U.S. patent number 3,747,469 [Application Number 05/158,704] was granted by the patent office on 1973-07-24 for linear linkless ammunition feed system.
This patent grant is currently assigned to General Electric Company. Invention is credited to Eugene Ashley, Douglas P. Tassie.
United States Patent |
3,747,469 |
Ashley , et al. |
July 24, 1973 |
LINEAR LINKLESS AMMUNITION FEED SYSTEM
Abstract
A cartridge storage and feed system includes a magazine having a
flat assembly of a plurality of side by side channels, each channel
for storing a column of cartridges, and an endless stripping
conveyor for cyclically withdrawing the leading cartridge from each
of said channels seriatim to provide a train of cartridges for
feeding to a weapon.
Inventors: |
Ashley; Eugene (Burlington,
VT), Tassie; Douglas P. (St. George, VT) |
Assignee: |
General Electric Company
(Burlington, VT)
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Family
ID: |
26855300 |
Appl.
No.: |
05/158,704 |
Filed: |
April 12, 1971 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
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826814 |
May 22, 1969 |
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Current U.S.
Class: |
89/34; 89/33.03;
198/540; 89/33.14; 198/598 |
Current CPC
Class: |
F41A
9/76 (20130101); B65G 47/681 (20130101); B65G
2201/0244 (20130101) |
Current International
Class: |
F41A
9/00 (20060101); F41A 9/76 (20060101); B65G
47/68 (20060101); B65g 037/00 (); B65g 047/06 ();
F41f 009/02 () |
Field of
Search: |
;89/33R,33B,33D,33MC,33BB,33BC,34,45 ;198/54,79,81 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Bentley; Stephen C.
Parent Case Text
This application is a continuation of Ser. No. 826,814, filed May
22, 1969, now abandoned.
Claims
We claim:
1. A cartridge storage and feed system comprising:
a magazine assembly having a plurality of side by side channels in
a planar array, each channel for storing a column of
cartridges;
an endless stripping conveyor assembly for serially withdrawing the
leading cartridge from the respective leading end of each of said
plurality of channels for providing a train of cartridges; and
an endless delivery conveyor assembly for receiving cartridges from
said stripping conveyor for delivery to a weapon;
said endless stripping conveyor assembly including
a plurality of series of stripping units, and
each series including seriatim:
a sprocket means,
a scoop and leading ramp unit,
a plurality of intermediate ramp units,
a trailing ramp unit;
each ramp unit having a ramp surface for cooperation with said
leading ends of said channels whereby to support the leading
cartridges at different instantaneous predetermined heights within
their respective channels, the difference between the maximum
height of said scoop and leading ramp unit and the minimum height
of said trailing ramp unit being equal to the maximum diameter of a
cartridge.
2. A system according to claim 1 wherein:
said endless delivery conveyor assembly includes:
a train of cradles, each for receiving a cartridge.
3. A system according to claim 2 wherein:
N.sub.m = the number of said plurality of channels:
P.sub.m = the distance between the centerlines of immediately
adjacent ones of said plurality of channels;
P.sub.c = the distance between centerlines of immediately adjacent
cradles of said delivery conveyor assembly;
X.sub.s = the distance between the centerlines of immediately
adjacent sprockets of said stripping conveyor assembly;
V.sub.c = the velocity of the delivery conveyor assembly;
V.sub.s = the velocity of the stripping conveyor assembly;
X.sub.s = N.sub.m [(Pc Pm)/P.sub.m +Pc]; and V.sub.c /V.sub.s =
(P.sub.c + P.sub.m)/P.sub.m.
4. A system according to claim 3 further including
a pressure bar assembly including a plurality of fingers,
each finger riding in a respective one of said plurality of
channels for positively engaging the respective trailing cartridge
in said channel.
5. A system according to claim 4 further including
a drive system for positively and synchronously driving said
stripping conveyor assembly, said delivery conveyor assembly, and
said pressure bar assembly.
