Note: Descriptions are shown in the official language in which they were submitted.
.
DESCRIPTION
TRANSPORT MECHANISM
The present invention relates generally to trans-
port mechanisms for use in material handling systems, but
more par$icularly to such mechanisms which are capable of
receiving concurrently at two or more spaced inlet openings,
a plurality of like objects, and of causing them to come to-
gether in a single row at a single outlet opening to be fed
to a predetermined location.
Many industries and other business and non-busi-
ness activities require the handling of a great many like
articles or objects within a short period of time. This is
certainly true with respect to mass production manufacturing
operations wherein profitability depends upon performing a
specific manufacturing, distribution or handling function
within an extremely short period of time so as to m~re ef-
fectively utilize both labor and capital.
High speed material handling systems are also re-
quired for reasons other than profitability, as for instance
in the making of modern-day armaments where there is a need
for handling a larse quantity of bullets or projectiles for
rapid firing guns and the like.
In all such applications, it is desixable to move
accurately, effectively and at an extremely high rate o
speed, a plurality of like objects from a storage compart-
ment or reservoir of such objects, to a predetermined loca-
tion such as the breech of a high speed weapon. Furthercomplicating the requirements is the need to have the ob-
jects or articles stored in maximum hiqh density manner
because space is usually at a premium. Thus the articles
must be moved from such high density storage condition to
the predetermined location at such extreme rate of speed
and in such accurate and effQctive manner.
Heretofore, such material handling systems have
been relatively slow in operation, being unable to transport
the objects from their storage compartment or compartments
to the predetermined location in a consistent, foolproof
manner and at high speed. With respect to a military weap-
onry, it will be readily understood that such 510w, unreli-
able systems have been responsible for many unfortunate
results such that military positions have been overtaken
due to the inability of weapons to fire projectiles consis-
tently and at high speed.
It is an object of the present invention to pro-
vide a transport mechanism for rapidly and sequentially
transporting a plurality of like objects from a storage com-
partment to a predetermined location.
Another object of the present invention is to pro-
vide a ~ransport mechanism as characterized above whereby
a plurality of like objects are fed substantially concur-
rently through a plurality of spaced inlet openings of the
mechanism and thereafter are ~apidly and accurately arranged
in a single row and in side by side relation for transport
to a predetermined location.
A still further object of the present invention
is to provide ~ transport mechanism as characterized above
which is adaptabl~ for handling substantially any si2e or
~5 shape of like objects for transporting them from a storage
compartment to the predetermined location.
Another still further object of the present in-
vention is to provide a transport mechanism as character~
ized above which permits high density storage of objects
within the storage compartment and which permits maximum ~
design alternatives in constructing the storage compartment
regardless o the si~e ~nd shape of the like objects.
An even still further object of the present inven-
~L2~L7~
tion is to provide a transport mechanism as characterizedabove which is virtually entirely mechanical in nature, ut-
- ilizing reliable physical drive mechanisms for spacing theobjects and then interleaving or merging them into a single
row to be transported to the predetermined location~
Another still further object of the present in-
vention is to provide a transport mechanism as characterized
above which is simple and inexpensive to manufactuxe and
which is rugged and dependable in operation~
The novel features which I consider characteristic
of my invention are set forth with particularity in the ap-
pended Claims. The invention itself, however, both as to
its organization and mode of operation, together with addi-
tional objects and advantages thereof, will best be under-
stood from the following description of specific Pmbodiments
when read in connection with the accompanyiny drawings, in
which:
Figure 1 is a fragmentary elevational view of a
transport mechanism according to the present invention show-
ing objects being transported from a storage compartmentto a predetermined location;
Figure 2 is a fragmentary sectional ~iew taken
substantially along line 2-2 of Figure l;
Figure 3 is a frasmentary sectional view taken
substantially along line 3-3 of Figure l;
Figure 4 is a top plan view of a portion of Figure
1, taken substantially along line 4-4 thereof;
Figure 5 is a fragmentary sectional view taken
substantially along line 5-5 of Figure 4;
Figure 6 is a sectional view taken substantially
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along line 6-6 of Figure 5;
Figure 7 is a sectional view taken substantially
along line 7-7 of Figure 4;
Figure 8 is a fragmentary sectional view taken
substantially along line 8-8 of Figure 7 of the drawings;
and
Figure 9 is a phantom view showing the relation-
ship between certain control and transport members.
