Note: Descriptions are shown in the official language in which they were submitted.
This .i.s a division of Serlal No . 161, 548 ~ila~ Januaxy
18, 1973, a division of Serial No. 112,898 flled May 13, 1971.
The presen~ invention relate~ to 8 perfor~cor for
punching ~ series of holes along ~che length of a web as it is
~ntermittently ~dvanced, and particularly to such a per~orator
w~ich perorates film 5~rips at a rate much grPater than here-
tofore possibl2 and which is adaptable to dlfferent film form8ts
a~d ilm wideh~, .
Continuous and in~ermittent perforators have been
u~ed in the ar~ to perora~e a row of perforation~ in succession
~long the leng~h of a web or film. In ~he manufacture of mo~ion
pi~ture ilm, w~ere a h~gh degree of accuracy is required in th~
ormat~on of the perfora~ions, per se, and the pitch therebetween
~t has been the usual practice to use per~ora~ors having a single
frame intermit~ent shut~le advanr~ ln c~mbination with a pilot
pin. In ~uch perforators, the ~ilm is in~ermittently advanced
~hrough a perfora~ing sta~ion by a ~hut~le mechanism having a
claw which engages a perforation ln the film previously made by
a reciprooal punch which acts on the film in ~he perorating
station while the film is sta~ionary. To insure high accurac~
~n the pi~ch be~ween perforations, a pilot pin is associa~ed
with the punch to move therewith. This pilot pin is located
between the punch and shuttle meehanisms by a distance from the
punch equal to one perforation pi~ch, and ~s arranged to
enter the perforation previously made by the punch just be-
fore the punch engages the film so as ~o accurately adjust
the f~lm adv~nce b~fore a succeedi.ng perforation is made. The
p~lot pin which is formed to accurately fit a previously ~de
:
~ . .
~ - ,
~ 5~
perforation is provided to correct for any slight inaccuracy in
fiLm advance which might be made ~y the shuttle mechanism.
~ hile perforators of the type having a si~gle frame
intermittent shuttle advance with pilots are known to possess
high accuracy, they are limited as to the speed at which they
can be operated because the conventional cam and follower
designs they have used in the shuttle mechanism will not stand
; up fox a reasonable length of time under the high accelerations
involved in high spaed operation. Furthermore, conventional cam
and follower designs used in shuttle mechanisms are subject to
sev~re wear, lubrication and heat generation problems, while
; ball bearing ~ollowers axe generally too massive and short in
life. Another shortcoming of known perforators of this type
has been ~he necessity of temporarily splicing the end of a
new web onto the end o an expiring web, or providing the and
of the new web with two or more perforations, in order to
thread a new web onto the perforator. Also, intermittent film
per~orators of the type mentioned have had a top speed of about
3,580 perforations per minu e and have been designed to ha~dle
one foxmat of ilm, e.g. 35mm, 16mm, 8mm and/or Super 8.
- Thus, in accordance with the present teachings, a film
advanci.ng assembly for intermittently feeding an unperforated
web strip through a given path is provided. The essembly
comprises a web guideway defining a portion of ~he path and
including support means for supporting face of the weh and
including a roller to facilitate movement of the web. Edge
guides are provided for guiding the edges of the web with means
provided for providing access to the other face of the web.
- A shuttle is provided which reciprocates through a path including
3q a web advancing stroke and a retur~ stroke and which has a~- ~ `!
friction pad attached to the shuttle to reciprocate therewith.
-3-
~5~
Means are provided Eor reciprocating the shuttle and causing the
friction pad to moYP, via the acce~s means, into pressing engage-
ment with other face of ~he web at the beginning of and during
the web advancing stroke of the shuttle to advance the web with
the pad retracting from engagement with the web duxing ~he return
stroke~
The novel fea~ures which I consider characteristic of
my invantion are se~ forth ~ith par~icularity in ~he appended
claimsO The invention itself, however, both as to its organi-
zation and its methods of operation, together with additionalobjects and advantages thereof will best be understood from the
following descr.iption o~ specific embodiments when read in con-
: nection with the accompanying drawings in which:
E'igure 1 is a front elevational view of the punch andthread-up shuttle mechanism of a perforating device construc~ed
in accordance with a preferred embodiment of ~he present invention
with the front fr~ne of the device bei~g partly broken away for
purposes of clarity;
4-5
~s~
Flgure 2 is a tl-ans~erse sect I on~l view taken sub~
~tantially along line 2-2 of Flgure 1, and showing the main shaft
assembly;
Figure 3 is a sectional view of the punch and thread-
Up shuttle mechanism of the perorating device taken substantlally
along linP 3-3 ~f Flgure 2;
Figure 4 ~s a top view ~aken substantially along the
line 4-4 of Figure 3;
Figure 5 shows a schematic of the high speed shuttle
10 showing the relationship between the upper cam, the flat cam,
the shuttle tooth path, the film plan and the eccentric dr~ve
sha~t;
Figure 6 shows plots of shut~le claw paths necessary
or the perforation of 35mm, Super ~, and regular 8 film
formats;
Figure 7 i5 a transverse sectlonal view taken sub-
æ~antially along the line 7-7 of Flgure 1, and showing the
- thread~ up shuttle assembly.
Figure 8 is a fragmen~ary sec~ional view taken sub~
stantially along the line 8~8 of Flgure 1, and showing bearing
assemblies for the thread-up shuttled
Figure 9 is a transverse sectional view taken sub-
8tantially along the line 9-9 of Figure 1, and showing the
thread-up shuttle film engagement area. -
Figure 10 is a top view of F~gure 7 with the ~trippersremoved and showing edge guiding and die arrangements necessary
` t~ per~orate regular 35 mm film.
~ .
.. . . .
~l~5~
Figure 11 is a schem~t:ic of the thread-up shuttle
snechanlsm showing the geome~rical relationships of the eccentric
drive shaft, the.engagement arm pivot point, and the film
engagement area.
Figure 12 shows the electrical control diagram for both
thread-up and high speed operations;
Figure 13 is a schematic view of a modification of ~he
perorator high speed shuttle mechanism adapted for use in
an amateur motion picture camera;
Figure 14 is a schematic v~ew of a modifica~ion of
the perforator high speed shuttle mechanism adapted for use in
an amateur projector.
Flgure 15 is a schematic view of a modifica~io~ of
the perforator thread~up shuttle mechanism adapted for use ln
an ~mateur ca~era.
Figure 16 is a schema~ic view of a modiflcation of
the perforator thread-up shuttle mechanism adapted or use in
: ~n mateur projector.
: ~igure 17 ls a schematic showing of another modifi-
20 cati~n o the per~orator thread-up shuttle mechanism adapted
.or use in an amateur camera~
Flgure 18 ls a schematlc showing of a modlica~ion of
the embodiment of the perforator thread-up shuttle mechanlsm
shown in Figure 17 which is adapted or use in an amateur
mothon picture projector.
Generally the present ilm perforator compr~ses a
perforating station at which a reciprocating punch acts on the
,
7- :
,, :
film while it is sta~ionary. The 11m s~ri.p is intermittently
~dvanced t~ and throu~h the per~orating station by a shuttle
mechanism including one or more claws which engage the
perforation(s) made at the perforating station and advance
the film one frame at a tlme. Associated with the punch, and
located between it and ehe point where the shu~tle engages the
film3 is a pilot pin which engages a previously made perforation
whlle the film is stationary and just before the punch engages
the film to perforate it. This pilot pin is shaped ~o accurately
10 fit the perforation and is spaced from the punch a distance
which is equal to the pitch spacing desired between the
perforations. The purpose of the pilo~ is to accurately
posi~lon the film just before the punch makes a successive
perforation so as to be assured the pitch between su~cessive
perforations ls exactly the same. It does this by correcting
~ny inaccuracy there might possibly be in the pullodown stroke
` ~ the shuttle mechanism or for any movement o the film which
- migh~ occur as or af~er the shuttle claw leaves film peror~
at~ons. The parts of the perforator are so designed and
mounted that it is adaptable to diferent film formats and
w~dths.