6. A system according to claim 5 wherein:
said stripping conveyor assembly includes an endless first train of
interconnected links;
said delivery conveyor assembly includes a second train of
interconnected links; and
said drive system includes
a first driven sprocket engaging said first train of links,
the second driven sprocket engaging said second train of links,
third driven means engaging said pressure bar assembly, and
driving means coupled to said first driven sprocket, said second
driven sprocket, and said third driven means.
7. A system according to claim 1 wherein:
said channels are formed in a rectangular plate having a front face
onto which said channels open and a trailing edge and a leading
edge which said channels also open;
said stripping conveyor assembly being disposed adjacent said
leading edge and encircling said plate, said series of stripping
units passing closely adjacent said front face of said front plate,
whereby to engage cartridges disposed in said channels and
extending therefrom.
8. A system according to claim 1 wherein each scoop unit has an
arcuate hook shaped leading edge and
and in each said series,
said sprocket means is supported between the trailing ramp unit of
the preceding series and the hook-shaped leading edge of the scoop
unit of the instant series, whereby the leading cartridge in a
column advances in said column as the preceding series passes
thereunder until it leaves said trailing ramp unit of said
preceding series and is caught between said hook-shaped leading
edge and said sprocket, and is carried around and down by said
sprocket to said delivery conveyor assembly.
9. An article storage and feed system, comprising:
a magazine assembly having a plurality of channels, each channel
storing a plurality of articles in a column; and
a stripping conveyor assembly including an endless,articulated,
train of links carrying means for individually engaging,
accelerating and withdrawing the leading article from the discharge
end of a first one of said plurality of channels; and next,
individually engaging, accelerating and withdrawing the leading
article from the discharge end of a second one of said plurality of
channels; and next, individually engaging, accelerating and
withdrawing the leading article from the discharge end of a third
one of said plurality of channels; and so on in sequence to
individually engaging, accelerating and withdrawing the leading
article from the last one of said plurality of channels, and
thereby providing a train of articles, one from each channel,
seriatim.
10. An article storage and feed system, comprising:
a magazine assembly having a plurality of channels, each channel
for storing a column of articles; and
a stripping conveyor assembly including an endless, articulated,
train of links carrying means for individually engaging,
accelerating and withdrawing the leading article from the discharge
end of a first one of said plurality of channels; and next,
individually engaging, accelerating and withdrawing the leading
article from the discharge end of a second one of said plurality of
channels; and next, individually engaging, accelerating and
withdrawing the leading article from the discharge end of a third
one of said plurality of channels; and so on in sequence to
individually engaging, accelerating and withdrawing the leading
article from the last one of said plurality of channels, and
thereby providing a train of articles consisting of a group of one
from each channel, seriatim; and then commencing another cycle of
individually engaging, accelerating and withdrawing the leading
article from said discharge end of said first one of said plurality
of channels, and so on as before, thereby providing a succeeding
train of articles consisting of a group of one from each channel,
seriatim; and so on, cyclically.
11. An article storage and feed system according to claim 10
wherein the articles are cartridges of ammunition, and said
channels are in a planar array.
Description
BACKGROUND OF THE INVENTION
1. Field of the Invention
This invention relates to systems for supplying cartridges to
automatic guns.
2. Background of the Invention
Aircraft armament now requires extremely high rates of fire, e.g.,
6 to 12,000 shots per minute, in short or sustained bursts. While
the modern Gatling type weapon disclosed by H. McC. Otto in U.S.
Pat. No. 2,849,921 on Sept. 2, 1958 and by R.E. Chiabrandy et al in
U.S. Pat. No. 3,380,343 on Apr. 30, 1968 is admirably suited to
this task, the supplying of cartridges to the weapon becomes a more
critical limitation as the individual mass and total number of
cartridges to be accelerated and conveyed from the cartridge source
to the weapon increases.
The original Gatling gun utilized an on-the-gun, gravity-feed
hopper. Subsequently J.G. Accles in U.S. Pat. No. 290,622 on Dec.
18, 1883 disclosed a positive, helical magazine feed for the
Gatling gun. Thereafter, under the lead of F. Bailey and H.P.
