53 move oil’ the even pound
point and into the notch 3| at the left of this,
point, then the inclined sides of this notch and
of tooth 53 will cam against each other as the
and‘ will set a step 34-2 of disk 32 and a step _ tooth moves downwardly and as a result, when‘
35-5 of the series of steps-of disk 33 coextensive
Under con
trol of these steps, the tens and units pound order
load record will be made, as will be later brought
out. In order to control the recording of the
.10 with step 34—2 at control position.
1'15
descending load direction, clockwise (as viewed
in F18. 3) to the extent of a full notch width.
This is equivalent to returning disk 30 through
ounce value of the load, which in the above ex
ample, is 8 ounces, disks 33 and 43 must be set
a full pound value and thereby subtracting one
position. The means for doing this will now-be
backward or reverse movement of disk 30 causes
pound from its primary load setting. However,
to bring the steps 4|—3 and 4|—3 to control ‘through means presently to be described, the
explained.
~
Referring to Figs. 2, 3, and 4, frame plate 24
20 has a guide bracket 43 at the upper end for slid
ably receiving and guiding the upper portion of
> a control bar 44.
The lower portion of bar 44
has a slot 440 'slidably coacting with a stud 45 on
frame 25. ,
;
v25
‘The upper end of bar 44 is pivoted to a léver 46
which is pinned at an intermediate point to the
core 41 of a solenoid 43. A spring 43 connected
to lever 46 normally holds core 41 and control
‘bar 44 at their upper limits. The portion of bar
30 44 passing through guide bracket 43 has a ver
tical slot 53 receiving pin 5| extending from one
side of a slide block 52 slidably mounted within
bracket 43. The lower part of block 52 is formed
to provide a knife edge tooth 53 which lies along
35 the plane including notched disk 30.
-
.
The tooth has a side extending radially of
disk 30 and a side inclined to the radial side.
Similarly, each notch 3| has a radially directed
side and a side inclined thereto. The angle be
tween the sides of a notch is the same same
angle between the sides of tooth 53 and the di
mensions oi' the tooth are such that the tooth
will fit snugly in a notch 3|. For convenience,
the radially directed side of a notch or of tooth
45. 53 may be referred to as the abrupt side while
the side inclined to the radially directed side may
be referred to as the inclined or cam side of a
notch 3| or'of tooth 53.
-
As previously stated, there are seventy notches
50 3| one for each of pound values 0 to 69. The
» points of the teeth 3|’ which form notches 3|
me at pound distances apart and each point
corresponds to an even~pound graduation of chart
26. Further, these points pass the point of knife
55 edge 53 in step with the travel of the correspond
ing pound graduations past index 23. Since each
notch corresponds to a range of one pound, the
notch may be considered as divided into six
teen equal divisions, each equivalent to an ounce
60 range of chart 26. If the load on the scale is
an even poundage, then the point of a tooth 3|’
which corresponds to such load value will be ex
actly opposite the point of tooth 53 and the
abrupt sides of tooth 53 and the notch to the
65
the tooth has fully and snugly entered this notch,
disk 33 will have been moved backwards, in a 10
right of tooth 53 (Fig. 3) will_be in radial aline
.Iment. Now, should tooth as be moved towards
corresponding movement of steppedv ounce disks
33 and 40 so that if the disk 33 has been reversed
a full pound, disks 33 and 43 will be set to read 20
out a value of 16 ounces.
Thus, for an even
pound load on the scale, the coaction of tooth
53 with disk 33 will in all cases provide accurate
load settings of the pounds and ounces orders.
If the load on the scale is a fraction greater 25
than an even poundage, disk 30 will move
counterclockwise (Fig. 3) past tooth 53 and ‘the
point of a tooth 3|’ corresponding to the even
pound value will be to the left of tooth 53 by an
amount equivalent'to the fractional value above 30
the even pound value. For example, a load of 25
pounds, 8 ounces will move the point of a tooth
3|’ corresponding to 25 pounds to the left of tooth
53 by half a notch width or by a distance equiv
alent to eight ounces. Now, movement of tooth
53 towards disk 30 causes the tooth to enter the
notch 3| which corresponds to the pound range
above the last even pound point and to cam
against the inclined side of this ‘notch to move
disk 33 backwards until the tooth is fully seated
in the notch. As a result of this cam action, disk
33 will have been set back half a tooth notch
distance or through an angle equivalent to eight
ounces. The reverse movement of disk 33 is pro~
portionally transmitted to stepped disks 33 and 45
43 to bring their steps 4|—-|I and 42-3 to con
trol position. ‘Further, as a result of the action
of tooth 53, disk 30 is locked in an even pound
position equivalent to the load less the fractional .
value.
'
50
The means for transmitting reverse movement \
of disk 33 to the ounce disks 33 and 43 will now
be described.
.