So that a new film can be threaded into the perforator
~ithout having the leading end temporarily spliced to the trailing
encl of an expiring film~ cr without ha~ing to provide the leading
end of a new film wQth perforations, the perforator is provided
w~th ~n automatic threading mechanism. This comprises an inter-
~it~ent film feeding mechanism which operates in synchronism
8 -
,
.
3~5~
with the punch ~nd shuttle feed and ~rictionally engages the film
to feed it in~ermittently one frame at a time to and thr~ugh t~e
punch mechanism to the shuttle mechanism. This automatic thread-
ing mechanism is selec~ively operated at a speed below the top
speed of the perforator and cannot be ac~i~ated unless the perfo-
- ra~or has been disconnected from the high speed power source for
~ time greater than a preselected ~ime delay to insure that the
machine has stopped. The automatic ~hreading mechanism is
com~ined with ~he perforator so tha~ after the shu~tle mechanism
has assumed control of the film leaving the punching sta~ion ~he
automatic threading mechanism will be automatically disengaged
and tlhe perorator can be brought up to top speed.
It is pointed out that the key element in this
perorator design is the shuttling mechanism which moves
the film intermittently at a rate as high as 12,000 perorations
per minute without damage, and which operates with accuracy and
low maintenance over a long span of life. Since the acceleration
- of a reciproca~ing mechanism increases as the square of the speed
and linearly with the distance traveled, it has been found that
20 the ahuttle mechanism for feeding a 35mm film is subjected to
~ccelerations which are over seven (7) times those ~or a shuttle
for a 16mm film runnlng at 3a580 rpm. Because of ~he bigh
accelerations involved3 it was ~ound impossible to use conven- :
tlonal cam and ollower designs for shuttle mechanisms operating
at speeds as hlgh as 12,000 perforatlons per minute because slid-
lng fol~ower members are subjec~ to severe w~ar, lubrica~ion,
and hea~ ge~erati-n problems The shuttle mechanism designed
1048
~or this perf~rator utilizes very light aluminum parts which
are symetrically Loaded. A rocker cam and flat cam arrangement
wb~ch is used to control the claw tip to the desired path of
travel incurs very little sl;ppage (relative slidlng mo~ement
~ the cooperating surface of the cams) and, therefore~ has a
long life even though fabricated of lightweight materials. The
fla~ cam is mounted in an aluminum carriage which extends length-
wise of the film path. The carriage is supported by two groups
of vertical suspension springs whioh are tuned to the operating
speed of the carriage. The shut~le arm is driven through ball
bearings by an eccentric at one endO The rocker cam is attached
to the shuttle arm and contacts the flat cam. A coupling spring
: i ..
, transmits horizontal motion ~rom the shuttle arm to the carriage ~ ;
member in such a manner as to produce negligible slippage be-
tween the cams, and also maintains proper contac~ pressure be-
.. .
~ween the cams. It has been found that the design of this shuttle
mechanism for ~uper 8 film (pitch 0.16671') is al50 satisfactory
for 35mm film (pïtch 0.187"), and for 8mm film (pitch 0~150").
The onLy change re~uired is the eccentricity o~ the drive and
the shape and size of the claw tooth member(s) of the shuttle.
~eferring now to the drawings, and initially to
~lgures L, 2, 3, and 7 thereo~, it will be seen that a perfora-
ting device embodying the present invention has a base plate
23 attached to base block 20 by any suitable means (not shown).
The side plate 25 (shown in Figure 7) and bac~ side plate 27 (see
Figure 7) are attached to base plate 23 by any suitable means
~not shown)~ Sprlng holder 32 is attached to base plate 23 by
- 10
. '
:........................................... .
~ 8
any suitable means, (not sho~) Two flat paralLel sprin~s
35 are ~ttached at one elld to spring holder 32 by clamping
strlps 37 and bolts 39. Springs 35 are attached at the
other end to punch support 45 by clamping strips 41 and
bolts 43. The purpose of clamping strips 37 and 41 is to
rigidly ~old the ends of springs 35 so that the desired bend~
ing behavior of springs 35 is obtained. Flat spring 46 is
att~ched to spring holder 32 by clamping strip 47 and boLts
4g. Punch truss 59 is attached at one end ~o punch support
45 by bolts 53 which pass through flat spring 46 and thread
into clamping strip 51. Punch holder 57 is attached to punch
~upport 45 by bolts 53 which pass through fla~ spring 46 and
thread lnto clamping strip 51. The purpose of clamping strips
47 and 51 is to rigidly hold the ends of 1at spring 46 so
that ~he desired bending behavior of fla~ spring 46 is obtained. ``
Punch ~upport 45 is free ~o piv~t about the inter-
section of the plane of flat parallel springs 35 and of the
plane of the flat spring 46. The pivot axis thus formed by
the intersection o the flat parallel springs 35 and flat
spring 46 may be considered as fixed in space the same as a
rigidly mounted hinge.
This type o spring hinge differs from a conventional
I hinge in three important respects. First, there is no play
i i~ the spring hinge and no play can develop as a result of
wear or loss of oil film; second, no lubrication is required,
and~ therefore, maintenance is reduced and the danger of oil
ge~ting on the film and in helping to attract dirt accumula-
- tion is minimized; and, third? the springs do not create a
,
~a3s~0~
~riction ~orque and do produce a restorin~ torque proportional :
to the angle of displacement from the neutral position ~r
zero stress position. In actual practice~ this ~estoring
t~rque has no detrimental effects but is actually used to
tune assemblies to supply sinusoidal acceleration torque at
the ~perating speed of che perfora~or~ The length and thick-
ness of flat parallel springs 35 and Elat spring 46 must be
chosen to keep the operating stress well below the endurance
limit o the spring material. ~-
One end of connecting spring 61 is attached ta the ~.
other end of punch truss 59 by bolts 63. The other end of
eonnecting spring 61 is attached to punch driver arm 67 by ; :`
bolts 63~o Punch driver arm 67 is rotatably a~tached to
ecccntric drive shaft 69 which is suitably eccentrically
~ournaled to rotate and is supported by front bearing plate 71
.~ `I
(as shown in Figure 2) and rear bearing plate 73 ~see Figure 2)
by ~.bearing assembly which will be described in more detail
wlth reference to Figure 2. Bolts 75 (as shown in Figure 2
~ttach front bearing plate 71 to base block 20, and bolts 76
(see Figure 2) attach rear bearing plate 73 to base block 20.
Let us now consider Figure 2, whlch shows the main
l drive shaf~ assembly in detailO This assembly is discussed in
:l considerable detail in order to show how the film perforator
:~ can be readily adapted to perforate different film formats and
~i .
film w~dths~ The configuration in Figure 2 is that necessary
to perforate 35mm film. Ma.in ball bearing 84 is fitted on
- 12 -
: , .
.. . ..
.
eecentric drive shaft 69 and constrained axially at the outer
race by end cap 80 and dirt seal plate 88 which clamps against
bearing plate 73 by ~ction Df bolts 82. Flexible c~upling 90
~s attached to eccentric drive s~aft 69 by screw 92. The
purpose of flexible coupling 90 is to allow for slight mis-
alignment between eccentric drive sha~t 69 and the motGr drive
shaft ~not shown~. The screw 92 clamps ~he right end portion
of the coupling against the inner race of main bearing 84 and
spacer 86 thus constraining the eccentric shaft in the axial
direction. Split ball bearing 94 is fitted on an eccentric
portion 95 of the drive shaft 69 and pressed into punch driver
arm 67. Oil shields 96 and 98 are pressed into punch driver
~rm 67~ ~ack shuttle spacer 100 is then slid ~nt~ eccentric
; drivs shaft 69 and constrained axially in one direction by
8plit ball bearing 94 and axially in the ot~er direction by split
ball bearing 104~ Shuttle arm 102 is journaled to ro~ate re-
lat~ve to eccentric portion 99 of the drive shaft 69 between
~pacers 100 and 112 through a bearing assembly that is comprised
. o~ ~wo split ball bearings 104, two oil shields 1~6, and spacers
108 and 110. Front shuttle spacer 112 is fitted on eccentric
drive shaft 69 and constrained axially in one direction by
~plit ball bearing 104 and axially in the o~her direction by
~plit ball bearing 119. Split ball bearing 119 i~ ~itted onto
counterweight sleeve 114 which is slid onto eccentric drive shaft
690 Main ball bearing 120 fits into end spacer 116 and is also
itted over c~unterweight sleeve 114. End spacer 116 is then
.
