Braiding machine eyelet tube support and drive mechanism

A braiding machine comprises a frame, a plurality of rotors on the frame and rotatable about rotor axes arranged about a braiding axis, drive gears for rotating adjacent ones of the rotors in opposite directions, and a plurality of strand shuttles which are driven by the rotors along a sinuous path in a given direction about the braiding axis. Adjacent ones of said rotors have transfer points for sequentially transferring a shuttle from a preceding rotor to a succeeding rotor with respect to the direction of the path, and the rotors and shuttle include interengaging retaining and escapement members by which the shuttle is moved with the preceding rotor toward the transfer point and then with the succeeding rotor away from the transfer point. A shuttle cam extends about the braiding axis, and cam follower rollers on the shuttle engage the cam for controlling the angular position of the shuttle relative to the preceding and succeeding rotors as the rotors move the shuttle through the transfer point therebetween.

BACKGROUND OF THE INVENTION 
The present invention relates to the art of braiding machines and, more 
particularly, to an improved arrangement for supporting and transporting 
strand eyelet tubes along a sinuous path about a braiding axis. 
Braiding machines are of course well known and are used, for example, to 
braid strands of materials such as steel, stainless steel, bronze, 
polyester, nylon, arramed, carbon fibers, and the like around a tubular 
substrate such as a flexible tube in connection with producing high 
pressure hydraulic or other types of pressure resisting hose. The braiding 
machines can also be used to braid many other products such as sewing 
threads, sutures, fishing line, ropes of many types, fashion textiles, 
cables for electrical and electronic use, lifting cables, and many other 
such products. 
One type of braiding machine used for producing products of the foregoing 
character is known as a maypole or horn gear type braider such as that 
shown in U.S. Pat. No. 3,783,736 to Richardson, the disclosure of which is 
hereby incorporated herein by reference for background purposes. In 
machines of the latter type, bobbin or strand carriers are moved by horn 
gears or notched rotors along sinuous paths around the braiding point or 
axis. Adjacent ones of the rotors rotate in opposite directions, whereby 
half of the carriers move along a sinuous path in one direction about the 
braiding axis while the other half of the carriers move along a sinuous 
path in the opposite direction. Each path runs radially inwardly and 
outwardly of the braiding axis and the two paths cross one another at each 
alternating direction, whereby the strands leaving the bobbins are 
interwoven as they converge to the braiding point. Such horn gear type 
braiding machines are limited in speed due to structural complexity and 
sliding friction between the component parts thereof and are subject to 
frequent and costly maintenance as a result of the number and structural 
interrelationship between the component parts. Moreover, machines of this 
type are structurally complex and require a high level of precision with 
respect to the manufacturing of the parts and the obtaining and 
maintaining of alignment and other structural interrelationships 
therebetween, whereby manufacturing costs are undesirably high as are the 
time and expense of maintenance required to maintain the high level of 
precision. Moreover, the restricted braiding speed reduces production rate 
and, thus, increases the cost of production. 
Another type of braiding machine used for the production of products of the 
foregoing character is a rotary braiding machine such as that shown in my 
U.S. Pat. No. 4,275,638 issued Jun. 30, 1981 and the disclosure of which 
is hereby incorporated herein by reference for background purposes. In a 
machine of the rotary type, there are axially spaced sets of inner and 
outer bobbin carriers which are rotated about the braiding point or axis 
in opposite directions, and a set of strand deflectors located between the 
carrier sets which cause the strands from one of the carrier sets to cross 
the path of the other, thus interweaving the strands. In my aforementioned 
patent, the strands from one set of bobbin carriers are guided axially 
past the other set of bobbin carriers by individual elongated eyelet tubes 
which are supported axially between the two carrier sets and driven along 
a sinuous path about the braiding point and across the path of the strands 
of the other set of bobbin carriers to achieve the interweaving of the 
strands about the braiding axis. The eyelet tubes have three axially 
spaced apart support points adjacent one end thereof, whereby undesirable 
forces can be imposed on the eyelet tubes during the driving thereof along 
the sinuous path about the braiding axis. Accordingly, manufacturing 
precision is required in an effort to minimize the imposition of such 
forces while, at the same time, providing the necessary stability with 
respect to supporting the eyelet tubes as they are driven along the 
sinuous path about the braiding axis. Moreover, even with such control in 
connection with manufacturing the component parts, braiding speed of the 
machine is restricted. The forces imposed on the eyelet tube and other 
component parts of the drive therefore are both radial and sliding 
frictional forces. The latter results from parts of the drive arrangement 
being fixed and sliding displacement of the eyelet tubes relative thereto, 
and the radial forces can impose bending loads on the eyelet tubes as a 
result of the three axially spaced points of engagement of the eyelet 
tubes with the support and drive components. Precision in manufacturing 
increases both manufacturing and maintenance costs, and restricted 
braiding speed reduces production rate and, accordingly, increases the 
cost of production. 