\
Control bar 44, as previously explained has a
vertical slot 53 receiving a pin 5| extending from
block 52 which isvformed with tooth 53. Con
necting bar 44 with block 52 is a spring 55 nor
mally holding the block in its lowest position on
bar 44,: this position being determined by en
gagement of pin 5| with the lower end of slot 60
50, as indicated in Fig. 3. Bar 44 is normally
held by spring 43 at its upper limit and bar 44
through engagement of the lower end» of its slot
53 with pin 5| of block 52 is normally holding
the block at its upper limit position. In this 65
position of block 52, the point of tooth 53 is free
disk 33, the point of the tooth and the point of _ of and above the disk 30.
Further, in the upper position of bar 44, a pin
and stop movement of the tooth. The disk 33 56 near its lower end is engaged with one end
70 will )thereby be locked in an even pound position.
of a lever 51 and holding the latter at its clock 70
Should the tooth 53 move oil’ the even pound wise limit (Fig. 3). Lever 51 is pivoted on pin
‘point of disk 30 and into the notch 3| at the 53 carried by frame plate 24 and has a slot 53
right oi’ this point (as viewed in Fig. 3), then engaged by a pin 63 extending from the side of
the'abrupt sides of this notch and of tooth 53 a plate or arm 62 which is pivoted at its lower
will merely engage along a radial line‘ and as a end on stud 63 ?xed to frame plate 24. Rigidly
75
I disk 33 corresponding'to the load may engage
2,111,127"
secured to the side" of plate 62 is 'an angle plate
66 (see Figs. 2, 3, andwl). Journaled between
.
7
'.
.3‘l
rim
clockwise
of chart
movement
26. Theofspring
arm 62
85 at
extends
the end
inofradial.‘
this
line with pin 66 and pivot 63 of'arin'62 so as to
plates 62 and 66 is ‘shaft 61 of a small, rubber
exert no turning ‘force on arm 62 and thereby to
covered, friction roller 68 which is in front of‘ the . ‘maintain roller 68 lightly'engagedwith chart 26.
'91.
With roller 68 engaged with chart 26, the lower,
.> When control bar 44 is
upper, normal, posi- . zero notch 10 of---.diskv 63 .is directly in frontof
tion, tooth 53" is clear Of‘diSk 30 and pin 56 is pawl tooth 15. ' Immediately after engagement of
engaging lever 51 to hold the latter in its ‘clock
roller 68 with'chart 26, the uninterrupted, con‘
5 rim of chart 26.
'
wise position. In iihlS'DOSltiOIl of lever‘ 51, its '
10>
tinued, downward movement of bar._44..begins to
10 notch 59 cams against pin 66 to hold arm 62 at move tooth 53 into .a notch 3| of disk 36 which
its counterclockwise limit and asrshown in Fig. 3,. is rigidly fastenedito chart 26.. As previously‘ ex
the arm 62 when thus set m tains'r‘oller'68 plained; ‘the movement of tooth 53' into a notch
clear of-and out of contact wit the rim of chart
26. While these parts 44, 51, 62, and 68 are thus
, _
j , '\
3i’ sets disk 36 back to-the ‘even pound load posi- »
lion and locks it in the! latter position,'mean
'whileimoving ‘disk 36 clockwise (Figs. 3 and 4)
set it without vinterference from roller 68.
to subtract‘the fractional pound ‘value of the load
Fast to the left end of shaft 61 of 'roller 68
from the load‘ responsive setting of disk 31L ‘Asa
(as viewed in Fig. 2) is a disk 63 ‘having seven
result oilthe setting‘of ‘diskV'30. chart 26 is. also
teen notches 10 which correspond in clockwise returned an amount corresponding" to the "freeorder (Figs. 3 and 4) to 0 to 16 ounces. ‘On the‘ tional pound value ofthe load. " The chart 26 at,
01 in home positions, the load acts on chart 26 to
20
20
~
right hand end of shaft 61 (as seen in Fig. 2) is . - the, vend: of this return-movement will have“ its
wound a fine clock spring 12‘ connected at oppo
site ends to shaft 61 and plate 66 to normally,
though‘lightly, urge shaft 61 and its roller 68 ‘in
‘ a clockwise direction (Figs. 3 and 4). The clock-7
even pound graduation'dlrectly at index line .29.
Since roller 68 was engaged with chart 26 before
the chart retum. movement was begun, the roller
68 will be Irictionally rotated counterclockwise
wise movement of shaft, 61 under the in?uence of. . (Fig, 4) byv chart 26 ‘in .‘proportio'n to ‘reverse
spring -12 is limited by engagement of a pin :13 movement of the- chart. For each ounce return
extending from the right side of notched disk 69 movement of chart 26, roller 68 is rotated through
.on shaft 61 (see ‘Fig. 2) with a ?nger .14 rigidly an‘angle covered by a tooth notch 10 of ‘disk 69.
projecting from the'upper, free end’ of plate 6.2. Thus,‘ for an eight ounce-‘returniof chart
25
Whenpin 1.3 ‘and ?nger 14 are engaged, disk 69 _. roller 68, its shaft 61, and disk 68 are‘ rotated
is in zero position.