Maxim, belt feeds, either continuous or link, became the mode. See
"The Machine Gun Belt," by Col. Jim Crossman, in The American
Rifleman, Dec. 1966, pp. 46-49. Departing from the belt approach,
A. Miclaus, Jr. in U.S. Pat. No. 1,136,695 on Apr. 20, 1915
proposed a linear, linkless feed system. The magazine had a
plurality of vertical storage channels, each containing a column of
cartridges under downward spring bias. An endless conveyor belt
below the magazine emptied each channel completely starting from
the most remote channel, and serially conveyed the train of
cartridges to the weapon. Recently, to supply a Gatling gun of the
Otto type, B. Dorsie and R.H. Casler, in U.S. Pat. No. 2,935,914 on
May 10, 1960 disclosed a linkless, positive, helical feed magazine,
of drum shape, in the spirit of Accles. A feed chute permits the
magazine to be spaced from the weapon. This type of magazine
becomes quite complex, and the drum shape is uneconomical in its
use of aircraft interior space.
SUMMARY OF THE INVENTION
Accordingly, it is an object of this invention to provide a
cartridge storage and feed system including a magazine of
relatively flat, rectangular configuration, for storing and
positively feeding cartridges to an endless stripping conveyor belt
for delivery to a remote weapon. The system is of relatively simple
construction and capable of high acceleration of the train of
cartridges.
A feature of this invention is the provision of a cartridge storage
and feed system including a magazine having a plurality of side by
side channels, each channel for storing a column of cartridges, and
an endless stripping conveyor for cyclically withdrawing the
leading cartridge from each of said channels seriatim to provide a
train of cartridges for feeding to a weapon.
RELATED CASE
Subject matter disclosed but not claimed in this application is
disclosed and claimed in U.S. Pat. No. 3,612,255 issued to D. P.
Tassie on Oct. 12, 1971.
BRIEF DESCRIPTION OF THE DRAWINGS
These and other objects, features and advantages will be apparent
from the following specification of the invention taken in
conjunction with the accompanying drawing in which:
FIG. 1 is a perspective view of a cartridge storage and feed system
embodying this invention;
FIG. 2 is a front view in elevation of the system of FIG. 1;
FIGS. 3 and 4 are similar to FIG. 2 and illustrate the progressive
stripping of cartridges from the magazine channels by the stripping
conveyor and their transfer to the delivery conveyor;
FIG. 5 is a perspective view of the synchronized drive system for
the system of FIG. 1;
FIG. 6 is a left side view in elevation, in partial cross-section,
of the system of FIG. 2;
FIG. 7 is a detail, showing the channel construction, taken along
the plane 7--7 of FIG. 6;
FIG. 8 is a perspective detail view of the lower left rear corner
of the system of FIG. 1
FIG. 9 is a perspective detail view of the turn around of the scoop
conveyor of FIG. 1;
FIG. 10 is a perspective detail view (from the front looking up) of
a scoop and sprocket of the stripping conveyor of FIG. 1;
FIG. 11 is a perspective detail view of the left rear of the
stripping conveyor of FIG. 1;
FIG. 12 is a perspective view of the system of FIG. 1 illustrating
the use of the delivery conveyor to reload the channels with
cartridges;
FIG. 13 is a view in cross-section taken along plane 13--13 of FIG.
6 illustrating the guide and drive for the stripping conveyor;
FIG. 14 is a front detail view in elevation of the scoop and the
delivery conveyor cradles;
FIG. 15 is an exploded perspective detail view of the system of
FIG. 1 illustrating the pressure bar assembly for the channels;
FIG. 16 is an exploded perspective detail view of the mounting for
the pressure bar of FIG. 15;
FIG. 17 is a front view in elevation in cross-section taken along
the plane 17--17 of FIG. 18 of the gearing in the mounting of FIG.
16;
FIG. 18 is a left side view in cross-section taken along the plane
18--18 of FIG. 17; and
FIG. 19 is a left side view in cross-section taken along the plane
19--19 of FIG. 17.