The improvement according to the present invention is illustrated and 
described herein in conjunction with the braiding machine disclosed in my 
aforementioned patent but, as will become apparent in connection with the 
disclosure herein, the invention is equally applicable to horn gear type 
braiding machines. 
SUMMARY OF THE INVENTION 
In accordance with the present invention, each strand of at least one set 
of strands to be moved along a sinuous path about a braiding axis is 
supported for such movement by a shuttle component which is transported 
along the path by a plurality of rotors arranged in a circular pattern 
about the braiding axis and mounted on the machine for rotation about 
corresponding rotor axes. The rotors and shuttles are structured and 
structurally interrelated in a manner which minimizes the imposition of 
undesirable forces therebetween, eliminates the potential of imposing 
bending forces against the shuttles and eyelet tubes supported thereby and 
eliminates sliding frictional forces therebetween. Accordingly, an 
appreciably higher braiding speed and thus a higher production rate is 
obtainable than with braiding machines heretofore available. Moreover, the 
rotors and shuttles are structurally simple, whereby production and 
maintenance costs are reduced. 
In accordance with one aspect of the invention, a shuttle is interengaged 
with a rotor for rotation therewith about a rotor axis by interengaging 
retainer and escapement components respectively on the rotor and shuttle. 
A cam track extends about the braiding axis, and a follower arrangement on 
the shuttle engages the cam track to relatively position the shuttle and 
the rotors such that the shuttle is transferred from a preceding to a 
succeeding rotor with respect to the direction of the path. More 
particularly in this respect, interengagement between the cam track and 
follower at the transfer point between adjacent rotors operates to release 
the escapement component on the shuttle from the retainer component on the 
preceding rotor while engaging another escapement component on the shuttle 
with a retainer component on the succeeding rotor. 
In accordance with another aspect of the invention, each of the rotors is 
provided with a corresponding drive gear axially spaced therefrom and the 
drive gears of the rotors are in meshing interengagement with one another, 
whereby rotation of one of the drive gears imparts rotation to the others 
for adjacent ones of the gears and thus the corresponding adjacent rotors 
to rotate in opposite directions relative to one another. Each shuttle 
extends axially between a rotor and its drive gear, and the drive gears 
and shuttles are provided with interengaging retainer and escapement 
components which, in the manner described above, interengage for the 
shuttle to rotate with a rotor and its drive gear. Likewise, as described 
above, the escapement component on the shuttle disengages the retainer 
component on a preceding gear and another escapement component engages the 
retaining component on the succeeding gear at the point of transfer of the 
shuttle therebetween. Accordingly, the shuttle and an eyelet tube 
supported thereby is stabilized at the two axially spaced points defined 
by the rotor and its drive gear with no sliding frictional force 
therebetween and without the potential for applying a bending force 
thereagainst. 
Preferably, the follower arrangement on the shuttles and the shuttle 
retaining components on the rotors and gears are roller elements 
respectively in rolling engagement with the cam track and flanges on the 
shuttles which provide the escapement components. This arrangement 
advantageously reduces wearing interengagement between the component 
parts, thus optimize the life thereof and minimizing downtime for 
maintenance or replacement of worn parts. 
It is accordingly an outstanding object of the present invention to provide 
an improved drive arrangement for transporting a strand along a sinuous 
path about the braiding point or axis of a braiding machine. 
Another object is the provision of a drive arrangement of the foregoing 
character which minimizes the imposition of undesirable forces against and 
between the component parts thereof. 
A further object is the provision of a drive arrangement of the foregoing 
character which enables operation of a braiding machine at a higher 
braiding speed than heretofore possible. 
Yet another object is the provision of a drive arrangement of the foregoing 
character in which the component parts are structurally simple and 
structurally interrelated in a manner which minimizes wear therebetween so 
as to optimize the life thereof and reduce downtime for maintenance or 
replacement of worn parts. 
Still, a further object is the provision of a drive arrangement of the 
foregoing character wherein a strand to be moved along the sinuous path is 
supported by a shuttle which is moved along the path by a plurality of 
rotors arranged circumferentially about the braiding axis and wherein the 
shuttle and rotors are structured and structurally interrelated for a 
shuttle to rotate with and to be transferred from a preceding to a 
succeeding rotor in the direction of the path efficiently and with minimal 
frictional engagement therebetween, thus to promote a longer life for the 
component parts while enabling a higher speed operation of the machine 
than heretofore possible. 