.
..
At the left of disk 69 (as viewed in Figs. 3 and
counterclockwise through: ariJ angle_'cove'red by
eight notches]!!! of disk .69. . Thus, eachnotch 10
4.) is a pawl tooth 15 carried by an arm 16 pivoted ' is-equivalent to an ounce load value.‘ Initially,
to frame stud 11. ‘A spring 18 normally holds
arm 16 and .its pawl tooth 15 free of disk 69'.
Control bar 44 is connected to a plunger 19 .
of a dash pct 86 adapted to dampen the down
ward movement of bar 44 and to cause this move
.
before return movement. of chart 1'26 begins and
with ‘roller 68 engaged withJthe chart‘, the-"pawl
nose 15 is in line' with the center‘of the lowest, _ '
or zero notch-10. Should chart v26 now be re-.' .40 f
turned less than'ghalf' an‘ounce distance; the zero
40 ment to be uniform.
notch‘ 16 will nothave moved past pawl nose 15-v
effectively time the down stroke of the control and consequently when the latter ismoved to
wards disk 69, ‘it will seat in the‘ zero notch .10
After chart 26 has been set in direct response. > and lock. disk 69. in its ‘zero position. Should
to a load on the-scale, the operator depresses a chart 26 be returned more than half 'an'ounce
45 start key ST to close starting contacts ST’ form-distance, zero notch") will pass pawl 15 and
The dash pot also serves to ‘
bar.
'
r
'
v
'
ing the following circuit (see Fig. 6) : -'
. .
the next, one ounce notch 10 will‘lie in the path
From + terminal 8|, through starting contacts. . of movement ofjpjawl 15.‘ Thus,-. the notchesiare.
ST’, through magnet 82, and normally closed cam arranged to pass pawl 15 at the half-ounce load
contacts 83 to the - terminal 84.
'
values. For example, 1% ounces above an even
5ft Above circuit energizes magnet82 to attract 'pound load will bring'the _2 ounce notch 10 in I
armature 82’ to close contacts 82a thereby shunt
line with pawl 15 while 1% ounces will bring the
ing starting contacts ST’. vThe circuit will now
1 ounce notch 16 in line with pawl .15.
’
Should _
remain energized as long as cam contacts 83 are‘ the ounce ‘value be exactly 1/2, then the point- of j
closed.
'
_
.
Armature 82' as diagrammatically shown in
Fig. 6 not only closes contacts 8211 but also simul
\ taneously closes parallel contacts 82b. Closing of
contacts82b connects solenoid 48 across the +
and — sides of the line and as a result, the sole
60 noid is energized. The solenoid thereupon-de
presses its core '41 to rock lever .46 downwardly.
against resistance of spring 43 and to-move con
trol bar 44 throughits down stroke. The down
ward movement of bar 44,‘ is resiliently communi- -
pawl 15 will contact a pointer disk 68 and ei’fec-'. tively lock the latter in its halfeounc'e position. ,
Should, however, the point of the pawl pass the -
point of disk 69 and move into the notch 16 ‘at
either side of this point, the maximum error will
be plus or minus one-half an.ounce._
'
>
60
As indicated in Fig. 4, disk 36 and chart 26 are .
locked by'tooth 53 in any even pound position‘
after an‘ eight ounce return movement of .chart
26.
As a result of the return of chart 26, roller - I
68 .and disk 69 have been rocked counterclociv. 65
cated to block 52 of tooth“ by means of spring" wise through an angle spanned ‘by eight notches
connection 55.
10,‘ther_eby bringing the ninth notch 18 which _'
Before the point of the tooth reaches the locus represents an 8 ounce value into line with pawl 15.l
of the points of teeth 3|’ of disk 30, pin 56 re
Now tooth 53’ is fully seated in a notch 3| of
leases lever 51 to permit a light‘ spring 85-con
70 nected at the upper end to the frame 24 and at»
the lower end to pin 6ll‘-—to rock' arm 62 clockwise
~ from the position shown in Fig. 3 to that shown
disk 30 and its downward movement is thus,ar- .
rested. Control bar 44 however continues its
down stroke and stretches spring 55 between the
bar and tooth 53. The ?rst part of the downward
in‘ Fig. 4. ‘A very slight’ amount of clockwise . movement of bar 44 after tooth 53 has beenfully
movement of arm 62 is su?icient to bring the seated in a notch 31 engages thepin 56 with an 75
75
periphery of roller 68 into engagement with the
4
2,111,127
arm 91 pivoted on frame stud 11 and rocks the
pawl tooth into engagement with the teeth of
ratchet] disk I99 causing the latter to impart ro
tation to disk I99 and its shaft I91.
Referring to Figs. 3 and 4, shaft I91 has a box
arm clockwise. _ Through a spring 98, the clock
wise movement of arm 81 is resiliently trans
mitted to arm 19 thus bringing pawl 15 into
- . locking engagement with 8 ounce notch 19.