Like reference character~ indicate corresponding
parts throughout the several views o~ the drawings.
Referring to Figure 1 of the drawings, there is
- shown therein a material handling system 10 wherein like
objects are transported from a storage ~ompartment 12 to a
predetermined location 14. Such like objects are shown in
Figure 1 as being projectiles or machine cannc>n rounds 16
for use in an automatic weapon (not shown), and are to be
transported by the material handling system 10 to the pre-
determined location 14. Although the subject invention has
extremely important application to military weaponry for
fast and effective weapon~ of all sizes, it is rea~ized that
the subject invention is equally applicable to thP trans-
porting or feeding of other kinds of like objects such as
beverage bottles, plastic containPrs, boxes and the like,
and, for that matter, substantially any other kind of object
which is required to be rapidly fed to a given or predetex~
mined location. Although reference heretofore and herein-
after may be made to projectiles for usè in weaponry, such
term is to be understood as including substantially any and
all kinds, si2es and shapes of objects.
The storage compartment 12 for the projectiles 16
may take substantially any desired form, but is shown in
~ Figures 1 ancl 2 as comprising an endless belt or chain 18
whereon the projectiles 16 are individually positioned and
mounted, as shown diayrammatically in said Figures 1 and 2,
so that automatic drive means can be employed to feed such
projectiles to the subject transport mechanism 20. That is,
by means of a suitable source of power for driving endless
belt 18, the projectiles 16 can be fed from the storage com
partmQnt 12 to the transport mechanism 20. A device includ-
ing a biasing spring ~2 is shown diagrammatically in FigurP
- 2 ~o provide the endless belt or chain 18 with constant ten~
sion for proper operation.
As shown most clearly in Figure 1 of the drawings,
lo the projectiles 16 are arranged in a plurality of levels or
banks or bays to facilitate simultaneous feeding of a plur-
ality of such projectiles from several different sources
~ thereby increasing the speed with which the projectiles can
be brought into the transport mechanism. Although the rep-
- 15 resentation sho~l in the dr~wings is with respect to two
pro3ectile banks or bays 24 and 25, it is well realized that
the number of such bays can be increased as desired, with
the subject invention being equally applicable to any number
of such bays.
It is a significant Eeature of this invention that
the transport mechanism be so constructed and operable as
to receive projectiles 16 or other objects at an extremely
fast rate and from maximum density storage wherP space is
utilized to maximum efficiency. Accordingly, transport
mechanism 20, as will hereinafter become more apparent~ is
adaptable to working with a storage compartment 12 wherein
the projectiles are stored adjacent each other and are bro-
ught out at high speed in such side-by-side relation.
The transport mechanism 20 includes, as shown
most particularly in Figure 7 of the drawings, a spacing
unit 28 and a merg:ing unit 30. Spacing unit 28, in con-
formance wi~h the construction of storage compartment 12
having two bays or levels 24 and 26 of projectiles 16, is
formed with two inlet openings 3~ and 34. Each such opening
is adapted to receive in a sequential manner a plurality of
~3L7~L~6
such projectiles 16. To accomplish this, each level of the
spacing unit 28 is provided with retainers 36, each of which
is provided with three arcuate cutouts 36a, into each of
which cutouts a projectile is placed as it is received thr-
ough the corresponding inlet opening. To facilitate movingthe projectiles from the endless chain 18 to the retainers
36, guide members 37 are provided to direct or guide the
projectiles through the inlet openings 32 and 34. It will
be noted, as shown in Figure 7, that the upper portion of
the spacing unit 28 has two such retainers 36, as does the
lower portion thereof.
The retainers 36 are mounted on a rotatable shaft
for receiving the projectiles as the retainers are rotated.
The upper retainers 36 are fixed to a hollow outer shaft
38, and the lower retainers 36 are fixed to a solid inner
shaft 40 which extends through the shaft 38.
Because of the particular construction of the pro-
jectiles 16, each of the lower guide members 37 is further
provided with a protrusion 42 which is so positioned and
adap~ed to receive the shallow annular recess 16a at the
base of the projectile. As will hereinafter become more
apparent, protrusion 42 insures proper vertical orientation
of the projectiles entering through inlet openinys 32 and
34 as they pass through the spacing unit 28.