Still another object is the provision of a drive arrangement of the 
foregoing character in which each rotor is rotated by a corresponding 
drive gear and wherein each rotor and drive gear and each shuttle have 
interengaging retainer and escapement component to stabilize the shuttle 
during movement thereof along the sinuous path and to achieve such 
movement with minimal forces against the component parts of the drive 
arrangement. 
Another object is the provision of a drive arrangement of the foregoing 
character wherein the position of a shuttle relative to a given rotor is 
controlled by interengaging retainer and escapement components 
respectively on the rotor and shuttle, a cam track extending about the 
braiding axis and having a portion extending partially about each rotor 
axis, and a cam follower arrangement on the shuttle engaging the cam track 
in a manner whereby a shuttle engages and rotates with a rotor about its 
axis toward a succeeding rotor along the path and is released from the one 
rotor and engaged with the succeeding rotor at the point of transfer 
therebetween for movement with the succeeding rotor about its axis.

DESCRIPTION OF A PREFERRED EMBODIMENT 
With reference now to the drawings, wherein the showings are for the 
purpose of illustrating a preferred embodiment of the invention only and 
not for the purpose of limiting the invention, FIG. 1 illustrates the 
lower portion of a rotary braiding machine and corresponds to FIG. 1 in my 
aforementioned patent modified to incorporate a strand eyelet drive 
arrangement in accordance with the present invention. Accordingly, 
reference can be had to my earlier patent for greater detail regarding the 
structure and operation of the machine which is basically the same except 
for the eyelet drive arrangement. Briefly, the machine comprises a frame 
A, an outer carrier B supporting a plurality of strand holding bobbins C, 
an inner carrier comprising a pair of axially spaced plates D and a 
plurality of pairs of bobbin support members E, each pair supporting a 
strand bobbin F therebetween. A plurality of eyelet tubes G extend from 
adjacent outer carrier B axially past the inner carrier and receive 
strands S from bobbins C on carrier B. Strands S emerge from the 
right-hand ends of eyelet tubes G and converge on a braiding point H which 
in the illustrated embodiment is the outer surface of a tubular member I 
which moves axially from left to right through the braiding machine. 
Strand guides SG guide strands S1 from each of the bobbins F for the 
latter strands to converge on braiding point H. 
In operation, the bobbin carriers rotate in opposite directions about the 
braiding point, and eyelet tubes G are driven about the braiding point 
along a sinuous path moving strands S radially inwardly and outwardly and 
circumferentially relative to strands S1 so as to move strands S over and 
under the strands S1 so that the strands are braided at the braiding point 
H. Bobbin carrier B and the carrier defined by support plates D as well as 
the bobbin support members E are adapted to be driven in the manner 
described in my aforementioned patent, although the drive train may be 
different in some respects from that shown in the patent. In particular, 
as will become apparent hereinafter, the eyelet tube drive arrangement 
shown in the patent is eliminated and replaced by the drive arrangement 
according to the present invention which is described in detail 
hereinafter. As in my earlier patent, fame A includes a cylindrical frame 
member 10 having an axis 12 with respect to which tubular member I is 
coaxial and which accordingly provides a braiding axis with respect to 
braiding point H. Accordingly, it will be appreciated that reference 
herein to one of the braiding point and braiding axis is synonymous with 
the other. Bobbin carrier B is supported for rotation on frame member 10 
by bearings 14, and frame member 10 includes a coaxial portion 16 on which 
carrier support plates D are rotatably mounted by bearings 18. Carrier B 
and carrier plates D are respectively rotated by a gear 20 and a pair of 
gears 22 mounted on a shaft 24 which is adapted to be driven by a motor M. 
Basically, the outer and inner bobbin carriers are structured, supported 
and driven as shown and described in my aforementioned patent, whereby 
reference may be had to the latter patent for details in this respect. 