~ - ,'
.
~s~
rigidly attached to front bearing plate 71 by screws 118. Mut 122
threads onto eccentric drlve shat 69, and is used to tighten the
entire shaft assembly together. End cap 124 is rigidly attached
to end spacer 116 by screws 125 and the outer race of bearing 120
s clamped in the process.
The eccentricity of eccentric drive shaft 69 at the
shuttle bearings 104 'or the 35~m film application is a little
more than 1/2 of the pitch of 35mm ilm whioh pltch is .0935 in.
The small excess of ~he order of 0.007 in. allows for bearing
clearance and deflection and insu~s easy entrance o the claw with-
out scuffing agalnst the perforation edge. If film having a
different pitch is desired to be perforated, the only changes that
need ~o be made in the main drive shat assembly as shown in Figure
2 ls that eccentric drive shaft 69 must be replaced by one having
the desired eccentricity at the bearings 94 and 104, count~rweight sleeve
114 must be replaced by one baving the proper geometry, and the
counterweight portion 114 of eccentric shaft 69 is also suitably
altered. Back shuttle spacer 100 must also be suitably altered.
If it is desired to perforate Super 8 film, the eccentricity of
~0 eccentric drive ahaft 69 at bearirlg3 94 and 104 mu91: be 0. 0834 Lrl. plu9
overage allowance, and for regular 8mm film the eccentricity must
be .075 in. plus allowance~ Of course~ the size and shape of the
claw tooth members of the shuttle and the punch and die arrange-
ment must also be appropriately changed ln order to perforate film
of different widths and different formats.
Spacer sleeve 126 is slid over lower shat 127 ~as shown
in Figure 3~ which is rigidly attached to front bearlng plate 71
- 14 -
,
and rear bearing plate 73 by bolts (not shown). The purpose
of this arrangement is to insure that proper spacing is maintained
between bearing plates ~1 and 73~
As sho~m in Fi.gure 3, two punches 130 one ~or each margin
of the ~ilm are held in punch holder 57 by set screws 13~, which
are shown in more detail in Figure 4. Two pilot pins 134, one f~r
the perforations at each margin of the fîlm, are held in punch
holder 57 by set screws 136 (see Figure 4). Punch holder 57 is
~: ~tt~ched t~ punch truss 59 by bolts 137 and 53. Top plate 138 is
attached to front bearing plate 71 and rear bearing plate 73 by
any suitable means (not shown). Three parallel leaf springs 140
. ~pp~opriately spaced by washers 142 and cons~rained by clamping
spa~er 144 are attached to ~op pla~e 138 by bolts 146. The other
end of parallel springs 140 are appropriately spaced by washers
150 and constrained by clamping spacer 152 and attached to flat
ca~ carriage 148 by bolts 154~ The purpose of clamping spacer
144 is to rigidly attach flat parallel springs 140 to top
plate 138 and to insure ~he desired bending behavior of parallel
~prings 140~ The purpose of clamping spacer 152 is to rigidly
attach parallel springs 140 t~ flat cam carriage 14B and to insure
~ proper bending behavior of parallel springs 140.
: The other end of flat cam carriage 148 is at~ached by
b~lts 162 to one end of three parallel springs 156 whose ends are
appropriately spaced by ~ashers 164 and c~nstrained by clamping
spacer 166 and attached to top plate 138 by bolts 168. The pur~
pose of clamping spacer 160 is to rigidly attach parallel springs
156 to flat cam carriage 148 and to insure the proper bending be
havior of flat parallel springs 156. The purpose of clamping
spacer 166 is tu rigidly attach parallel springs 156 to
top plate L38 and to insure the proper bending behavior of
parallel springs 156. Flat cam 149 is rigidly cemented into
1at cam carr1age 148,
Rocker cam 180 is attached to shu~tle arm 102 by screws
182. Shuttle bracket 185 is attached to shu~tle arm 102 by
bolts 186. The film is intermittently advanc~d through the per-
forating station by two shuttle elaws or tee~h 184 on shuttle
10 bracket 185 of the shuttle mechanisms, each of which engages
8 per~oration in the film previously made by a respective
rec~procal punch 130 which acts on the film in the perforating
station while the ilm is s~ationary.
To insure hi8h accuracy in the pitch of the perorations,
pilot pins 134 are associated with the punches 130 and move there-
w~thA Pilot pins 134 are located between punches 130 and shuttle
teeth 184 by a distance equal to one perforation pitch from the
punch and are arranged to enter the perforations previously made
by the punches just before the punches engage ~he film so as
~0 to accurately adjust the film advance before succeeding perora-
tions are made. Pilot pins 134 are formed to accurately fit
previously made perforations and the~r purpose is to correct or
any slight inaccuracy in film ~dvance which might be made by the
~huttle mechanism~
The shuttle mechanism des~gnated f~r this perforator
utillzes very light~ight aluminum parts which are symmetrically
loaded. The arrangement of rocker cam 180, flat cam 149, and
- 16 ~
,
. .. . . .
~ ~3S~
fl~t cam carriage 148 which are used to control the motion o:
shuttle teeth 184 to the des~red path of travel, incurs ~ery
l~ttle slippage between the cams 180 and 149, and~ therefore,
has a long life even though fabricated of lightweight material.
Flat cam carriage 148 extends lengthwise of the film path and is
~upported by two groups ~f suspension springs 140 and 156, which
are tuned ~ the opera~ing speed of flat cam carriage 1480 Shut~le
~rm 102 is driven through ball bearings 104 by eccentric shaft
69. Rocker cam 180 is integral with or attached to shuttle arm
102 and contacts flat cam 149. Rocker cam 180 has an arcuate
~urface which rides on fla~ cam 149, and gives the required motion
of shuttle teeth 184. U-shaped coupling spring 170 (see Figure
4~ transmits motion from shu~tle arm 102 to flat cam carriage
148 in such a manner as to produce negligible slippage between
the cams 180 and 149, and also maintain proper contac~ pressure
b~tween the cams at all speeds of operation o~ ~he shuttle
mechani sm~
As mentioned above, springs 140 and 156 are tuned to
the operating speed for the mass of 1at cam carriage 148 and all
parts associated with its connection to the free ends of the flat
parallel springs 140 and 156. Flat cam carriage 148 slants at
su~stantially 20 to the film path to make the acceleration
pattern of the drive system ~or the flat cam carriage 148 approach
simple harmonic that can be, and is 3 tuned by the ~lat parallel
springs 140 and 156.
The end of U-shaped eoupling sprLng 170 that is attached
~ 17 ~
~' . ' .
to shuttle ann 102 by bolts 172 is tilted slightly in a counter-
clockwise direction relative to the remainder of the sprlng
for maintainiTtg contact pressure between the cams at all speeds
of operation.
The left end of punch truss 59 is operatively connected
to eccentric drive shaft 69 ~hrough punch driver arm 67 and
cDnnec~ing spring 61. The o~her end of punch truss 59 is
pivotally mounted by crossed springs 46 and 35, whlch causes
punches 130 to reciprocate across the film path to perfora~e
the film.
Pilot pins 134 are slightly longer than punches 130 ~o
enter previously formed perforations just as shuttle teeth
184 are leaving perforations and before punches 130 engage the
: film to insure the film being advanced the desired pltch
; before a pair of successive perforations is made therein.