DESCRIPTION OF THE PREFERRED EMBODIMENT
The cartridge storage and feeding system shown in FIG. 1 includes a
main plate assembly 10, a stripping conveyor assembly 12 and a
delivery conveyor assembly 14. The main plate assembly includes a
plurality of side by side channels 16, each channel adapted to
receive and to hold a column of cartridges 18, and a pressure bar
assembly 20 adapted to advance the cartridges contiguously forward
into engagement with the stripping conveyor assembly 12. The
stripping conveyor assembly withdraws the leading cartridge from
each column serially and transfers these cartridges as a train of
cartridges to the delivery conveyor assembly, which delivers the
cartridges serially to the weapon (not shown).
As shown in FIGS. 2, 3 and 4, the stripping conveyor is an endless
belt encircling the lower portion of the main plate assembly and
consisting of a plurality of wedge and sprocket assemblies or
series. Each wedge assembly includes a plurality of ramp elements
22, 24, 26, 28, 30, 32, 34 of which all except 22 are L-shaped. The
leading element 22 is of maximum height and the trailing element 34
is of minimum height. The difference between the maximum and
minimum heights is equal to the maximum diameter of the cartridge.
The leading edge 36 of the lead element is arcuate, or scooped, and
is spaced from a sprocket 38 having a plurality of cut outs 40 and
which is carried ahead of the leading element.
It will be seen that each wedge assembly advances across the front
of the main plate assembly from left to right, its ramp elements
gradually lower the lead cartridges in each channel to a level
whereat the leftmost cartridge, which rides off the trailing ramp
element, rides into a sprocket cut-out 40 and under the leading
edge or scoop 36 of the adjacent leading element of left adjacent
wedge assembly. The sprocket carries the scooped cartridge
counter-clockwise around and down and onto a cradle 42 of the
delivery conveyor assembly. The upper run of the delivery conveyor
assembly advances from left to right under the stripping conveyor
assembly and receives the scooped cartridge therefrom.
Various configurations in the combination are feasible, based on
the following criteria:
If N.sub.m = the number of cartridge channels of the main plate
assembly;
P.sub.m = the distance between the centerlines of immediately
adjacent channels of the main plate assembly;
P.sub.c = the distance between the centerlines of immediately
adjacent cradles of the delivery conveyor assembly;
X.sub.s = the distance between the centerlines of immediately
adjacent sprockets of the stripping conveyor assembly;
V.sub.c = the velocity of the delivery conveyor assembly; and
V.sub.s = the velocity of the stripping conveyor assembly;
then X.sub.s = N.sub.m [P.sub.c P.sub.m /P.sub.m +P.sub.c ]; and
V.sub.c /V.sub.s = (P.sub.c + P.sub.m)/P.sub.m.
Thus, if P.sub.c = P.sub.m, then X.sub.s = N.sub.m /2; and V.sub.e
= 2 V.sub.s.
In the embodiment here shown, Pc = Pm, there are 16 channels 16 in
the main plate assembly, and six wedge assemblies in the stripping
conveyor assembly. The delivery conveyor assembly runs twice as
fast as the stripping conveyor assembly. It will be obvious that in
any configuration to keep the delivery conveyor assembly filled, at
least two wedge assemblies must be utilized.
The main plate assembly 10 includes a main plate 46 having a
plurality of parallel, laterally spaced apart channels 16 in its
front face, each channel having a pair of forward, laterally
directed lips 48 to engage the extractor disks 49 of the cartridges
18. Also provided on the front face of the main plate are a left
gear rack 50 and a right gear rack 52, a left, upper, forwardly
directed, arm 54, a left lower, fowardly directed arm 56, a right,
upper forwardly directed arm 58, and a right, lower, forwardly
directed arm 60. A transverse beam 62 is secured to the lower
margin of the main plate and extends downwardly and rearwardly
therefrom. This beam supports the stripping conveyor system, the
delivery conveyor system, the drive system and the main plate
assembly.