Disk
cam disk I I5.formed at one side with cam groove
99 is now locked in a differential position corre
II9. Riding in groove H9 is a follower pin “1
extending from the side of a link II9 which is
slotted at the left end to receive shaft I91 and
pivoted at the other end to a lever II9. Lever
H9 is connected by a ‘link I29 to an arm I2l
rigidly carried by a sleeve I22 rotatably mounted
on shaft 95 and heldin place against movement
sponding to the fractional load value. Operating
under control of disk 99 are means to‘ corre
spondingly set ounce disks 39 and 49, as will now
be explained.
-
Frame 29 has a stud 99 which is to the left of
shaft 91 of roler 99 (as viewed in Fig. 2) . When
roller 99 is engaged with chart 29, stud 99 and
shaft 91 are in axial alinement. Rotatably
mounted on stud 99 is a gear sector 9| integrally
provided opposite the gear teeth with a ?nger 92.
Finger 92 is adapted to engage a pin 93 extend
ing from the left side of disk 99 (see Fig. 2).
When roller 99 is moved into engagement with
$30 chart 29 and disk 99 is still in zero position, pin
93 is engaged by ?nger 92. This is \the home po
sition of the ?nger and of its associated parts.
After disk 99 is moved counterclockwise to an
‘ounce setting, then by means _to.be described
later, the ?nger 93 is vmoved in the same direc
along shaft 95 by opposite bushings I23 pinned to
the shaft (see Fig. 2). Also fast to sleeve I22 is
an arm I 24 extending oppositely to arm I2I. 15
Arm I24 has a stud I25 projecting into an arcu
ate slot I29 cut in gear 99 and is connected to
gear 99 by a light spring I21.
‘Shaft I91 of cam disk II5 has been set‘ ro
tating, as previously described. During the ?rst 20
60° (see the timing diagram, Fig. 7) of the revo
lution of disk II5, its cam groove II9 coacts with
follower pin II1 to move link “9 to the right
away from the home position shown in Fig. 3. ’
As link “9 moves to the right, it rocks'lever
tion to engage pin 92 and be stopped thereby in a V ||9 clockwise and the lever, in turn, through link 25
position-corresponding to that of disk 99.
I29 rocks ann I2I and its sleeve shaft I22 clock
Gear sector 9| is meshed with a gear sector 94 wise away from their initial positions shown in
fast to the left end of a shaft 95 which at the Fig. 3. As sleeve shaft I22 rocks clockwise its
30 right end (as viewed in Fig. 2) rigidly‘carries
arm I24 moves in the same direction and through
a larger gear sector 96. Gear sector 99 in turn
meshes with a gear sector 91 fast to. sleeve shaft
39 and ounce disks 39 and 49. Thus, as finger
92 of gear sector 9i moves from its initial, home,
_or zero position to engage pin 93 of disk 99, gear
light spring I21 yieldingly draws gear 99 after it.
As gear 99 is fast to shaft 95, the latter is also
moved clockwise. Gear 94 on the shaft there
upon rocks gear 9| on stub shaft 99 counterclock
wise until ?nger 92 engages pin 93 of locked disk 35
99. As a result, gears 9|, 94, and 99, are stopped
sectors 92, 94, 99, and 91 move through angles
proportional ‘to the ounce setting of‘ disk 99 and
after being moved through angles corresponding
therefore correspondingv to the fractional load
to the ounce setting of disk 99. Arm I24 which
actuated these gears through spring I21 into
value. As a result, shaft 39 and its ounce disks
40 39 and 49 are set with the steps 4| and 42 repre
senting the ounce values at the, control position. i
their differential positions, continues moving to
the end of its forward stroke after the gears are
arrested under control of disk 99 and spring I21
Fig. 4 indicates the positions of ‘disks 39 and 49
at the end of their setting according to an eight
ounce value. A step 4|-‘-9 and a step 42-9 are
45 in control position.
stretches.
-The movement of gear sector 9I-and there
and 49—under ;control of disk 99 is governed as
'
'
‘
40
_
As gear 99 rotated clockwise, it rocked meshed
gear 91 and its sleeve shaft 39 counterclockwise 45
to moveounce disks 39 and 49 in the latter di
rection. Thus, if as previously assumed, disk
99 has been set in an 8 ounce position, then rig
idly connected disks 39 and 49 will be moved
from their home positions shown in Fig. 3 to the
'
fore of the elements 9.2, 94, 95, 99, 91', 39, 39,
follows:
30'
,
50 ,> ‘Immediately after bar 49 through its pin 59
> has caused the locking by pawl 19 of disk 99,
.positions shown in Fig. 4.
the lower end of the bar engages the upper one ~
At this point, ‘all the stepped disks are set in
of a pair of spring blades 99 and I99 to close control positions according totthe even pounds
switch "I, the points of which are carried ‘by ' and fractional pounds of load on the scale. Thus
. the spring blades. Referring to Fig. 6, closing of for a load of 25 lbs. 8 ounces,.disk 32 has a step
55
switch I9I establishes the followingcircuit:
' 34—-2 in control position, disk 33 has a step
Circuit A.--From + terminal 9|, through 35-5 in control position, disk 39 has its step
‘ switch I.9I and clutch magnet I92 to .— termi
4I—9 in control position, and disk 49 has its step
‘nal94.