At the top of spacing unit 28, as shown in Figure
7 of the drawings, is ~ drive mechanism or transmission 46
for rotating the concentrically arranged shafts 38 and 40
in a predetermined sequence or manner, as will hereinafter
be explained in greater detail. To enable shaft 38 to prop-
erly rotate, a suitable bearing 48 is provided between the
lower portion of shaft 38 and a frame member. In simular~
fashion, a suitable bearing 50 is provided between the lower
extremity of shaft 40 and a frame member, and another bear-
ing 52 is provided between an intermediate portion of shaft
40 and a frame member.
~Z~7~6
-7-
As the projectiles 16 are received at the inlet
openings 32 and 34, they are guided into the re*ainers 36
by guide members 37. From there, the projectiles are trans-
ported by the rotating shafts 38 and 40 to a position essen-
tially diametrically opposite the inlet openings. To ac-
complish this, a gear member 54 is provided, to be driven
by a drive gear 56 which is part of the merger unit 30, and
whichis connected to a suitable source of rotational power
(not shown~. When the subject transport mechanism 13 is
operating, gear 56 is driven at a constant speed so as to
drive gear 54 accordingly.
Referring to Figure 5 o~ the drawings, a bearing
57 is provided between gear 54 and an enlarged portion 38a
of shaft 38 so that gear 54 is maintained in proper coaxial
re~ation with shaft ~8.
The upper end of shaft 40 which extends beyond
the upper end of hollow shaft 38 is formed with a reduced
portion 40a having splines 40b, a further reduced portion
40c, and an end portion 40d having fastening threads 40e.
~iounted on the reduced portion 40c of shaft 40 is
a suitable bearing 58 which carries connecting drive member
60, which is formed with three extensions 60a which are off-
set from each other by ninety degrees with respect to the
axix of rotation of drive member 60 as shown most particu-
larly in Figures 4 and 6 of the drawings. A threaded fast
ening bolt 62 having a head 62a and a fastening nut 62b is
provided in each of such extensions 60a as shown most par-
ticularly in Figures 5 and 6 of the drawings.
The bearing 58 provides proper orientation of con-
necting drive member 60 with respect to the concentricallyarranged rotatable shafts 38 and 40, as did bearing 57 for
drive gear 54.
Shaft 38 is provided with a cylindrical reduced
--8--
portion 38b formed with splines 38c, and a reduced threaded
end portion 38d which carries a fastening nut 64.
Fitted onto the splines 40b and 38c of the shafts
40 and 38, respectively, are cylindrical drive plates 66
and 68, respectively. As shown most particularly in Figures
5 and 6 of the drawings, each such drive plate 65 and 68 is
formed with three circular openings as shown at 66a and 68a
respectively, to accomodate the three extensions 60a of the
drive member 60. That is, as shown in Figure 5, each exten-
sion 60a of member 60 extends through openings 6Ça and 68a inthe drive plates 66 and 68.
To effectively rotate the shafts 38 and 40 from
gear member 54 and connecting drive member 60, a drive pin-
- ion 70 is provided therebetween, as shown. Such pinion is
formed with upper and lower end portions 70a and 70b which
are mounted in the inner races of bearings 72 and 74, re-
spectively, the outer races thereof being fitted within
suitable openings in drive member 60 and gear 54, respect
ively. Drive pinion 70 is further formed with eccentric
shaft portions 70c and 70d shown most particularly in Figure
5.
Each of the drive plates 66 and 68 is formed with
a rectangular cutout as shown at 66b and 68b, respectively.
As shown most particularly in Figure 6 with respect to drive
~5 plate 66, the rectangular cutout 66b is of~set ninety d~-
grees with respect to the aforedescribed circular openings
66a. A bushing 76 formed with a cylindrical opening 76a for
rotatably receiving the cylindrical eccentric shaft portion
70c, as shown in Figure 6, is provided with a generally
squar or rectangular outer periphery, as shown at 76b so
as to have only reciprocatory motion within opening 66b of
drive plate 6~o That is, as will hereinafter become more
apparent, bushing 76 is restricted to radial, reciprocatory
movement within slot or opening S6b of drive plate 66.
g
In like fashion, a bushing 78 having a cylindrical
through opening 7Ba and a generally sguare or rectangular
outer periphery 78b is provided to reseive eccentric shaft
portion 70d of drive pinion 70. The bushing 78 slidably
fits within the slot or opening 68b formed in drive plate
~8.