The film is fed in~o the perforator through a guideway
~^ ~omprising a film apron 188 which is attached to base plate
23 by suitable means (not shown~ and a film apron oover 190
attached to film apron 188 by suitable means (not shown).
The ilm leaving the perforating station passes through a
guideway comprising a film apron 192 at~ached to bas plate
23 by suitable means (not shown~ and a film apron cover 194
~ttached to takeup side film apron 192 by suitable means ~not
~hown) .
Front die holder 196 (as shown in ~igure 7) and rear
die holder lg8 (see Figure 7~ are attaohed to base plate 23 by
~ultable means (not shown). Punch side stripper 202 is sup~
~ 8
ported from the bottom by die holders 196 and 198 (see Fic~ure 7)
and constrained in the upwards direction by str~pper clamp 204
~as shown in Figure 4) which is attached to front side plate 25
by screw 205, and by stripper clamp 206 (see Figure 4) which is
~ttached to back side plate 27 by screw 207.
Take~up side stripper 200 is supported ~rom the bottom
by die holders 196 and 198 (see Figure 7~ and constrained in
~he upwards direction by stripper clamp 208 (as shown in Figure
4~ which is a~tached to front side plate.25 by bolt 209 (see
Figure 4) and stripper clamp 210 (see Figure 4~ which is attached
; to back side plate 27 by bolt 211 (see Figure 4). Spacer sleeve
; 213 (see Figure 3) is attached to front bearing plate 71 (not
shown) and rear bearing plate 73 (not shown) by suitable means
(not shown). The purpose of spacer sleeve 213 i.s to insure the
proper spacing between bearing plates 71 and 73.
A~ shown in Fi~ure 4, pilot pin spacer 220 ls loosely
held betw~en pilot pins 134 and punches 130. Pilot pin wedges ;- .
: 2~2 and 224 are forced into grooves in pilot pin spacer 220 to
obtain fine adjustment o~ the lateral position o pilot pin
spacer 220.
Figure 5 shows a schematic of the high speed shuttle
~howing the relationship betw~en rocker cam 180, flat cam 149,
path of point P on shuttle teeth 184, the film plane, and
eccentric drive shaft 69, T~e eccentricity of drive shaft 69
~111 be designated by e. As eccentric drive shaft 69 rotates
in the direction shown, rocker cam 180 rides on flat cam 149,
and shuttle arm 102 and shuttle teeth 184 move in such a way as
' 19
~5~3~
to cause point P on shuttle teeth 184 to move in the path
~hown schematically by the d~tted line in Figure 5. It should
be noted that the total stroke length during one s~roke is
equal to twice the eccentricity o~ eccentric drive shaft 69
or 2e.
Slnce flat cam 149 is coupled to shuttle arm 102 by
U-shaped coupling spring 170 (as shown in Figure 4~ and is
~uspended by flat parallel springs 140 and 156 3 flat cam 149
necessarily oscillates back and forth paralLel to itself and
moves up and down parallel to itself. This motion in co~lbin-
: ation with the rocking motion of the arcuate surface of rocker
cam 180 gives negligible slippage between cams and the desired
motion of shuttle teeth 184.
As shown in Figure 5, at the starting point tangle
= 0), the point 2 on rocker cam 180 is in contact with flat
~;- cam 149, and the reference point P on t~e shuttle teeth 184
is on the axis (horLzontal line 0-0) with the value of x= e.
The drive point 3 rotates about the fixed point 7 at an
eccentricity of e. To some extent the choices of dimensions
~nd shape of rocker cam 180 are arbitrary, but they are largely
dictated by consideration o~ the desired film pitch, the amoun~
f in~and-out travel required to clear the stripper, the
~traightness o~ the path a~ter full engagement, and the s~are~-
ness oL the corners without incurring excessive upward accelera-
t~ons. ~nîle the cam L49 is described above as having a planar
sur~ace for cooperation with the convex surface of the rocker
cam 180, it is to be understood that the surface of cam 149
; 20 ~
. .-- _ . . .
~L~3S~
need not be planar9 it may be concave or convex. The require~
ment of the surfaces of the cams 180 and 149 is that they
should be so formed that as the sha~t 69 rota~es, the value
of "Y" should vary by a minimal amount while the claw 184
~s disposed in a perforation, ~hat is, during a pull~down stroke
and that the claw should enter and leave a perforation in
directions substantially perpendicular to the film plane~
. .
Figure 6 shows plots of the path o Point P of the
shuttle teeth 184 for 35mm, Super 8, and regular 8 film.
The degree values indicated in Figure 6 correspond to eccen~ric
drive shat ~9 angle ~ as shown in Figure 5. For 35mm film,
..
~he eccentricity e of the eccentric drive shaft 69 is 94.2
mils. For Super 8 film, the eccentricity of e~centric drive
~haft 69 is 84.0 mils. For regular 8mm film, the eccentricity
f eccentric drive shaft 69 is 75.6 mils. These values are
slightly more than one half film pitch to allow for bearing
cle~rance and to provide free entry o teeth 184.
In urder to eliminate the necessity of temporarily
; splicing the end o~ a new fi1m to the end of an expiring film,
or providing the end of a new web with one or more perforations
to insure its being handled by the perforator, this perforator
incorporates an automatic threading mechanism which will thread
unperfor~ted fil.m to and through the punch mechanism and to the
~huttle mechanism. This automatic threading mechanism inter~
mittently advances the film to the punch and shuttle mechanisms
by intermittently frictionally engaging the film and ad-
~ancing i~ in increments substantially equal tD the perforation
21 -
-- - _.. .
pi~ch and the a~vancing stroke o the shuttle mechanism.
In order to investigate this automatic threading
mechanism ln more detail, let us return our consideration to
F~gures l, 3 and 7~ Shaft 228 is rotatably journaled in bear-
ings 230 (as sho~ in Figure 7) whioh are supported by base
block 20. Arm 232 is rigldly at~ached to shaft 228 by bolt 234
~as shown in Figure l). Arm 238 ls attached to arm 232 by
bearing stud 236 and a bearing assembly, which will be de~
scribed ln more detail with reference ~o Figure 8. Engagement
arm ~r shuttle arm 240 is at~ached ~o arm 238 by shaft 242 and
a bearing assembly which will be discussed in more detail be-
low. One end of engagement arm 240 rides on eccentric split
ball bearing 119 (as shown in Figure 2) in an engaged position,
One end of spring 246 is hooked onto spring anchor pin 244
which is attached to arm 232. The other end of spring 246
hooks around pin 248 which is rigidly attached to front side
plate 25. The purpose of spring 246 is ~o urge arm 232 and
shaft 228 in a clockwise direction. One end of spring 252
hooks around pin 250 which is rigidly attached to ~r~l 238. The
other end of spring 252 is hooked around pln 254 which is rigid-
ly attached to engagement shu~tle arm 2~0. .The purpose of
$pring 252 is to urge the left end of engagement arm 240 in
c~unter-clockwise direction in relati~n to arm 238.
Stop 256 is attached to front side plate 25 by bolts
258 ~as sho~ in Figure 7). The purpose of stop ~56 is to
l~m~t the counter-clockwise travel of the right-hand end
~f engagemen~ arm 240 when the thread up shuttle is in the
- 22 - ~
~5~
disengag~d position as shown in Figure 1~ Stop pins 262
~nd 266 are rigidly attached to base block 20 to limi~ the
travel of arm 232. To the other end of shaf~ 228 is attached
bracket 268 ~as shown in Figure 3). Flat spring 270 (see
Figure 3) is attached to bracket 268 by screw 272 (see Figure 3).