60
_.
1
,.
-
42—9 in control position.
The above circuit energizes magnet I92. ‘ R.e-- '
V‘Jferring to Fig 5, magnet I92 when energized rocks
.
The‘ control positions of the several {stepped
disks, are the positions which are in line with
sensing ?ngers I39, one for each of the disks.
latch lever I92a counterclockwise to release a
clutch-pawl I 95..‘ The pawl is carrledby a disk The action of these ?ngers and the means conI99 rigidly carried by ,a shaft 1191 journaled be
trolled thereby is similar and therefore only one
tweenoframe plates 24 and‘25"
need be speci?cally described, the units of ounce
Rotatably carried by shaft in at one side ‘of ' sensing ?nger I39 being selected.
)
disk I99 are the rigidly conected' worm gear I99
The forward stroke of arm I24 and the setting
andv ratchet disk I99. Gear I99 meshes with of ounce disks 39 and 49 are completed at 99'
worm 1I'I9 on shaft III of motor M. Motor M is of the revolution of shaft I91. ‘ Cam groove II9
set in-operation at the beginning of a series of has an arcuate portion permitting the arm I24 to
weighing and recording operations -and~may ‘be dwell at the‘ end of its forward stroke until 215°
considered as in continuous operation.
Accord
.ingly, ratchet‘ disk I99 is continuously rotating.
1 -Now when latch I920. is released by magnet I92
from clutch pawl I95, 9. spring “2 moves the
of the revolution of shaft I91 .(see Fig. 7).
,
95
'
70
‘
Disk H5 is formed at the side opposite groove
II9 with another separate box cam groove I32
within which is the follower I33 of an arm I34 75
'
secured to a, shaft I 36 which also has fastened
to it an 'arm I36. Arm I36 is connected by a
link ‘I31 tosan arm I36 fast to a shaft I36- Shaft
5
.
' 2,111,127
.51
further than lever I53 and strikes thetype wheels
a sharp blow. Between the hammer‘ and‘type
wheels is a card guide or chute I59 in which a
card or sheet C is inserted before the weighing
I39 rigidly carries bail arms I40 connected at operation. Between the card,C- and type wheels
their outer ends by a bail .rod_ I42. Rod I42 is
an inking ribbon R. Thus, the hammer when
‘separately connected by 'individualnsprings I43 ‘ is
it strikes the type wheels causes the latter to
to each of four levers I44 (only one is shown)
which ‘are freely pivoted on shaft I39. Each ‘print the load record on card 0.
lever I44 is pivotally' connected at its upper end
10 to a separate one‘ of the's‘ensing ?ngers I30.
[After the weight record has been made, the
partsv are ready to be restored.
As indicated by‘the timing diagram, between
65° and 125° of the revolution of disk H5 and
'
10
Asvindicatedin the timing diagram (Fig. '7),
the printing operation is completed at about 135°
of the cycle. ~At 150° of‘ the cycle, cam groove
I32 functions to move rod I42 counterclockwise
and the rod engages -the levers I44 to restore 15
them and- their connected sensing ?ngers I30 and
type wheels I46 to zero on home positions. The
while arm I24 is idling at the end of its forward
stroke, cam groove I32 acts on follower I33 to
15 rock arm I34 and its shaft I35 counterclockwise
from their home positions shown in Fig. 3. Arm
vI36 of shaft I,35 thereby rocks counterclockwise
and through link I31_rocks shaft I39 clockwise.
restoration of these parts is completed at 210° >
of the cycle.
As a result, rod I42 moves clockwise and through
20 springs I43 yieldably moves levers I44 in the same
direction. As levers I44 move in this direction,
. .
_
The stepped disks 39 and 40 are vnow free to 20
be restored. At 215° of the cycle, cam groove
H6 functions to cause counterclockwise rocking
of arm I24 and its stud I25; As the stud moves
they bring ?ngers I30 .into engagement with the
control steps of the disks 32, 33, 39, and 40.
The ?ngers are stopped in di?erential posittions'c'orresponding to the heights‘ of the steps
which are in; control positions. When a ?nger
counterclockwise; it encounters the lower end
wall of slot I26 ‘and positively restores‘ gear 96 25
and its connected parts 91, 38, 39, 40, 95, 94, 9|,
and 92 to their home positions. The restoration
I30 is thus arrested in a differential position, its ~ of the latter parts is completed at 275° of the
‘operating arm I44 is likewise and similarly ar
rested. Rod I42 however continues to the end
30 of its clockwise stroke and stretches springs I43
after the levers I44 have been arrested. Rod
~ cycle.