Drive pinion 70 is further formed with a cylin-
drical intermediate portion 70e whose axis coincides with
the axis of rotation of pinion 70 as defined by the end
portions 70a and 70b within bearings 72 and 74. Such inter-
mediate portion 70e is formed with external gear teeth 70f
which mate with the internal gear teeth 80a of a stationary
ring gear 80. Such ring gear 80 is mounted on the frane of
the spacing unit 28, stationary relative to the rotation of
shafts 38 and 40~ as will hereinafter become more apparent.
The spacing unit 28 operates generally as follows:
The projectiles 16, as shown in Figure 2 of the drawings,
are fed into the inlet openings 32 and 34 by means of the
aforedescribed chain drive 18 and guide members 37. In this
r~gard, as shown in Figure 2, the individual projectiles are
positioned in one of the three arcuate openings in the re-
taining members 36 at the respective level at which such
projectiles enter $he unit 28. The concentrically arranged
shafts 3g and 40 are continuously rotated as follows: Refer-
ring to Figure 5 of the drawings, the gear 54 is driven ata constant angular speed by virtue of the drive gear 56.
The drive member 60 is rotated with drive gear 54 as a
result of being fi~nly connected thereto through the three
extensions 60a and fastening bolts 62. This causes drive
pinion 70, as defined by its axis extending through the end
poxtions 70a and 70b ~eof, to follow a circular path about
the axis of rotation of the concentrically arranged shaft~
38 and 40, Engagement of pinion 70 with the drive plates
66 and 68 through the bushings 76 and 7~, respectively,
causes such movement of pinion 70 to rotate shafts 38 and
40. This results from the fact that the drive plate 66 i5
`. '.- ', !~ '
. . .
7~
10'
firmly secured to shaft 40 by virtue of the firm engagement
of the former with the splines 40b on the latter~ and by
virtue of the firm engagement between drive plate 68 and
the splines 38c on shaft 38. Such rotation of shaft 38
causes each projectile 16 in the upper portion of the spac-
ing unit 28 to be rotated from the inlet opening 32. In
~ like fashion, rotation of shaft 40 causes the projectile in
the lower portion of the spacing unit 28 to have similar
rotational movement from the inlet opening 34.
10As drive pinion 70 is so actuated to rotate the
shafts 38 and 40 through their respective drive plates 66
and 68, pinion 70 is caused to rotate about its own axis as
defined by end portions 70a and 70b thereof. This results
from engagement of gear teeth 70f of pinion 70 with gear
teeth 80a of stationary riny gear 80. Such rotational move~
ment of pinion 70 about its own axis causes eccentric shaft
portions 70c and 70d to follow paths about the axis of ro-
tation of pinion 70, producing a reverse movement component
and thereafter a forward movement component to the movement
of the respective drive plates 66 and 68 about the axis o~
rotation of the shafts 38 and 40. By designing the eccen-
tric shafts accordingly, the rotational speed of shafts 38
and 40 can be varied while the projectiles are being trans-
ported from the respective inlet openings of the spacing
unit 28 to the outlets thereof.
Depending upon the number of inlet openings in the
spacing unit 28, the drive pinion 70 is so constructed with
eccentric shaft portions that the projectiles 16 are moved
at a ~aster speed at the outlet portion of the spacing unit
28 as compared to their speed upon entering unit 28 at the
inlet openings thereof. This causes the space between ad
jacent projectiles to be increased proportionately. By co-
ordinating such increase in angular speed with the relative
position of the retainers 36 on the respective shafts 38 and
40~ a ~pace is developed between adjacent projectiles at
~z~
at each level, which space is aligned with one of the pro-
jectiles at the other level. This enables the several lev-
els of projectiles to be merged subsequently into a single
row of projectiles with the proper spacing therebetween.
The present invention will be better understood
and appreciated from the following mathematical description
and the kinematic diagram of Figure 9.