In accordance with the present invention, an improved support and drive 
arrangement is provided for moving eyelet tubes G about braiding point H 
and along a sinuous path which moves strands S radially inwardly and 
outwardly and across and under strands S1 so that the strands S and S1 are 
braided at braiding point H. The improved drive arrangement is designated 
generally by the numeral 30 in FIG. 1 and comprises a plurality of eyelet 
tube shuttles 32, a corresponding plurality of rotor and drive gear units 
34, and a control cam 36. As will become apparent hereinafter, alternate 
ones of the rotor and drive gear units 34 are mounted on an inner frame or 
support plate 38 extending about and suitably secured to cylindrical frame 
member 10, such as by welding, and the ones of the rotor and drive gear 
units 34 alternating with those on plate 38 are mounted on a frame plate 
40 extending about plate 38 in radially outwardly spaced relationship 
thereto. More particularly with regard to the cam and frame plate 
structure, which is best illustrated in FIG. 2, control cam 36 is defined 
by a plurality of identical cam segments 42 mounted on outer frame plate 
40 by a plurality of machine bolts 44. Preferably, the ends of adjacent 
segments 42 abut one another and are recessed to provide a circular 
opening therebetween which receives a dowel 46 on plate 40 by which the 
segments are accurately aligned relative to one another. Each of the 
segments has a cam surface which is described in greater detail 
hereinafter, and the cam surfaces of the several cam segments together 
provide a serpentine or sinuous cam track extending about the machine or 
braiding axis 12. Inner frame plate 38 is cut to provide an outer surface 
48 which corresponds generally to the contour of the cam track, and frame 
plate 40 is cut to provide an opening therethrough which generally 
corresponds to the contour of the cam track. Surface 48 is spaced radially 
inwardly of the cam track to provide a sinuous path P therewith which 
extends about the braiding point or axis. Each of the cam segments 
includes a lobe 50 extending radially inwardly with respect to machine 
axis 12, and each lobe includes an opening 52 for receiving the bearing 
housing of a rotor and drive gear unit mounted on plate 40 therebehind as 
set forth more fully hereinafter. Plate 38 includes a plurality of lobes 
54 extending radially outwardly of axis 12 between adjacent ones of the 
lobes 50, and each of the lobes 54 includes an opening 56 therethrough for 
the bearing housing of a rotor and drive gear unit mounted thereon. In the 
embodiment illustrated, there are a total of twelve lobes 50 and 54, and 
it will be appreciated that the axes 52a of openings 52 and 56a of 
openings 56 are equally radially spaced from axis 12 and are equally 
spaced apart circumferentially thereabout. 
As best seen in FIGS. 2 and 3 of the drawing, and with respect to the 
counterclockwise direction of path P shown in FIG. 2, the cam surface of 
each cam segment 42 has an entrance portion 58, first and second entrance 
ramp portions 60 and 62, respectively, a crown portion 64, first and 
second exit ramp portions 66 and 68, respectively, and an exit portion 70. 
Entrance portion 58 and first entrance ramp 60 have a uniform radius of 
curvature with respect to axis 56a of opening 56 through lobe 54 adjacent 
the entrance end of the cam segment, and exit portion 70 and second exit 
ramp 68 have a uniform radius of curvature with respect to axis 56a of 
opening 56 through lobe 54 adjacent the exit end of the cam segment. 
Second entrance ramp 62, crown portion 64 and first exit ramp 66 have a 
uniform radius of curvature with respect to axis 52a of opening 52 in lobe 
50 of the cam segment, and the lower or radially outwardly extending ends 
of second entrance ramp 62 and first exit ramp 66 are contoured to 
smoothly merge into the corresponding one of the arcuate entrance and exit 
portions 58 and 70. As will be appreciated from FIG. 3, and for the 
purpose which will become apparent hereinafter, first entrance ramp 60 and 
second exit ramp 68 are axially offset with respect to one another, 
whereby second entrance ramp 62 and first exit ramp 66 are likewise 
axially offset with respect to one another. The contours of ramps 60 and 
68 provide for first entrance ramp 60 to abruptly intersect crown portion 
64 along a line 60a defining the exit end of ramp 60 and for second exit 
ramp 68 to abruptly intersect crown portion 64 along a line 68a defining 
the entrance end of ramp 68. The cam surface of each of the cam segments 
42 is identical, whereby it will be appreciated that the foregoing 
structure and structural interrelationship between the cam surface 
portions are applicable to each of the cam segments with respect to the 
direction of path P shown in FIG. 2. 
As will be appreciated from FIG. 1, each of the rotor and drive gear units 
34 comprises a bearing housing 72 which rotatably supports a shaft 74 
having a rotor 76 mounted on one end thereof for rotation therewith and a 
drive gear 78 mounted on the other end thereof for rotating the shaft as 
set forth more fully hereinafter. Rotor and drive gear units 34 are 
mounted on the inner or rear sides of frame plates 38 and 40 and in this 
respect, as will be appreciated from the unit 34 shown mounted on plate 38 
in FIG. 1, the rotor and drive gear units include a front portion and 
flange, not designated numerically, respectively extending through an 
opening 56 and engaging behind the frame plate, and the unit is secured 
thereto such as by a plurality of machine bolts 80 extending through 
openings therefor in the flange. As best seen in FIGS. 4 and 5, each of 
the rotors 76 includes an apertured hub 82 receiving the corresponding end 
of shaft 74. A key 84 interengages the rotor and shaft for the rotor to 
rotate with the latter, and the rotor is axially retained on the shaft by 
means of a nut 86 on the threaded outer end of the shaft. Rotor 76 further 
includes a rotor arm 88 welded or otherwise secured to hub 82 and 
extending tnansverse to the rotor axis as defined by the axis of shaft 74. 