Plane 13--13 is taken at 45.degree. to the plane of the front face
of the main plate 46. As seen on FIGS. 6 and 13, a rear lower guide
groove 64, a rear upper guide groove 66, a front lower guide groove
68 and a front upper guide groove 70, all parallel, spaced apart
and symmetrical are formed in the beam. A left sprocket 72 and a
right sprocket 74 are disposed in apertures through the bar
perpendicular to the plane 13--13. A left stripping conveyor
sprocket drive shaft 76 and a right stripping conveyor sprocket
drive shaft 78 are journaled through the bar and respectively keyed
to the sprockets by a left key 80 and a right key 82. A left
bracket assembly 84 and a right bracket assembly 86 are secured to
the beam 62. A left, delivery conveyor sprocket drive shaft 88 is
journalled through the left bracket assembly 84 perpendicular to
the plane of the front face of the main plate; and a right,
delivery conveyor sprocket drive shaft 90 is similarly journalled
through the right bracket assembly 86. A main power shaft 92 is
journalled through and between the bracket assemblies 84, 86, and
this shaft is adapted to receive the power necessary to drive the
total system. A left face gear 94 and a right face gear 96 are
fixed to the drive shaft 92, and are respectively meshed with a
left spur gear 98 fixed to the shaft 88 and a right spur gear 100
fixed to the shaft 90. A left bevel gear 102 is fixed to the lower
end of the shaft 76 and is meshed with the gear 98, and a right
bevel gear 104 is fixed to the shaft 78 and is meshed with the gear
100. A left splined shaft 106 is journalled through and between the
left upper and lower arms 54, 56; and a right splined shaft 108 is
journalled through and between the right upper and lower arms 58,
60. A left spur gear 110 is fixed to the lower end of the shaft 106
and is meshed with a bevel gear 112 fixed to the upper end of the
shaft 76; and a right spur gear 114 is fixed to the lower end of
the shaft 108 and is meshed with a bevel gear 116 fixed to the
upper end of the shaft 78.
The pressure bar assembly 20 includes a cross bar 118 having two
series of pressure fingers 120 extending therefrom. The difference
in length between the longest and the shortest finger in each
series is equal to the maximum diameter of the cartridge. The cross
bar is releasably secured to and between a left traveling gear box
122 and a right traveling gear box 124 by four bayonet type pin
fasteners 126. Each pressure finger travels in a respective channel
16 under the lips 48 thereof, while the cross-bar 118 travels over
the front face of the main plate. A left spur gear 128 is fixed to
the left shaft 130 which is journalled at the right end to a left
web 132 of the cross-bar 118 and meshed with the left rack 50. The
left end 134 of the shaft 130 has a triangular cross-section. The
left traveling gear box 122 includes a housing 136, and a worm gear
138 splined to a shaft 140. The right end 142 of the shaft 140 has
a triangular recess adapted to interlock with the shaft end 134,
and the left end has an adjustable machine screw extension 144. The
shaft right end 142 passes through an aperture in the housing 136
to interlock with the shaft left end 134. The shaft extension 144
passes through an aperture in the housing 136 and is captured by an
arm 146 which is pivoted at its lower end 148 to the housing and
which is biased at its upper end 150 by a spring 152 against the
housing. The arm 146 serves to normally lock the shaft 140 to the
shaft 130. Pivoting of the arm 146 longitudinally separates the
shaft 140 from the shaft 130, without longitudinally disturbing the
worm gear 138. The worm 154 is free on the shaft but is secured to
an adjustable spline 156 outside of the housing, so that rotation
of the splined shaft 106 causes in-train rotation of the worm 154,
the worm gear 138, the shafts 140 and 130 and the spur gear 128.
Rotation of the spur gear 128 which is meshed with the rack 50
causes translation of the traveling gear box and the cross bar 118.
The right traveling gear box 124 is provided with a symmetrical
assembly including a housing 158, a worm 160, an adjustable spline
162, a worm gear 164, a shaft 166, and a spring biased arm 168; and
the rack 52 meshes with a spur gear 170 which has a shaft 172
interlocking with the shaft 166.
The stripping conveyor assembly 12 includes and endless chain of
links of substantially modified double-U-construction driven by the
sprockets 72 and 74. In each wedge assembly or series, the sprocket
38 is carried by a link 174, the leading element 22 is carried by a
link 176, the elements 24, 26, 28, 30 and 32 are carried by a
respective link 178, and the element 34 is carried by a link 180.