Symbol Description Example
Value
Sl Outlet item spacing, inches 2.1
fl Outlet feed rate, items/second 30
n Number of inlet rows 2
So Inlet item spacing, inches 1.5
fo Inlet feed rate~ items/second 15
Vl Outlet item velocity, inches/second 63
Vo Inlet item velocity, inches/second 22.5
Velocity ratio = Yl/Vo 2.B
p Angle between inlet(s) and outlet, degrees 180
m Number of retainer positi~ns (per row) 3
~ Angular position of gear 54, degrees variable
20 9 Angular velocity of gear 54, rev/sec
~ Angular acceleration of gear 54, (ass~ zero) 0
~ Angular velocity of pinion 70, rev/sec -10
d Pitch diameter of pinion gear 70f, inches 1.5
D Pitch diameter of ring gear 80a, inches 4.5
25 Z Distance between retainer shaft 38 & 40 ~ and
pinion 70 ~, inches 1.5
Q Pinion offset (distance between 70a ~ and
70c~)~ inches .25
e Mechanism eccentricity = ~ 6
30 Angular position of retainer 36a, degrees varia~le
8 max
~ Angular velocity of retainer 36a, rev/sec 5 avg
2~ min
Angular acceleration of retainer 36a,ra~/sec llb86 ma~
~L79L~
-12-
R Pitch radius of retainer 36a, inches 1.253
: ~ distance between 36a and shafts 38 h 40 )
The design problem generally begins with given values
for the outlet item spacing (Sl), the outlet feed rate ~fl),
the number of inlet rows (n) and the inlet item spacing (So).
~ For this example the respective values are 2.10 inches, 30
items/second, 2 rovs and 1.50 inche~. The following para-
meters are immediately calculable.
-
Inlet feed rate
10fo - nl = 30 = 15 items/second
:` Outlet item velocity
Vl flSl = 30 x 2.10 = 63.00 inches/second
Inlet item velocity
Vo = foSo = 15 x 1.50 = 22O50 inches~second
Velocity ratio
= Vl = 63.00 = ~.
Vo 22.50
Or
~ = nS= 2 x 2.10 = 2.80
Sol1.50
Depending upon the geometry re~uired, the designer
will have a desired value for the angle between the inlet
and outlet (p~ and may proceed to choose the number of re-
tainer positions (m). However he is restrained by the re-
~uirement that the mechanism repeats its cycle ev~ry 360/m
in order that the inlet and outlet velocities are the same
at all interfaces with the m cutouts (36a). By way of ex-
ample,
if m = 2 then p = 90 or ~70
m = 3 p = 60~ or 130 or 270
m = 4 p = 45 or 135 or 225 or 315
~LZ~7446
..
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the specific requirement being
p = 180 +360
m m
where i is either zero or a positive integer
It is further noted that it is usually desireable, in order
to obtain an efficient form for the cutouts 36a, to arrange
interface with the inlet to occur slightly past the minimum
velocity point (i.e., ~t a higher velocity), and to inter-
face with the outlet slightly past the maximum velocity
point (i.e., at a lower velocity). This will result in a
: small compensating adjustment to p.
However, for the purposes of this example, let us
assume that intexface at the inlet and outlet is to occur
at the minimum and maximum velocity points respectively,
and the desired value for p is 180. Therefore, m is chosen
to be 3 (i=l) and the speed of gear 54 (and the average
speed of shafts 38 & 40) is
~ = fl = 30 = 5 rev
m n 3x2 sec
Now pinion 70 must rotate m revolutions wi$h r~-
spect to gear 54, for every revolution of gear 54. Various
planetary gear arrangements are available to accomplish
this. The arrangement selected for this particular embodi-
ment results in rotation of pinion 70 opposite to that ofgear 54. Therefore, the rotational speed of pinion 70 is
~ = - (m-l) ~ = -28 = ~10 rev/sec
and the pitch diameter ratio of ring gear 80a to pinion
3~ 70f is
D = m = 3
Selecting d = 1.5 inches
D = md = 4.5 inches
Z = tD - d)/2 = 1.5 inches
~eferring to Figure 9, the e~uations of motion for the
~l74~;
spacing unit (retainer 36) are:
a = ~ - tan 1 ~sin (m~)
Le + cos(m~)~
a = ~1 - m (e cos(m~) + 1)