Arm 88 has axially outer and inner sides with respect to the outer end of 
shaft 74, and the radially outer ends of the rotor arm are defined by 
support blocks 90 extending axially inwardly of the inner side of the arm 
and having diametrically opposed, outwardly open C-shaped recesses 92 
therein. As will become apparent and described in greater detail 
hereinafter, recesses 92 are adapted to operatively interengage with the 
shuttles of the machine to transport the latter along path P about 
braiding axis 12. Recesses 92 are of uniform radius with respect to a 
centerline 94 parallel to the axis of shaft 74 and, for the purpose set 
forth hereinafter, the recesses have an angular extent of slightly less 
than 180.degree. and the radially outer ends of the rotor arm are defined 
by surfaces 96 extending laterally outwardly from recesses 92 and inclined 
radially inwardly of the rotor arm at an angle of about 10.degree. 
relative to a plane through centerline 94 which is transverse to a line 
bisecting recesses 92. Also for the purpose which will be described in 
detail hereinafter, the axially inner side of rotor arm 88 is provided 
radially inwardly adjacent each of the recesses 92 with a shuttle 
retaining roller 98. Rollers 98 are preferably of steel and are rotatably 
mounted on the rotor arm by headed axle bolts 100 having shanks threadedly 
interengaged with openings therefor in the rotor arm, whereby each roller 
is rotatable about a roller axis provided by the corresponding axle bolt. 
As will be appreciated from FIGS. 1 and 6-8 of the drawing, each eyelet 
shuttle unit 32 includes a tubular body member 102 which is circular in 
cross section, has an axis 103, and receives a corresponding eyelet tube 
G. Each shuttle unit further includes escapement arms 104 and 106 axially 
inwardly adjacent the opposite ends of the body member and a control arm 
108 axially inwardly adjacent the escapement arm 104. As will be 
appreciated from FIG. 1, body member 102 extends through the radial space 
between the inner and outer frame plates 38 and 40, escapement arms 104 
and 106 are axially adjacent rotors 76 and drive gears 78, respectively, 
and control arm 108 includes a pair of axially offset follower rollers 110 
and 112 which engage the cam track of control cam 36. In the manner 
described more fully hereinafter, the escapement arms and control arm 
operatively interengage with the rotors, drive gears and control cam to 
support and transport the shuttles about path P. 
As best seen in FIGS. 6-8, each of the escapement arms 104 and 106 includes 
an arm plate 114 apertured to receive body member 102 and mounted thereon 
such as by welding. Arms 114 extend transverse to axis 103 and are in 
alignment with one another in the direction between the opposite ends of 
the body member. The radially outer ends of each arm are provided with an 
escapement cam 116 secured thereto such as by welding and extending 
axially outwardly therefrom with respect to the corresponding end of the 
body member. Each of the arm members 114 is spaced axially inwardly of the 
corresponding end of body member 102 to provide a rotor engaging surface 
118 at the end on which escapement arm 104 is mounted and a drive gear 
engaging surface 120 at the end on which escapement arm 106 is mounted. 
Escapement cam blocks 116 of escapement arm 104 are provided with 
diametrically opposed arcuate escapement cam surfaces 122 which are convex 
relative to rotor engaging surface 118, and escapement cam blocks 116 of 
escapement arm 106 are provided with diametrically opposed arcuate 
escapement cam surfaces 124 which are convex with respect to drive gear 
engaging surface 120 of the body member. As will be appreciated from FIG. 
7, the diametrically opposite sides of arm member 114 of escapement arm 
106 are provided with threaded apertures therethrough and through body 
member 102 to receive set screws 125 by which eyelet tube G is mounted on 
the shuttle against displacement relative thereto. 
Control arm 108 is axially inwardly adjacent escapement arm 104 and is 
transverse to axis 103 and orthogonal with respect to escapement arms 104 
and 106. The control arm provides for follower rollers 110 and 112 to be 
axially offset from one another for the reason set forth hereinafter, and 
the mounting arrangement for this purpose includes a mounting arm 126 
welded on body member 102 and common to both follower rollers, and arms 
128 and 130 welded on body member 102 on axially opposite sides of arm 126 
and extending outwardly in laterally opposite directions from the body 
member. Follower roller 110 is received between arm 128 and the 
corresponding portion of arm 126 and is rotatably mounted thereon by an 
axle bolt and nut assembly 132, and follower roller 112 is received 
between arm 130 and the corresponding portion of arm 126 and is rotatably 
mounted thereon by an axle bolt and nut assembly 134. Preferably, as best 
seen in FIG. 6 in connection with follower roller 110 and in FIG. 8, each 
of the follower rollers comprises a hub 136 of aluminum and a tire or 
thread 138 of molded polyurethane mounted on the outer periphery thereof. 