In order ~Q see how the thread-up shuttle mechanism
ls placed in the operative position, le~ us ~urn our attention
to Figures 1 a~d 3~ in which the ~hread-up shuttle is presently
~hown in the disengaged or inoperative position, In order to
pLace it in the operative position, an electrically energized
solenoid 302 (see Figure 12) is energized which ur~es the top
of flat spring 270 (as shown in Figure 3) in the counter-
clockwise directionO The purpose of flat spring 270 is to
aLlow for over travel of solenoid 302. The counter~clockwise
moti~n of flat spring 270 rotates bracket 268 in the counter- :
clockwise directlon. S~nce bracket 268 is connected to shaft
228 by screw 272, shaft 228 also rotates in the counter-clock-
wi~e direction~ Arm 232 will rotate in the counter-clockwise
direction untiL ~et screw 264 is limited in its travel by
~top pin 266. Arm 240 will now be lowered away from stop 256
thus allowing spring 252 to urge the left end of engagement
arm 240 into contact with ball bearing 119 (as shown in
Figure 2). As the left end o~ engagement arm 240 rides on
eccentric bearing 119 the right end of engagement arm 240 will
move ~n a path such that it frictionally grips and advances the
web to and past the punching position in increments substan-
tially equal tc) one perforation pitch. The frictional means
by which the filrn is gripped by the right end of engagement
arm 240 will be discussed in more de~ail below with reerence
t~ Figure 9.
In order to disengage the thread-up shuttle assembly,
the electrical solenoid 302 when de energized will cease to
press on flat spring 270. Spring 246 will then urge arm 232 in
a clockwise direction causing shaft 242 to move in a direction
such that the film is disengaged, the arm 240 in so moving
~triking stop 256 causing the left end of engagement arm 240
to move outof engagement with eccentric ball bearing 119
: (as sho~ in Figure 2).
As shown in Figure 8, the lower end of arm 238 is
ro~atably journaled to arm 232 by a bearing assembly com-
prising bearing stud 236 suitably held by two balL bearings
; 275 and spacers 277. Shaft 242 is journaled to rotate in the
upper end of arm 238 through a bearing assembly comprising two
ball bearings 279 and spacer 281~ Engagement arm 240 is ~ress
~itted onto shaft 242.
F~gure 9 sh~ws that stop arm 2~3 and one end o flat
sprin~s 285 are attached to engagement arm 240 by bolts 287.
Shuttle pad 289 and stop arm 291 are attached to the other end
of spr~ngs 285 by bolts 293. The bottom surface of shut~le
pad 289 is covered with a high friction ma~erial; such as
:~! polyurethane, to furthPr enhance the film driving action.
Four ball bearings 295 and ~wo spacers 297 are at~ached t~
shaft 299 which is rigidly attached to apron member 188. As
. 24 ~
: .
sho~ in Fi~ure 9 flat springs 285 in connectlon wlth stop
arms 283 and 291 comprises a resilient breakaway connecti~n
causing shuttle pad 289 to move with the shuttle at all times
except after the shu~tle pad 289 moves into eng~gement with
the face of the film, at which time engagement arm 240 moves
relative to shuttle pad 289 and stresses springs 285 whi.ch
resiliently urge shuttle pad 289 into engagement with the film.
As ~he lef~ end of engagement arm 240 rides on eccentric
bearing ll9 (as shown in Fi~ure 2) the right end of engagement
arm 240 causes shuttle pad 289 to move ~hrough the open top
o~ the film guideway and lnto press;ng engagement with the
face of the ~ilm at the beginning of and during the film ad-
vancing stroke ~ the shuttle to advance the film~ At the
end of the film advancing stroke the right end of engagement
arm 240 moves so as to ~tract shuttle pad 289 from engage-
ment with the film and hold it retracted during the return
~troke.
In order to determine the correct relationship be-
tw~en the locations of eccentric drive shaf t 69, bearing stud
2369 shaft 242, and ball bearings 295 let US look at a
scher~tic of the geometry as shown in Figure 13., Figure ll
- shows schematically the side ~iew of the zone of the ~ilm path
~o be occupied by the thread~up shuttle, The fiLm path with
free turning ball bearings 295 just below the film surface
~nd the location of eccentric drive shaft 69 are known. We
; must establish the location of shaft 242 whi~h swings about the
bearing stud 236 and the eccentricity e at the driver required
to obtain the desired film advance T~
~ 25 - :
5~
The right cnd of engagement arm 240; shown ln
Figure 11 by dotted line, is fitted wlth the shu~tle pad 289
(see also Figure 9) which is spring loaded against a stop and r
so adjusted that it pinches the film against ball bearings .
295 during approxi~ately one-half of the eccentric rotation
and lifts away frQm the film for the remainder of ~he time
when the thread-up shuttle mechanism ls in its operative con~
ditlon. It is also understood t~ t the left end o engagemen~ -
arm 240 (as shown in Figure 1) engages ~he split ball bearing
119 (as sho~.~n in Figure 2) during the time requ~red for thread-
up and then is disengaged and does not contact the eccentric
bearing 119 or the film during the remainder of perforatin~ the
roll of film.
It is necessary that the motion of shuttle pad 289
be essentially perpendicular to the plane of the film at the
instant of making contact and at the instant of leaving the
11m. This prvduces the most accurate control of the film
motion as no longitudinal motion takes place during the short
in~erval of time when pinching pressure is being established
cr released. We therefore locate shaft 242 in the plane of
the film as extended beyond the location o~ ball bearings 295
~as shown in Figure 11). The length of the arm from point A on
` shuttle pad 289 to sha:t 242 is of secondary importance but it
. has been found well to make the distance X from the center of
shaft 242 to point A a little shorter than the distance Y
between the center of eccentric drive shaft 69 and shaft 242.
. - 2~ ~
~5~
This produces a motion a t the right end of engagement arn~ 240
which is ess~ntially elliptical in shape, the minor axis being
perpendicular to the film.
Now draw the line from the center o~ rotation of
bearings 295 which is perpendicular ~o the film and also draw
the line from the center of rotation of eccentric shaft 69
which is perpendicular to the line drawn from the center of
~hat 242 to the center of eccentric drive shaf~ 69. The
int~rsection of these lines deines the point I, It can be
s~n that the two extreme positions- of the travel of engage-
ment arm 240 can be anaLyzed as if it had physically been con
strained to rotate about point I as an axis. The center of
the eccentric bearing 119 (as shown in Figure 3) on the eccen-
tric shaft 69, the center of shaft 242, and the point A at
their extreme positions all move a distance corresponding
to the anglea measured about axis I. It ~ollows directly
that the eccentric travel 2e must be equal to the desired
film trave~ T multiplied by the ratio of the lengths of the
line from the center o eccentric shaft 69 to point I divided
X~ by the distance from point ~ to point I. It also ollows that
the ~dvance angle is 180+a . The phase relation between
eccentric position and film travel is also readily understood
fro~ this construction.
The moving pivot, shaft 242, can be constrained by
an arm pivoted at I, however lt is usually not practical to
~perate at this grea~ a distance. The a;::tion is entirely
~7 -
. . .
~L~5~
satisfactory if another pivot poi.rat such as point 23~ is
chosen so l~ng as the point 23~ falls on the line between
the cen~er oE shaft 242 at its mid stroke and point I.
Strictly speaking the center of shaft 242 does
not rer~in in the plane o the film because the line be~ween
the center of shaft 242 and the center of bearing stud 236
i~ not perpendicular to the film plane at ball bearings 295.
However the plane of the shuttle pad 289 slightly modifies the
ilm path and does the clamping or lifting of~ strictly ;n a
~0 direction perpendicular to i~sel~.
The automatic threading mechanism described above is
combined with the perforator so that it can be selectively en-
gaged and will automatically disengage when the end o~ a new
f~lm reaches a point in the ilm path following the shuttle
mechanism and, after the shuttle teeth 184 have control of the
film. To understand this operation better, attention îs called
t~ Figure 12, which shows the thread-up shuttle electrical con-
trol diagram. There is no ilm in the perforator when it is
desired to begin the thread-up sequence. Thread-up button 300
is pressed and then released. Time delay relay TDR is energized,
which closes its normally open switch T~R-l~ Solenoid 302 is
energized and pushes against spring 270 to rotate shaft 228
counter-clockwise thus causing engagement arm 240 to come into
engagemen~ with ball bearing 119 and be driven by eccentric
: dri~e shaft 69, hence pUttiIlg the thread-up mechanism in ~he en-
gaged or operative condition as described in detail aboveO Re
-2
:
:, ,
- - .