I42 now idles under control of cam groove I32
at the limit of its clockwise stroke until 210°
of the cycle.
as.
'
As shown in Fig. 5, shaft I01 has a cam I65 30
which is engageable with the long blade 830 of
contacts 83 to separate it from short blade 83I
to thus open contacts 83. As indicated in Fig. ‘7,
between 280° and 285° of_the cycle, cam I65 opens
83. This results in breaking the circuit
Each lever I44 is formed at its lower end with } contacts
through magnet 82 which thereupon releases its
:teeth I46meshed with a pinion I41 of a type armature 82’ to cause contacts 82a and 82b to
wheel -I48. When lever I44‘ is set in differential
35
open. Cam I65 permits contacts 83 to reclose
before the end of the cycle of shaft I01 but since
contacts 62a are then open, the circuit through 40
position, through teeth I46 it rotates pinion I41
and type wheel I48 to bring-into printing posi
40 tion that type lug intended for'pri'nting the digit
magnet 82 cannot be made again except by the
represented by the differential position of lever ‘
closing of starting contacts ST’.
I44. Since ‘this differential position is deter
mined by the step engaged by ?nger I30, it is
evident that each type wheel I48 is set to print
45 the value corresponding to the height of the
control step. Thus, the units ounce order type
wheel. I48 is set to print 8 under control of step
42-6 of disk 40, as shown in Fig. 4.
.
1
Opening" of contacts 821) breaks the circuit
through solenoid 48 and control bar 44 starts its
return or upward stroke. As bar 44 moves up,
it releases blade 99 and switch IOI opens, thereby
breaking'the circuit through clutch magnet I02.
This occurs at, about 285° of the single revolution
of shaft 101. With clutch magnet I02 now de
energized, spring I02’ returns latch mm to in?
For'a load ‘of 25 lbs. 8 ounces, the tens and
50 units disks 32 and‘ 33 will respectively control
itial position for intercepting the tail of clutch
their sensing ?ngers I30 and connected levers I44
pawl I 05. When disk I06 and its shaft I01 have
made one revolution, latch I020. engages pawl I05
to'set the tens lbs. order and the units lbs. order
type wheels to print 2 and 5, respectively while
rocks it out of engagement with ratchet disk
disks'39..and 40 will respectively set their associ-‘ . and
I09, thereby ‘uncoupling shaft I01 from the motor 55
ated
tens
of
ounces
and
units
of
ounces
order.
55
drive. l/When pawl I05 is engaged by latch mm,
' type wheels torespectively print 0 and 8.
A_t 125° (see Fig. '1) of. the revolution of shaft
“I01, all the type wheels I48 have been set ac
cording to the load and remain set while- rod I42
is idling-at the end of its forward stroke until
the latter also engages a projection I06’ of disk
I06 to stop the disk and its shaft I01 in a definite
home position after the shaft has made a single 60
.
revolution.
’
K/
As bar 44 is now moving up, pin 56 leaves arm
150° of the cycle. During this idling period,
printing, takes place. The means 'for effecting
81 permitting springs 68 and 18 to retract lock
printing comprises a shaft I50 geared one-to-one
tooth 15 from the notch 10 of disk 69 engaged by .
by gearing I5I to shaft I01.-
Shaft I50 has a cam
I52 coacting with follower lever I53 rotatably
the tooth. During a further part of the return
stroke of bar 44, pin 56 engages lever 51 to rock
mounted on a shaft I54. Lever I53 is connected ' it clockwise (Figs. 3 and 4) causing its slot 59- to
by spring I55 to a hammer I56. At 135° of the cam against pin 60 for rocking arm 62 counter- ,
cycle, cam I52 permits lever I53 to be rocked clockwise. This movement of arm '62 withdraws
clockwise by a spring I51.' The lug I58 on lever roller 68 from engagement with. the rim of chart
I53 held engaged with hammer I56 by spring I55 26. As bar 44 moved to bring its pin 56 from arm
thereupon imparts clockwise movement to the
hammer
The drop in cam I52 is such that lever
I53 stops clockwise motion before hammer I56
strikes the type lugs-of type wheels I48. Due to
75 its momentum, the hammer continues to move
81 to lever 51, through spring 55 it' moved tooth
53 upwardly. Following the point of the return
stroke at which roller 68 was disengaged from
chart 26, the lower end of slot 50 of bar 44 en
5
6
2,111,127
gaged pin H of block 62 of tooth 63 to positively
bring tooth 63 clear of disk 30.
'
'
The parts are now in their initial positions, in
,
5
dicated in Fig. 3.
>
'
_
>
set the-printing wheels I30" to 'printthe load"
values;
At 135° of the cycle, cam I62 causes hammer‘
I66 to strike the type wheels for making a load
value imprint on a card C.