The axial offset between follower rollers 110 and 112 provides for roller 
110 to engage and roll along first entrance ramp 60 and first exit ramp 
66, and for roller 112 to engage and roll along second entrance ramp 62 
and second exit ramp 68 to control the corresponding shuttle in the manner 
and for the purpose set forth more fully hereinafter. 
As will be appreciated from FIGS. 1 and 7 of the drawing, each eyelet tube 
G terminates axially outwardly of escapement arm 106 adjacent the sides of 
drive gears 78 facing bearing housings 72 of the rotor and drive gear 
units 34 and include a tubular eyelet extension G1 which, in the manner 
set forth more fully hereinafter, axially spans the drive gears and 
provides an inlet to the eyelet tube for the corresponding strand S. Each 
tubular eyelet extension includes a tubular shank 135 having an inner end 
threadedly interengaged with a threaded bore provided therefor in the end 
of the eyelet tube, an unthreaded intermediate portion having an axial 
length slightly greater than the thickness of drive gears 78, and an outer 
end in the form of a radially outwardly extending flange 137 which 
facilitates screwing the extension into and out of engagement with the 
eyelet tube. While not shown, flange 137 can have peripheral flats to 
accommodate a wrench or other tool for rotating the extension. Preferably, 
the entrance end 139 of the eyelet extension is rounded to accommodate the 
movement of strand S thereacross. 
Referring now to FIGS. 9 and 10 of the drawing, the side of each drive gear 
78 facing bearing housing 72 of the corresponding rotor and drive gear 
unit is provided with diametrically opposed outwardly open arcuate shuttle 
engaging recesses 140 and a shuttle retaining roller 142 axially inwardly 
adjacent each of the surfaces 140. Surfaces 140 and rollers 142 correspond 
in contour, dimension and function to recesses 92 and rollers 98 of rotors 
76. Further, surfaces 140 and rollers 142 are in alignment axially of the 
rotor and drive gear unit with the recesses 92 and rollers 98 of the 
corresponding rotor. As will become apparent and described in greater 
detail hereinafter, recesses 92 and 140 and rollers 98 and 142 are adapted 
to operatively interengage respectively with rotor engaging surface 118 
and escapement arm 104 and with drive gear engaging surface 120 and 
escapement arm 106 of a shuttle unit 32 in connection with transporting 
the latter along path P and about the braiding axis of the machine. For 
the purpose set forth hereinafter, the teeth of drive gear 78 aligned with 
the diametrically opposed surfaces 140 are partially cut away radially and 
circumferentially to provide recesses 144 therein. Surfaces 140 and 
rollers 142 can be provided on gears 78 in any desired manner and, in the 
embodiment illustrated, are shown as a unitary component in the form of an 
apertured arm 146 similar to rotor arm 88 and which is received on shaft 
74 and secured to gear 78 by threaded fasteners 148. Surfaces 140 can be 
provided in support blocks 141 similar to blocks 90 on rotor arm 88, and 
retaining rollers 142 can be mounted on arm 146 by headed axle bolts 143 
corresponding to axle bolts 100 on the rotor arm. 
FIG. 11 schematically illustrates rotors 76 mounted on the lobes of frame 
plate 38 and cam segments 42 of control cam 36 in the manner described 
hereinabove in connection with FIGS. 1 and 2, and schematically 
illustrates shuttles 32 alternately in the position of transfer between 
preceding and succeeding rotors with respect to the direction of path P 
and the position immediately following the transfer from the succeeding 
rotor to the next succeeding rotor in the direction of the path. FIG. 12 
illustrates drive gears 78 of the rotor and drive gear units in meshing 
engagement with one another and with one of the gears 78 in meshing 
interengagement with a drive gear 150 which is shown as rotating 
counterclockwise, whereby the drive gear immediately driven thereby is 
rotated clockwise in FIG. 12. FIG. 12 is a view of the drive gears in the 
direction from left to right in FIG. 1, and the schematic illustration of 
FIG. 11 is with respect to viewing the rotors and shuttles in the 
direction from right to left in FIG. 1. The lowermost drive gear in FIG. 