.
lay Rl simultaneously is energized wh~ch closes its normally
open switch Rl~l. As normally opened switch Rl~l is cl~sed,
motor ~I driving eccentric shaft 69 begins running at 1800 rpm.
The end of a roll of unperforated film is then inserted into
the channel bet~en the supply side film apron 188 (as shown
in Figure 3) and supply side film apron cover 190 (as shown
in Figure-3). The thread-up shuttle mechanîsm then advances
the film in the manner described in detail above until normally
c~osed switch 307 in the film path defined by the take-up side
1~ film apro~ 192 and take-up film apron cover 194 (as shown in
Figure 3) is reached by the filmO When the film reaches n~rmal-
ly closed switch 307 it opens it. This causes solenoid 302
- to be~ome de-energized thus allowing engagement arm 240 (as
shown in Figure 2~ to move out of contact with ball bearin~ 119
(as shown in Figure 2) hence putting the thread-up shuttle
: mechanisrn in the inoperative condition as described in detail
.. . .
~bove. Time delay relay TDR then starts a time delay of approx- -
imately 10 seconds~ After the 10 seconds has elapsed~ time delay
rel&y TDR is de-energized which in turn opens its switch TDR-l
which de-energizes relay Rl causing its switch to revert to the
position sho~, causing motor M to stop. The thread-up opera-
ti~n is now c~mplete.
After the threading operation is complete and the high-
speed shuttle mechanisrn is capable of controlling the film, the
machlne is put in high speed opera~ion in the following manner.
Again referring to Figure 12, high speed s~art button 310 is
~ILO15~
pressed ar.d released. Relay R2 is energized which malces
its normally open switch R2-1. The closing of switch R2 1
turns on 400 ~Iz supply 313 which powers motor 306 at 12~000
rpm through normally closed swi~ch Rl-l. The fllm is then
perforated in the manner described in detail above~ ~ocated
in the film path adjacent to swltch 307 there is a ~econd switch
.~14, normally open, which is closed when film is ln this posi-
~ion of the film path but which normally opens when there is
no fil~ in this portion of the film path. Since ~llm has
already been threaded through the perfora~or past thls switch
314 it is closed which allows the motor M ~o operate at high
speed. I~en the trailing end of the film passes switch 314 it
returns to it~ normally open s~ate to de-energize relay R2
and this in turn allows its switch R2 1 to return to the normal-
ly open condition shown and cut of the 400 Hz supply 313 where-
upon the motor stops. The perforation is then complete~
In order to see how the film is guided to and through
the perforating station, let us look at Figure 10. As shown
ln detail in Figure 10, edge guide buttons 325 are attached
to flat sprin~ 327 which is attached at i~s center in spaced
relat~on to the front side plate 2S by means of a clamp screw
339 and by spacer 343~ Set screws 329 which are threaded into
ront side plate 25 press against spring 327 thus controlling
its position. Edge guide buttons 331 are attached to spring
333 which is attached at its center in spaced relation to the
back side plate 27 by means of the clamp screw 341 and spacer
3b,5. Spring 333 is maintained in position by compression
- 30 -
springs 335 w~ich are pressed against by set scre~s 337
threaded into baclc side plate 27. The purpose o~ edge guide
buttons 325 and 331 and the spring arrangement is to control
the lateral position of the film as i~ goes ~hrough the per-
f~rating sequence. Another advantage of the gate configura-
; tion as shown in Figure 10 is that front die holder 196 and
rear die holder 198 are cu-rved such that they define a curved
pa~h for the film approaching and leaving the perforating
p~ition so as to maintain the film in a bowed condition ~or
overcoming any transverse cllrl the film might possess at the
time it is perforated.
Also, as shown in Figure lO, die 349 and pilot die 347
~re pressed into die holders 196 and 198. When the machine is
; perforating, punches 130 fit with very small clearance into ;~
dies 349 and pilot pins 134 fit loosely into pilot dies 347.
While an embodiment of the perforator has been described in
which the elongated web to be perforated is a photographic
~otion picture film, it will be unders~ood that other web
materials, e.g., paper, may be perforated by apparatus in accord-
2~ ance wlth the present invention and such perforated webs o~
paper or other material may be advanced by a claw device in
accordance with the present invention. Also, while the con-
vex cam has been described as being associated with the shuttle
. j , .
arm 102 and the flat cam as being mounted by the spring members
: 140~ 156, it is to be understood that the convex cam could be
mounted on the spring members and the flat cam could be associa
ted with the shuttle arm.
. - 31 -
.. . . . .
Reference is now made to Figure 13 which i~ lustrates
a simpli~ied embodiment of my novel shuttle means which is
particularly adapted for use in motion picture cameras where
the intermittent pull-do~ speeds required are relatlvely
slow. Since motion picture cameras, particularly those
intended for amateur use, do not require such long design life,
probably less than 100 hours as compared to 16,000 hours for
the per~orator, i~ is no~ necessary to elimlna~e slip between
the rocker and fla~ cams 180 a~d 149 respectively. In fact3
the ~lat cam need not be mounted in a moveable carriage or
driven by an eccentric through the U-shaped coupling spring 170,
but may be stationary with attendent simplicity and cost reduc-
tion. Also simple bearings will suffice in place of the ball
bearings. Referring to Figure 13, we see that drive shaft
3S5 is sui~ably journaled in bearing~ (not sho~) which are
m~unted in frame members (not shol~n3~ Drive shaft 355 receives
its pow~r input from a motor ~not sho~) in the direction
sh~wn. Pin 357 is rigidly attached to drive shaft 355. ~d-
~ance arm 359 is suitably journaled to pin 357 by a bearing
assembly (not shown). Advance arm 359 contains an arcuate cam
surface 180 which rides against stationary flat cam 149~,
which is rigidly attached to fr~me member 364 by suitable means
(not shown), ~he resulting path of point P on the shuttle
to~th portion 184 of advance arm 359 is shown by the dashed line
in Figure 13. The shuttle tooth portion o advanc~ arm 359
suitabLy engages the perforations in the film so as to ad-
~ance it the desired amount. It can be appreciated that ~he
: ~ - 32
.
~ 5~
cams and ecccn~ric drive can be placed to one side of the
film with onl~ shuttle tooth 184 being o~-set to align with
one of the rows of perforations in the film. In such a case
the flat cam surface could be in ~he szme plane as that of
the film.
The stationary flat cam scheme sho~ in Figure 13
is satisfactory for camera use since advance will ~ake place
during approximately 1/2 of one rotation of drive shaft 355.
For a projector it ~s necessary to interrupt the ligh~ be~m
three or more times for each frame advance tu avoid flicker
problems. As a result the shut~le when designed for use
in ~ motion picture projector must advance the film in about
6 or less of the time allocated for one frame at the
usual projection frame rates (16-24 per second). The shuttle
mechanism described for the perforator and the stationary
~lat cam version shown in Figure 13 for motion picture
cameras require nearly one-half of the frame period. A
~uitab~e embodiment adapted ~or use in motion picture pro-
~ectors can easily be provided by u~ing the "skip-frame"
principle.