Summary
. -
Following the printing operation cams “6, I32,
A load is placed on platform I0. The weight of ' and I52 restore their-associated parts to initial
the load causes levers I2, I3, and I6 to depress positions. 1 At 285° of the cycle, cam I66 opens
tape I6 to thereby rock pendulum shaft I6 clock , contacts 03 to cause deenergization' of, solenoid 33
10 wise (Fig. 1) through an are equivalent to the and magnet. 02.. Solenoid III now rises and switch
10
/load. Through gears 20 and 2I, shaft I8 similar
IOI- opens and breaks" thecircuit. through clutch
ly rocks weight shaft 22 and its rigidly. carried magnet I02. Deen‘ergization of magnet I02 re
parts, chart 26, tens of pounds" stepped disk 32 sults in shaft I01 being stopped after it'has made
and units of pounds stepped disk 33.
15
.
6) to close contacts ST’ thereby forming a cir
cuit through magnet 82.
v20
'
The operator now depresses start key ST (Fig.
Energization of the
magnet closes contacts 82a to shunt out the start
ing contacts ST’ and closes contacts 62b to ener
gize solenoid 38. Solenoid 48 now moves'control
bar 33 through its down stroke.
_
The initial part of this stroke withdraws pin
66 of bar 43 from lever 61, permitting a light
spring 06 to rock the arms 62 and 66 to bring
one revolution. As bar 43 moves through its re
turn stroke, the parts directly controlled thereby '
.return to initial positions.
a
-
While ‘only a'single embodiment of the inven
ticn has been‘ disclosed, it isto‘be understood
that any variations, ‘departures, or modi?cations
derived from the principles of theinvention are
to be considered as within the bounds of the in
vention which is to be limited only by the scope‘
of the claims.
I
claim:
'
'
'
.
_
'
25 the friction roller 68 carried by the arms from
1. In a load weighing scale; vthe combination
the position shown in Fig. 3 to the position shown of a rotatable disk primarily settable in a load
in Fig. 4 in which the roller is engaged with the ' position, means for rotating said'disk away from a
rim of chart 26.. The next part of the stroke 10f
bar 44 starts moving tooth 53 into a notch 3! of
30 disk 30 and as the tooth moves intoth'e notch it
earns the disk 30 clockwise in a direction reverse
to that in which it is moved by the load.
When
the load position in proportion to a fractional
value of the load, a friction-wheel .frictionally
rotated. by engagement with the diskv during ro
30'
tation of. the disk by said means, and indicat- '
ing
_
mechanism
controlled by the friction,
I
wheel
the tooth is seated ?ush in the notch 3|, it has ‘for operation according to rotation of the wheel
set disk 30 back trough‘ an angle corresponding . by the disk. .
'
a ‘
35 to the ounces above the even pound'age and has
2.
In
a
load
weighing
scale;
the
combination
locked the disk In such position._- As disk 30 is of 'a rotatable disk primarily settablein --a load
fast to chart 26, the latter and'its shaft 22 are positiornmeans for e?fecting a secondary setting
correspondingly set back. Stepped disks 32 and - of the disk to rotateit in proportion to -a frac-'
33 are also set back and this results in the central tional value of the load, a friction wheel engage-n
40 position of a pound step 35 of disk .33 being in
able with the rim oi’;v the disk to be frictio'nally
front of its sensing ?nger I30, thus removing the rotated .thereby‘during its secondary setting, and 40
danger of the ?nger engaging the point of the indicating mechanism'controlied by said friction '
step 36 and sliding on’ the. point to abutthe
incorrect tooth.
-
I
~
As chart 26 is set back, it frictionally rotates
roller 66 counterclockwise (Figs. 3 and 4) through
anangle corresponding to the ounce orders of
the load. When the chart 26 has been locked in
wheel for'operation according to -'said‘ fractional
. load value.
3. In a load weighing: scale; the combination of
a rotatable disk primarily settable in a position
corresponding to the load, means .to effect a sec
ondarysetting-of the disk to rotat'eit away from
, its even pound position, disk 69 on shaft.“ of ' said load position in proportion to a fractional
50x roller 30 has a notch- 10 corresponding to the value of the load, a friction wheel normally free of
50'
‘ ounce load in position to be engaged by a pawl
the‘ disk, means controlled by operation of the
13. The downward movement of bar 43 continues ?rst-mentioned means preliminary to effecting
andpin 66 strikes lever 01 to rock pawl 16 into, said secondary setting operation for engaging said
engagement with the notch 10 of disk‘ 69 which
. 55 corresponds to the ounce load. At the end of the
down stroke of bar 43, it closes switch IOI.
When switch IOI closes, clutch magnet I02 is
energized to release shaft I01 for a single revolu
wheel with said disk to thereby cause‘ the diskr to '
55
frictionally rotate the wheehduring the secondary
setting operation in accordance with-said frac—
tional load value, and indicating mechanism con
trolled by said wheel according to its rotation.
tion cycle. Referring to the. timing diagram, Fig.