Each link has a central web portion 182 with a boss extending
therefrom, an angled web extension portion 184, a lower side wall
having a trailing extension 186 and a leading extension 188, and an
upper side wall having a trailing extension 190 and a leading
extension 192. A pin 194 having a sleeve 194a interconnects the
extension of immediately adjacent links, and has a lower roller 196
and an upper roller 198. An intermediate pin 194b having a sleeve
194c is fixed within each link to provide a full complement of pins
194 and 194b to be driven by the sprockets 72 and 74. The rollers
196 and 198 are adapted to ride in the rear guide surfaces 64, 66,
and the front guide surfaces 68, 70. The bosses 200 on the links
178 are cylindrical and respectively support the elements 24, 26,
28, 30 and 32 spaced from the respective web portions. The bosses
202 on the links 180 support the element 34 spaced from the
respective web portion, and has a cut-out 202a to clear the
adjacent sprocket. The element 34 also has a cut-out 34a to clear
the adjacent sprocket. The bosses 204 on the links 174 have a
respective shaft 206 upstanding therefrom on which the sprocket 38
is mounted for rotation between a lower thrust washer 208 and an
upper washer 210 and is captured by a cotter pin 212. The sprocket
38 includes a central tube portion 214, an upper end plate 216
having five teeth 218 and five cut-outs 220, and a lower end plate
222 having five teeth 224 and five cut-out 226. The lower plate 222
has a peripheral groove 228 therein, and each tooth 224 has an
arcuate groove 230 in its lower surface. The leading element 22 is
substantially a hollow box, including a rear wall 232, a front wall
234, a top wall 236, a side wall 238 and a rear wall extension 240.
The edges of the side wall are arcuately shaped to provide the
leading edges 36. The front surface of the rear wall extension 240
is immediately behind the rear surface of the lower end plate 222
of the sprocket. An arcuate guide finger 242 is fixed on a pivot
rod 244 which is journaled through and between the front and rear
side plates 238, 232. A spring 146 biases the finger away from the
sprocket. The leading edges 36 and the inner face of the guide
finger are concentric with the sprocket. A plurality of regularly
spaced apart disks or buttons 248 are fixed to the upper surface
250 and the front surface 252 of the horizontal beam 62. As each
sprocket 38 is transported transversely across the main plate
assembly by the train of links 178, the buttons sequentially engage
the lower level of the cut-outs 226, like cogs, and cause the
sprocket to rotate about its shaft 206.
It will be noted that the train of links 178 passes between the
rear guide surfaces 64, 66 and the front guide surfaces 68, 70,
i.e., around the returns, without any guidance. This is
accomplished by (1) making the distance between the centerlines of
adjacent link pins 194 equal to the distance between centerlines of
the rear guide surfaces 64, 66 and the front guide surfaces 68, 70;
and (2) meshing the drive means, i.e., sprocket 72 and/or 74, with
both lengths of the train. The dynamic characteristics of the
linkage during turnaround are such that the center of gravity of
the link decelerates at a uniform rate and then accelerates at a
uniform rate. The path of the center of gravity forms a true
semicircle. Also, the link rotates about its center of gravity.
Thus the link is under control both geometrically and
dynamically.
The buttons 248 adjacent the front and rear lengths of the train of
links 178 serve to synchronize the rotation of sprockets thereon.
However, the sprockets swing away from the horizontal beam when
going around the returns. To maintain synchronization of the
rotation of the sprockets between the front and rear lengths a left
cam plate 254 and a right cam plate 256 are respectively mounted to
the ends of the beam. In going around a return, as a sprocket lower
plate cut-out 226 leaves the last button adjacent one length, one
of the arcuate grooves 230 in the sprocket lower plate engages the
edge of the cam plate 254 or 256 and remains engaged until a lower
plate cut-out engages the first button adjacent the other length.
While an even number of links 178 has been shown, an odd number may
be utilized. Further, while a sprocket and rod drive combination
has been shown, a rack may be formed on each link, and be driven by
a gear.