Figure 14 shows a modification of the perorator
high speed shuttLe device as it might be applied to an
amateur motion picture projector. Drive shaft 355 is suita-
bly journaled in bearings (not shown) which are mounted
~n frame members (not shown). Drive shaft 355 receives its
power input frotn a motor ~not shown), and is rotated in
the direction shown. Pin ~57 is rigidly attached to shaft
~ - 33 ~
:,
~ . :
7 1 '~ t
~SS , Advancc arm ~59 is attached to pi.n 357 throu~h a
~u~tabl.e bearing assembly (n~t sho~). Gear 387 is mounted
on shaft 355 by pins (no~ sho~ Gear 389 i5 mounted on
shaft 3~8 which is suitably journaled to rotate through
bearings (not sho~ which are mounted in the supporting
frame members (not shown). Gear 389 meshes with gear 387
and provides the necessary spe~d reduc~ion needed ko ob~ain
;. ~he proper skip frame rate~ Peripheral 391 is rig~dly moun~ed
to gear 389 by pins (not shown)~ Flat cam 149 is attached
to mounting bracket 383 through pin 381 and a suitable bear-
ing assembly (not sho~). Mounting bracket 383 is attached
to frame member 385 by suitable means (not shown). One
end of spring 393 is hooked around pin 395, which is rigidly
; attached to flat cam 149 to the left of pin 381~ The
other end of spring 393 is hooked around bracket 399 ~hich
~s attached to support member 4,01 by suitable means ~not
~hown). The purpose of spring 393 is to hold the leEt end of
flat cam 149 ln contac~ with cam 391. Advance arm 359
has a peripheral cam surface 180 which rides in contact
with the portion of flat cam 149 that is to the right of
pivot pin 381. One end of spring 361 hooks around pin
362 which is rigidly attached to advance arm 35~ . The
other end of spring 361 hooks around bracket 365 which
ls rigidly attached to support member 401 by sui~able means
~ot shown). The purpose o~ spring 361 is to hold the cam
180 of advance arm 359 in contact with flat cam 149 . The
~ 34 -
", ,, - - - - ~r
.
.
~5~
arcua~e cam surface 180 Oll advance arm 359 is of such a
shape so as to cause point P on the shuttle tooth portion
184 of advance arm 359 to engage a perforation in the
film and to cause point P to follow a path approximated by
the dashed line in Figure 14. Cam 39~ has an arcuate sur- :
face such that point P engages the perforation and then pro~
perly disengages the peroration during one rotat~on o
drive shaft 355 O The shape of cam 391 also is such that
it urges the left end of flat cam 149 in such a way that
point P will not engage the perforation of the film during
the subsequent two rotations oE drive shaft 355 . Depend-
~ng upon the gear ratio, any number of skipped strokes can
be provided. It should be noted that flat cam 149 and
the arcuate cam portion 180 of advance arm 359 can be
placed to one side of the film with only the shuttle tooth
184 being off set to align with ~he row of perforations
ln the fiim strip, In such a case the flat cam surface could
be in the ~ame plane as that of the film.
The film intermittent drive on the perforator
used during thread-up is a shuttling device which is designed
to drive a film which has no perforations. F~gure 15 shows
a modification of the thread-up shuttle design that may
be used in a motion picture camera that can accommodate per-
orated or unperorated ~ilm~
.. . .
~ ~ - 34a -
.
.
... . . . . . . . .. . ...
Refelring in detail to Figure 15~ we see that
drive shaft 415 is suitably journaled to rotate in bearings
(not sh~wn) which are mounted to fixed frame members (not
~hown) . Drive shat 415 re ceives its power input from a
motor (not shown~ in ~he direction sho~. Pin 417 is rigidly
~ttactled to ec:centric drive shaft 415. Shuttle arm 240 is
ro~atably attached to pin 417 ~hrough a sui~able bearing
as~embly (not shown). One end of arm 238 is a~tached to
~huttle arm 240 by pin 242 and a suitable bearing assembly
~not shown)~ The other end of arm 238 is rotatably attached
t~ bracket 427 by pin 236 and a suitable bearing assembly
(not shown)O Bracket 427 is at~ached ~o frame member 429
by suitabl~ means (not shown). Arm 431 is at~ached to
arm 238 by link connection 433 having either end pivots
. ~r ~nd connections~ The bottom end of arm 431 is attached
t~ bracket 437 through pin 435 and a suitable bearing assembly
~not shown). Bracket 437 is attached to frame member
429 by suitable means ~not shown), The top end of arm 431
and pad surface A may be covered by a high-fric~ion material,
such as polyurethane, to improve the film driving ~orce
with less spring pressure. The upper surface of arm 431
is trimmed accurately to provide optimum driving geometry and
~s muunted JUSt a few thousandths o an inch below the film
~ur~ceO Link connection 433 is so located in relation to
34b ~
'
.
..... .... " . ~ .. .. " .. ., ... . ... . ~ ... . . .. ... .... .. . . . .. ........ . . . . . . . . .... . ... . .
. . . . .
~s~
plns 236' and 435 as to produce the deslred film advance trMvel
o~ the upper surface of arm 431. 'rhe advantages of the embodi-
ment shown in Figure 13 is ~he added positive driving force
imparted to the film. This le~ds to hlgh prec~sion as w~s the
case in one experimental perfora~or in which this was the sole
means of advance and pitch determin~ion of ~he re~ulting
~ilm. Operation with lower clamp for~es or high speed or both
are improved by this arrangement, Ihe locations of the center
of eceentric drive shat 415, pin 242l, pin 236~ and pin 435
10 are obtained by ~he same considerations 8~; described above
; i~ arriving at ~he corresponding poin~ i~ Figure llo As
eccen~ric drive shaft 415 rotates in the direction shown ~n
Figure 15 the film is advanced in the direction shown by the
arrow in Figure 15. Intermitt~nt advance of film F wlll ~ake
place during approximately 1/2 of the rotation of drive shaf~
4150 The dr~ving control pad A is suitably attached to arm
240~ by means of resllienc connections and a s~op as described
in r~lation to Figure 9.
:: Figure 16 shows a schema~i.c of a further modifi~
ca~ion of the perforator thread up shuttle mechanism that
might be used in an amateur motion pic~ure projector
application. Drive shaft ~15~ ~ suitably 30urnaled to
rotate in bearings ~not shown~ which are mounted on fixed
~ rame members (not shown). Drive shaft 415' receives i~s
; power input from a mo~or (not shown) in the direction shownO
: Pin 417'is rigidly attached eccentrioally to drive sh~ft
415'. Shuttle arm ~40" ~s rotatably journaled to pi~ 17'
_ 3~ _
D
5~
~hrough a suitable be~ring assembly (no~ shown). Ge~r 451 i3
mounted on shaft 415' whlch is suitAbly 30urnaled ~o rotate
ln the ~rame members ~not shown)~ Cam 457 is rigldly
~tached to gear 453 by pins (not 6hown). Arm 238', is
rotat~bly journaled to shuttle arm 240" by pin 242" which in
turn is rigidly attached to shuttle arm 240t' by a suit~ble
bearlng assembly (not shown). The other end of ~nm 238;' is
pivotally attached ~o cam follower arm 465 by pin 463 ~nd a
su~table bearing assembly (not shown)0 The righ~ hand end of
cam follower arm 465 is pivotally attached to bracket 467
through pin 466 and a suitable bearing assembly (not shown~.
Bracket 467 i5 attached to support member 429l by any suitable
~eans (not shown~, The purpose o spring 471 i~ to hold the
left end of cam follower arm 465 in contact with the peripheral
surface of cam 457~ Arm 431' is a~tached to arm 23g" by link
connection 433' ~hich can have either end pivots or flexible
~nd connections. The ~ottorn end of arm 431' i9 attached ~o
braçket 437' through pin 435' and a suitable bearing assembly
.. . . .
(not shown)0 Bracket 437' is rigidly attached to support member
20. 429l by any suitable means (not shown). As drive sh~f~ 415'
i8 driven in the direction shown in Figure 16 film F is
advanced intermittently in the direction shown by the
arrow in Figure 16. The purpose o~ cam 457 is to urge the
; le~t end o~ cam follower arm 465 in such a manner so tha~
the relative location of pine 463, 242" and 435' is altered
80 that the film is intermiktently advanced a dist3nce equal
'. .