‘a. In a load weighing scale} the combination
50 7, between 0 and 60° of this cycle, a cam groove
of
a rotatablyv mounted diskv responsive to the
II6 of disk H5 “on shaft I01 causes clockwise
force
of the load to be set thereby in‘ load ‘posi'r'v
movement of an arm I24 to move parts 9|, 92;
93, 95, 96, 91, 33, 39, and 40 in accordance with tion, means operable subsequently to load setting .'
the ounce setting of disk 69. Astep ll of disk 39 of the disk for effecting a secondary setting of
65 and‘ a step 42 of disk 30 representing the tens’ the disk by rotating-it away from the load po
and units ounce orders of the load are’now‘ in a sition in proportion to. a fractional load value. a._
front of their sensing ?ngers I30.
friction wheel of lesser diameter than the disk,
Following the setting of disks 39 and 30, a‘ cam normally free of the disk and movable into en- '
groove I32 of disk II6 causes the levers I“ to be gagement with the disk to be- frictionally rotated
70 differentially positioned under control of them
by the latter during its secondary setting through
gagement of sensing ?ngers I30 with the steps 34, a greater angle than the angle of secondary ro- »70
36, ‘I, and 42 of the tens of pounds disk 32, units tation of the disk, movement multiplying mech
“of pounds disk 33, tens of ounces disk 39, and anism controlled by ‘the wheel In accordance with
units of ounces disk 40.
75
rotation of the latter to further multiply the sec
The levers I“, when differentially positioned. ondary movement of the disk. and mamas: de
9,111,127
vices controlled by said mechanism for operation
in proportion to said fractional load value.
5. In a load weighing scale; the combination
of a member movable proportionally to the load
to a position corresponding to whole and frac
iional values of the load, means to effect a supple
mentary movement of the member in proportion
to the fractional load value, a plurality of ele
ments, one having steps representing the digital
values of a lower denominational order of the
fractional load value, the other having steps rep
resenting the digital values of a higher order of
the fractional load value, means controlled by
the member in accordance with its secondary
movement for commonly actuating said elements
to select steps of each representative of the dif
ferent orders of digits representing the fractional
load value, ?ngers for sensing the heights of the
selected steps, and multi-denominational order
indicating devices controlled by the ?ngers to
indicate the fractional load value in its several
orders.
6. In a weighing scale; the combination of a
notched member movable proportionally to the
load, a tooth movable into a notch of said mem
ber and arranged and constructed to cammingly
coact with a wall of said notch during movement
into the notch to effect a supplementary move
ment of the member proportional to a fractional
load value, and indicating mechanism controlled
by the member according to its supplementary
movement to indicate said fractional load value.
'7. In a weighing scale; the combination of a
rotatable disk movable proportionally to the load
35 and having notches with inclined sides, the width
of each notch corresponding to a single pre~
selected unit value of the load, a knife edge
shaped to ?t into a notch of the disk, means for
moving the knife edge into a disk notch to cause
40 the knife edge to cam against the inclined side of
the notch and rotate the disk in proportion to a
fraction of such unit value, an indicating device,
and mechanism controlled by the disk for operat
ing the indicating device in accordance with the
45 extent of rotation of the disk by said knife edge
7
to thereby enter said fractional value of the load
unit into the indicating device.
8. The combination as de?ned in claim '7, the
mechanism controlled by the disk including a
wheel normally free of the disk, and moved into
engagement with the disk under control of afore
said knife edge operating means, said wheel after
engagement with the disk being rotated thereby
reversely to rotation of the disk and in proportion
to the fractional unit movement of the disk, and 10
means cooperating with the wheel to convert ro
tation of the latter into equivalent operation of
the indicating device.
9'. The combination as de?ned in claim 7,
aforesaid mechanism including a cyclically op
erable actuator, a device controlled by the knife
edge operating means for setting said actuator
in operation for a single cycle, and means con
trolled by the actuator for operating said indicat
20
ing device under control of said disk.
10. In a load weighing scale; a rotatable disk
primarily settable in a load position, means for
effecting a secondary movement of the disk by
rotating it away from the load ‘position in pro
portion to a fractional value of the load, a wheel
of lesser diameter than the disk having periph
eral engagement with the disk and rotated by en
gagement with the disk through a greater angle
than the latter during the secondary movement
of the latter, and indicating mechanism con 30
trolled by the wheel for operation according to
the rotation of the wheel by the disk.
11. In a load weighing scale; a rotatable mem
ber primarily settable in a’load position, means
for effecting a secondary movement of the mem
ber by rotating it away from the load position in
proportion to a fractional value of the load, a
rotatable device of lesser radius than the member
and having peripheral engagement therewith to
be rotated thereby during secondary movement 40
of the member through a greater angle than the
latter, and indicating mechanism controlled by
the device for operation according to the rota
tion of the device by the member.
FREDERICK Q. RAST.
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