The delivery conveyor assembly 14 is similar to that shown by R.G.
Kirkpatrick in U.S. Pat. No. 3,429,221 issued Feb. 25, 1969.
Briefly, the assembly includes a train of links 260, each link
having a cradle 42, a left knuckle 264, two right knuckles 266, a
front guide follower 268 and a rear guide follower 270. Adjacent
knuckles are coupled by a pin 272. The train of links rides on and
around a folded inner guide plate 274 which has a front guide
groove 276 and a rear guide groove 278 formed therein to
respectively receive the front follower 268 and the rear follower
270 of each link. A left sprocket 272 and a right sprocket 274 are
respectively fixed to the shafts 88 and 90 and are disposed between
and extend through the upper and lower folds of the guide plate.
The teeth of the sprockets engage the train between adjacent
cradles to drive the train. An outer guide plate extends from the
right hand end of the main plate, around the right return and under
the train of links to the left. Although not shown, the delivery
conveyor continues on the left to the gun which is being fed.
For operation, each of the channels 16 is charged with the same
number of rounds. Each round is held in the channel by the lips 48
siezing the extractor disk 49, as shown in FIG. 7. The lower,
leading round of each row rests on the upper edge of a respective
ramp element 22. . . 34. A finger 120 of the cross-bar 118 rests on
the highest, trailing round of each row. Rotation of the main power
shaft 92 causes rotation of the stripping conveyor shafts 76, 78
and, thereby, the train of stripping conveyor links 178, and also
causes rotation of the splined shafts 106 and 108 and, thereby, the
cross-bar spur gears 128 and 170. Shaft 92 also causes rotation of
the delivery conveyor shafts 88 and 90 and, thereby, the train of
delivery conveyor links 260. The centerline spacing between
adjacent channels 16 is equal to the centerline spacing between
adjacent cradles 42. The delivery conveyor has twice the velocity
of the stripping conveyor. As each combination of scoop 36 and
sprocket 38 passes under a channel 16 it scoops off the lowermost,
leading round and passes it around and down to a cradle 42 in the
delivery conveyor. In effect, each combination of scoop and
sprocket fills up the length of delivery conveyor between it and
the next preceding scoop and sprocket. The pressure bar assembly 20
maintains a constant pressure on the columns of rounds, so that the
respective leading rounds are presented to the stripping conveyor
irrespective of the effect of gravity. The delivery conveyor
delivers the rounds from the scoop and sprocket combinations,
around, down and back to the gun.
Rounds of ammunition may be loaded into the main plate assembly by
either of two alternative modes.
In the first, direct loading mode, the four fasteners 126 are
withdrawn and the arms 146, 168 are swung outwardly to release the
cross bar 118 from the traveling gear boxes 122, 124, whereupon the
cross bar may be slid up the front face of the main plate until the
fingers 120 clear the channels 16. Rounds may then be inserted from
the top into the channels by sliding the extractor disc 49 of each
round 18 under the lips 48 of the respective channel. The rounds
will slide down until the leading round in each channel rests on
the upper edge of the respective ramp element. An equal number of
rounds must be inserted in each channel. The cross bar 118 is then
returned to the top of the plate with its fingers 120 entering the
channels 16 and slid down until each finger rests on the last round
in each respective column. The traveling gear boxes are run up
manually into alignment with the cross bar until the shafts 140 and
130, and 166 and 172 re-engage. The four fasteners 126 are
replaced.
In the second, reverse feed mode, the rounds of ammunition are
initially fed into the delivery conveyor. The drive shaft 92 is
rotated in reverse, to run the entire system in reverse, including
the scoop-sprocket combinations from right to left, and the
pressure bar assembly 20 upwardly. The delivery conveyor delivers
the rounds to the stripping conveyor. Each round passes under and
into a sprocket, is guided by the finger 242 upwardly out of the
cradle 42 and along the scoop leading edges 36, into a channel 16
and a top of the ramp element 34. As the rounds are spun off onto
the ramp elements, the pressure bar 118 with its fingers 120 rises
to accommodate the rounds.
* * * * *