~ - 36 -
; . '
:~s~
to one frame pitch du~ing one rot~tion of d~ive sh~ft 415
~nd not advanced durin~ the subsequent two rotations of
drlve shaft 415', Depending upon the gear ratio any
number of skipped strokes can be provided. The relative
locations of drive shaft 415' a pin 242'9, pin 463 ~nd pin
435' are determined in she sam~ manner as above described
or the embodiment sho~n in Figure 11. The loca~ion of
~: link connec~ion 433' in relation ~o pin 463 on cam ollower
arm 465 and pin 435' is chosen such tha~ the desir d fllm `
1~ ~ravel is obtained as the film advancing station. The
` driving contact pad A is suitably attached to arm 240" by
means of resilient connections and a stop as described in
~ rela~ion to Figure 9.
;, Figure 17 shows a further modification of the
thread-up shuttle used in the perf~rat~ng device as it
might apply to an amateur motion picture camera that can
accommoda~e either perforated or unperforated film. Dr~ve
~haft 490 is suitably journaled to rotate through b~arings
~not shown) which are mounted in a rame support (not shown).
~0 Eccentric pin 492 i9 rigidly ~ttached to drive shaft 490.
Shuttle arm 494 is attached to drive shaft 490 through pin
492 and a suitable be~ring assembly (not shown). The
o'cher end of shutt~e arm 494 is pi~votally attached to
arm 498 at point 496 and ~erminates in a gripper fin~er
497 which is adapted to pinch she film between itself and
top edge of arm 498 during the film advance stroke. Finger
497 with its contact pad ~ is resiliently connected to arm
494 wlth a stop arranged to lift A from the f~lm for ~he
return stroke as discussed ln connection with Figure 9,
The bottom of arm 498 is attached to bracket 502 through
pln 500 in a suitable bearing assembly (not shown), B~acket
502 is rigidly attached to support member 504 by any suitable
manner (not shown), Preferably the angle between ~he lines
onmed between pin 500 and the center of drive shat 490 and
a l~ne drawn between the center o~ drive shaft 490 and pin 496
should be approximately 90 for optimum opera~ion. In like ,
manner ~he line drawn between pin 500 and point A where the
f~lm is gripped by the gripper 497 and to top of arm 498 should
be at approximately 90 to the tangent to the film path as
drawn at point A, The pivot center 496 should preferably be
on the same tangent to the film path, The embodiment sho~l in
Figure 17 may be preferable ~o that shown in Figure 15 where
~pace requiremen~s migh~ be restricting or some applica~ions.
As drive shaft 490 rotates in the direction shown in Figure 1~,
the film is advanced intermittently in the direction shown by
~he arrow in Figure 17. Note that this intermi~tent film
travel is opposite in direction to the applica~ion shown in
Flgure 15. The geome~ry can be arranged with equal ease and
~irnpliclty such that pivot 496 falls to the le~t of point A
in which case the film ;s advanced to ~he let for ~he di.rection
o rotation shown on Figure 17. In the modification shown ;n
Figure 17, arm 498 takes the place of arms 238 and 431 and
link connection 433 in the configuration as shown in Flgure 15
o 3~ -
i ' , .
4~
In the camera or perfora~or application, as sllown in Figure 17,it is understood tha~ the gripper 4g7 on the right end o~
shuttle arm 494 pinches the fllm against the top o~ ~rm 498
during approximately one-half of the eccentric rot~tion and
liftq away from the film for the remainder of the time.
Figure 18 shows a further embodiment o the ~hread~
up ~huttle of the perfora~or as it might be modified to operate
as an lntermittent feed appllcable ~o ~n ama~eur motion picture
projec~or. Eccentric pin 492' is rigidly attached tn drive
shaft 490' w~ich is sui~ably journaled to rota~e in be~rings
(no~ shown) which ~re mounted in a support member (not shown)~
The let end of shuttle arm 494' is attached to drive sha~t
490~ by pin 49~9 and a suitable bearing assembly (not sho~l).
Gear 516 is fixedly mounted on drive shaft 490' and gear 518 is
rigidly mounted on ~ha~ 520 which is suitably journ~led to
rot~te in bearings (not shown) which are su~tably mounted in
the ~upport frame (not shown). Gear 518 meshes with gear 516
to give the desired 3:1 or other ratio vf speed reduction
necessary for skip frame operation as required in a mo~.ion
picture pro3ec~or. Gam 522 is moun~ed rigidly on gear 518 by
pins ~not shown). The right end of shuttle arm 4941 is
pivotaLly a~tached to arm 498' by pin 496l and ~ermina~es : :
i . in a gripper finger 497l which ;.s adapted to pinch the film
between itself and the ~op edge o~ arm 498' during the film
advance stroke. Finger 497' wi~h ;~s contac~ pad A' is
reslliently connected ~o arm 49~l with a stop arranged to
. lit Al from t~le film for the return stroke as discussed in
c~nnection with Figure 9.
. ~.... . .:.~ ~ 39 --
... .. .... ~ .. . ...... ... . . . ..... . . ..... ., . ... .. . , . , " ., ~ . . , , ,, , ~ , . . . . .
. .
. ~5~
ThP bo~om nd of arm 498' is ~ttached to br~cket
502' through pin 5QO' in a sultable bearing assemblyO
Br~cket 502'1s rigidly at~ached to suppor~ member 504 9 by
any sui~able means (not sho~m)O The right end of cam
follower arm 530 is pivotally attached to bracket 534 by
pin 532 and bracket 534 is rigidLy mounted to support member
5047 hy any sui~able means ~no~ shown)O One end of spring
538 ;s hooked around pin 540 attached to cam follower arm
. 530 and he o~h~r end of spring 538 is hooked oneo brs~ke~
542 which is rigidly mounted ~o support member 504' by ~ny
~uitable means (not shown)O The bo~tom end of arm 544 is
pi~otally at~ached to cam follower arm 530 through pin 546
and a suitable bearing assembly ~not shown)O Pin 548 i~
rigidly attached to arm 4989 and fi~s through a slot in ~rm
544 so that arms 544 and 498~ m~y have relatl~e motion in
the direction o~ the slot onlyO The purpose of spring 538
to^u~e cam follower anm 530 into continuous contact
_ 5 '~
~ith th~ peripheral surface of cam 52~o The surface of cam
522 is of such a shape that during the first rota~icn of
8haf~ 490' the film is gripped at point A' between the
gripper portion 497' of shuttle arm 494' and the ~op of
;: arm 498i during one-half of the shaft ro~a~ion and lifts
8way from the film for ~he remai.nder of the timeO During
the subsequent two rot~tions of shaft ~901, the surface of
cam 522 is suc~ that it urges cam follower arm 530 upwards
which in turn causes pin 546 and arm 544 to mov~ upw~rds~ ~:
. Arm 546 tl~en contacts arm 497 ' ~nd rai ses it suffiGien~ly
: ~ 40 -
~ . .
to prevent the fi~m from being advanced durin~ the
subsequent revolutions of drive sha~t 490'. Depending
upon the gear ratio~ any number of skipped strokes can be
provided~ With the dlrection of rotation shown ln Figure
18 for drive sh~ft 490' 9 the film is advanced in~ermit~
tently ~o ~he right as shown by ~he arrow. The pivo~ point
496' can alternatively be located to the left of poin~ A'
reversing the film travel direc~ion as explained for Figure
. 17~ The top surface of arm 498l in the vicinity of point
10 Al engaged by pad surface A' may be covered with a high
friction material, such as polyurethane, to further enhance
the f~lm ad~ancing action. The region of Arm ~98' around
~;~ point A9 ~s carefully trin~ed and mounted a few thousandths
of an inch below the ilm surface.
It may be desirable to locate pln 546 substantially
i~ line wi~h pin 5001 in order to prevent unwanted relative
mo~ion between arm 544 and arm 598'. Th~ arrangement shown
in Figure 18 ls presented for the sake of clarity.
e inven~ion has been described in detail with
particular reference to preferred embodiment thereof, bu~
it will be understood that variations and modifications
can be effected within the spirit and scope of the invention.
, ' ' '
' ' ' .
:,
; ~ 4~ -
,