L e2 + 2e cos (m~) + 1 J
a = m2 e sin(m3) (e2 - 1) (2 )~
~=-O) ~e2 + 2e cos~m~) ~ 1)2
The maximum and minimum velocities are:
a max = jl+ m
l e-lJ
a min = [1 m ¦ O
The minimum velocities occur at ~ = 0 and multiples of
360, and the maximum velocities occur at ~ = 180 plus
m m
increments of 360o
m
The required velocity ratio is
1' = a max = e2 + em + (m-l)
a min e2 _ em + (m-l)
Solving for the desired value of ~ = 2.8 yields
e = 6
Q = Z/e = .25 inches
a max = 8
a min =
a max = 8 rev/sec
& min = 26 rev/sec
R = Vo = Vl = 1.253 inches
2~ a min 2~ a max
7~
-15-
Peak angular accelerations v~cllr ~t:
~ = m cos -l L~ (e24+l)~+2]
(and also at ~urther increments of 3~0/m)
The peak accelerations are:
~ max - ~1686 rad/sec2 at Q = 41.13
oo
a min = -1686 rad~sec2 at ~ - 78.g7
The peak tangential acceleration imposed on the item is:
~o
At max = R max = 5.47 gees
386
The peak radial acceleration imposed on the item is:
o )2
max = 386 B.20 gees
The above analysis allows one skilled in the art to forsPe
many useful permutations of th:is invention. A more detailed
analysis which includes the ef~ects of friction and pressure
angles shows the mechanism to be capable of extremely high
(although not infinite of course) outlet item velocities
(Vl). Further, the mechanism may be configured to acc~mo-
date a zero ~or even negative) inlet item velocity. Thezero inlet velocity case is of particular interest ~or
cross-feed applications where items are to be introduced
into the inlet perpendicular to the direction of motion
rather than tangentially. In this configuration the mecha-
anism exhibits characteristics similar to a Geneva drive
with ~exo dwell. By way of illustration, suppose the design
parameters of the above example are adopted except the de-
sired inlet velocity is taken to be zero and the outlet item
spacing i5 taken to be 4O0 inches. ~her~fore-
Sl = 4.0 inches
fl = 30 items/sec
- 2
a6
-16-
So = O
fo = 15 items/sec
Vl = 120 ips
Vo = O
~ = infinity
Q = 5 rev/sec
d = 1.5 inches
D = 4,5 inches
- ~ = 1.5 inches
e = m-l = 2
Q = Z/e = d/2 = .75 inches
max = (1 + m ) ~ = 4 8 = 20 rev/sec
~min = 0
R = 120 = .955 inches
2 ~ x 20
~max = + 11,988 rad/sec2 @ ~ = 52.36
amin = 11,988 rad/sec2 @ ~ = 67.63
At max = 29.7 gees
AR max = 39.1 gees
The motion of eccentric shaft portion 70c of pinion 70 is
transmitted to the drive plate 66 via a journal bearing in-
terface between eccentric shaft portion 70c and bushing 76
plus a sliding interface between bushing 76 and dri~e plate
66. Efficiency and power transmission may be readily im-
proved by providing a connecting rod with anti-frietion
bearings between pinion eccentric 70c and drive plate 660
This of course will complicate the equations of motion but
does not significantly change the kinematics of the mechan-
ism.
Referring now to Figure 7 of the drawings, merger
unit 30 comprises an upper frame member 100 and a lower
~rame member 102. The upper frame member is provided with
a suitable opening for retaining a bearing 104 for receiving
a drive shaft 106. Such shaft is formed with an intermedi-
ate portion 106a for receiving the inner race of bearing
-17-
104, and a splined end portion 106b for non-rotably receiv-
ing the drive gear 56. The extreme end portion of shaft
106 is provided with fastening threads 106c for receiving
a fastening nut 110. Shaft 106 is further provided with a
5 mounting portion 106d.
In similar fashion, lower framP member 102 is pro-
vided with a through opening for receiving a bearing 112
which carries a rotatable shaft 114 having a splined portion
- 114a for non-rotatably receiving a gear 116~ Shaft 114 is
also provided with a threaded end portion 114b for receiv-
ing a fastening nut 120. A mounting portion 114c is formed
integrally with shaft 114.