12 which is driven by gear 150 corresponds to the lowermost rotor 76 in 
FIG. 11, whereby the latter rotates counterclockwise in FIG. 11 and 
provides a counterclockwise direction for path P relative to braiding axis 
12. In this respect, the intermeshing engagement between adjacent ones of 
the drive gears 78 imparts rotation to adjacent ones of the rotors in 
opposite directions relative to one another. In response to such rotation 
of the rotors, shuttle units 32 are transported along path P by the rotors 
and between transfer points at which a shuttle is transferred from a 
preceding to a succeeding rotor. Entrance ramps 60 and 62 and exit ramps 
66 and 68 of the control cam come into play in connection with follower 
rollers 110 and 112 to control the position of escapement arm 104 of 
shuttle 32 relative to retaining rollers 98 of the rotors during the 
approach of the shuttle to the transfer point on the entrance side of 
segment of the control cam and during approach of the shuttle to the 
transfer point on the exit side of the segment. Control of the shuttle in 
this respect will be described in greater detail hereinafter. 
Transportation of the shuttle along path P between transfer points on the 
entrance and exit sides of a cam segment will be understood from FIGS. 11 
and 13-15 and the following description thereof with reference to rotors 
R1, R2 and R3 and the shuttle 32 which is at the transfer point between 
rotors R1 and R2 and on the entrance side of a cam segment 42 in FIGS. 11 
and 13. In the latter Figures, rotor R1 is the preceding rotor and R2 the 
succeeding rotor with respect to the direction of path P and with respect 
to the transfer of shuttle 32 therebetween. When shuttle 32 is at this 
transfer point, follower roller 110 has reached edge 60a of entrance ramp 
60 and rotors R1 and R2 are substantially aligned relative to the axes of 
the drive shafts 72 thereof, whereby rotor engaging surface 118 of the 
shuttle is captured between opposed recesses 92 on the rotors. Further, 
escapement cam surfaces 122 on escapement arm 104 of the shuttle engage 
shuttle retaining rollers 98 on rotors R1 and R2, whereby the shuttle is 
stabilized with respect to rotor R1 and with respect to the transfer 
thereof to rotor R2. As will be appreciated from FIG. 13, follower roller 
112 is in alignment with entrance ramp 62 whereby continued rotation of 
rotor R2 clockwise from the position shown in FIG. 13 results in shuttle 
32 being interengaged with rotor R2 and moving therewith to the position 
shown in FIG. 14. Moreover, the shuttle is released from rotor R1 as rotor 
R2 moves clockwise and rotor R1 counterclockwise from the transfer point. 
In moving from the position shown in FIG. 13 to that shown in FIG. 14, 
shuttle 32 remains interengaged with rotor R2 by the uniform curvature of 
inlet ramp 62 and crest 64 of the cam track. As rotor R2 continues to 
rotate clockwise from the position shown in FIG. 14 to the position shown 
in FIG. 15, follower roller 110 engages exit ramp 66 as follower roller 
112 moves along crest 64. Accordingly, shuttle 32 remains interengaged 
with rotor R2 because of the uniform curvature of ramp 64 and exit ramp 66 
and, when rotors R2 and R3 reach the transfer point therebetween shown in 
FIG. 15, follower roller 112 is at entrance edge 68a of exit ramp 68. In 
connection with the approach to the transfer point on the exit side of the 
cam segment the clockwise rotation of rotor R2 and counterclockwise 
rotation of rotor R3 brings shuttle engaging surfaces 92 thereof into 
engagement with opposite sides of rotor engaging surface 118 on the 
shuttle. In connection with the approach and departure of shuttle 32 from 
the transfer points shown in FIGS. 13 and 15, the inclined end surfaces 96 
on the rotors facilitate the relative displacement of the rotors through 
the transfer point without interfering engagement therebetween. 
When adjacent rotors are in the positions for transferring a shuttle 
therebetween, such as shown in FIG. 13 for example, the end of the shuttle 
adjacent the corresponding rotor drive gears 78 interengages with the 
latter as shown in FIGS. 16 and 16A of the drawing. More particularly in 
this respect, shuttle receiving recesses 140 on the gears receive drive 
gear engaging surface 120 of the shuttle and escapement cam surfaces 124 
of escapement arm 106 of the shuttle interengage with shuttle retaining 
rollers 142 on the gears to support the shuttle and thus eyelet tube G 
during the transfer. FIG. 16 is looking at gears 78 in the direction from 
right to left in FIG. 1, whereby it will be appreciated with respect to 
FIG. 13 that the gears designated G1 and G2 in FIG. 16 correspond 
respectively to rotors R1 and R2. Furthermore, it will be appreciated from 
the foregoing description that when gears G1 and G2 rotate away from the 
position of transfer therebetween the shuttle remains interengaged with 
gear G2 through shuttle escapement cam surface 124 and the shuttle 
retaining roller 140 so as to rotate with the gear to the next transfer 
point. FIG. 16A is looking at gears 78 in the same direction as FIG. 16 
but from behind arm 146 and rollers 142. Accordingly, as will be 
appreciated from FIGS. 7, 9 and 10 and the preceding description herein 
with respect thereto, the end of body member 102 on which escapement arm 
106 is mounted, and the corresponding end of eyelet tube G terminate 
axially adjacent the front or outer side of drive gears 78, whereby the 
unthreaded portion of shank 135 of eyelet extension G1 extends across the 
teeth of the drive gear through the opposed recesses 144 in the teeth of 
adjacent ones of the drive gears which are aligned at the transfer point 
to provide a passageway thereacross for shank 135 and thus strand S as 
will be appreciated from FIG. 16A. 