Fixed to the mounting portion 106d and 114c by
means of bolts 1;22 at the top and ~ottom of unit-30, is a
rotor 124 having eight vertically extending channels 124a
provided by radially outwardly extending arms or partitions
124b. As shown most particularly in Figure 3 of the draw-
ings, each of such radial extending partitions 124b is form-
ed with a pair of vertically extending grooves or slots as
shown at 126 and 128.
As shown most particularly in Figure 3 and 7 of
the drawings 7 the upper portion of the merger unit 30 is
provided with four vertically movable projectile holders
130, one for every other one of the aforementioned channels
124a formed in rotor 124 as shown in Figure 3. Each such
holder comprises a back portion 132 and an arcuate inter-
mediate portion 134 as well as an enlarged lower portion
132a which is provided with a slot or opening 132b for re-
ceiving the lowermost edge of a projectile 16. The arcuate
intermediate portion 134 is operable to receive and cradle
the intermediate portion of the projectile.
The upper portion of member 132 is formed with an
offset 132c which carries a horizontally disposed rotatable
cam follower 136.
-18-
In like fashion, the lower section or level of the
merger unit 30 is provided with four holders 140 having an
arcuate intermediate portion 142 and a lower portion 140a
which is formed with a groove or cutout 140b for receiving
5 the lower edge of the projectile. Holder 140 is formed at
its lower end portion with an offset 140c which carries a
horiæontally disposed rotatable c~m follower 144.
- A cylindrical outer housing 146 is bolted to upperframe member 100 and lower frame member 102, thus forming
the primary structure of merger unit 30~ An upper hori20n-
tally disposed U-shaped endless track 148 is fixed to the
inner surface of such cylindrical outer housing 146 with
varying elevation as shown in Figure 7. The horizontally
disposed cam follower 136 is positioned in track 148 so as
the rotor is rotated by gear 116 through shaft 114, the
holders 130 are caused to move vertically within the respec-
tive channels 124a of the rotor. The four upper holders
130 have their upper and lower portions slidably fitted
within the slots 126 and 128 of the partitions 124~. Thus,
by rotating the rotor approximately one hundred eighty de-
grees about its axis, the individual projectiles 16 are
moved axially downward to an intermediat~ position, hal~-
way between the upper and lower levels of the merger unit 30,
In like fashion, a lower endless channel 150 is
~ixed to the inner cylindrical surface of cylindrical outer
hou~ing 146, at the lower portion thereof. This enables the
four lower projectile holders 140 to be cammed upwardly as
the rotor is rotated about its axis, to the same interme-
diate position as aforedescribed.
The embodiment presented herein is intended to
provide ~ingle row output at an intermediate position exact-
ly halway between the two axially spaced input rows. Thus
endless tracks 148 and 150 are identical, as well as cam
~ollowers 136 and 1440 However, output a~ any other desired
~79L9~
--19--
position is readily obtained by varying the respective pro-
portions of the two tracks.
From such intermediate position, as shown in Fig-
ure 7, the projectiles are successively transferred to a
transport mechanism including a rotatable shaft 160, the
upper end portion of which is carried by a bearing 162 with-
in an appropriate portion of the frame of the merger unit 3n~
The lower portion of shaft 160 carries a pair of gears 166
- and 168 and is mounted in a bearing 170 within frame member
102. Gear 168 is caused to mate with gear 116 to insure
that shaft 160 rotates in accordance with the rate of rota-
tion of the rotor of merger unit 30.
Shaft I60 comprises a pair of retainer members
172 whereby the projectiles 16 are removed from the merger
- 15 unit 30 at the predetermined location.
- As shown most particularly in Fiyures 1 and 5 of
the drawings, a gear member 55 is formed integrally with
gear 54 to drive a gear member 180 which is carxied by a
shaft in the storage compartment 12. Thus, the drive mech-
anism for the sparing unit 28 and merger unit 30 is util-
ized to drive the endless chain within the storage compart-
ment 12 so that all of the components of the system are
properly timed and roordinated. It is thus seen that the
present invention provides a mechanism for sequentially tak-
ing a plurality of like objects from a storage compartmenand feeding them to a predetermined location in a rapid and
effective manner.
Although I have shown and described certain spe-
cific embodiments of my invention, I am well aware that many
modifications thereof are possible~ The invention, there-
fore, is not to be restricted except insofar as is necessi-
tated by the prior art and by the spirit of the appended
Claims~