As mentioned above, entrance ramps 60 and 62 and exit ramps 66 and 68 
operate in connection with follower rollers 110 and 112 to control the 
position of the escapement arm 104 of shuttle 32 relative to shuttle 
retaining rollers 98 of rotors 76 during the approach of shuttle 32 to the 
transfer point between preceding and succeeding rotors with respect to the 
direction of path P. Thus, in connection with the illustrations in FIGS. 
13-15, entrance ramps 60 and 62 control the position of escapement arm 104 
of shuttle 32 relative to retaining rollers 90 of rotor 92 as the shuttle 
approaches the transfer point between preceding rotor R1 and succeeding 
rotor R2. Similarly, exit ramp 66 and 68 control the position of 
escapement arm 104 of the shuttle relative to retaining rollers 98 and 
rotor R3 as the shuttle approaches the transfer point between preceding 
rotor R2 and succeeding rotor R3. More particularly in this respect, with 
reference to entrance ramps 60 and 62 FIGS. 17-19 of the drawing, FIG. 17 
schematically illustrates the position of shuttle 32 as it approaches the 
transfer point shown in FIG. 13. In this position of the shuttle, rotor 
engaging surface 118 thereof is received in one of the shuttle receiving 
recesses 92 of rotor R1 and the shuttle is interengaged for movement with 
rotor R1 about the axis of its shaft 72 by the interengagement between one 
of the escapement cam surfaces 122 on escapement arm 104 of the shuttle 
and a shuttle retaining roller 98 on the rotor. As further mentioned 
hereinabove, entrance ramp 60 has the same radius of curvature relative to 
the axis of rotor R1 as does entrance end 58 of the cam segment on which 
rotor R2 is mounted, and entrance ramp 62 has the same radius of curvature 
relative to axis 72 of rotor R2 as does crest 64 of the cam surface. Thus, 
as will be appreciated from FIG. 17, follower roller 110 engages entrance 
ramp 60 of the cam and maintains the shuttle in the interengage position 
with rotor R1 for movement therewith toward the transfer point. Moreover, 
this position of the shuttle relative to rotor R1 and movement of roller 
110 along ramp 60 allows movement of shuttle engaging recess 92 on rotor 
R2 and a shuttle retaining roller 98 thereon respectively into engagement 
with shuttle surface 118 and the other escapement cam surface 122 of 
escapement arm 104 of the shuttle when rotors R1 and R2 reach the transfer 
point therebetween shown in FIG. 13 and schematically in FIG. 18. At this 
point, follower roller 110 has reached exit edge 60a of entrance ramp 60 
and follower roller 112 has moved onto the lower end of entrance ramp 
portion 62, whereby it will be appreciated that continued rotation of 
rotor R2 in the clockwise direction and rotor R1 in the counterclockwise 
direction provides for follower rollers 110 and 112 of shuttle 32 to 
engage crest 64 and entrance ramp 62, whereby the shuttle remains 
interengaged with rotor R2 for movement therewith about the axis thereof 
to the position shown in FIG. 14. Further in connection with such 
movement, as will be appreciated from FIG. 19, rotor engaging surface 118 
of the shuttle is received in shuttle engaging recess 92 of rotor R2 and 
shuttle retaining roller 98 of the latter engages with an escapement cam 
surface 122 on escapement arm 104 of shuttle 32 to hold the shuttle 
engaging surface in recess 92. Further, as rotors R1 and R2 move away from 
the transfer point therebetween, the shuttle retaining roller 98 on rotor 
R1 disengages from escapement cam surface 122 with which it was previously 
engaged and the shuttle receiving recess 92 of rotor R1 moves out of 
engagement with rotor engaging surface 118 of the shuttle to release the 
shuttle for movement with rotor R2. As will be appreciated from the 
foregoing description with reference to FIGS. 17-19, when rotors R2 and R3 
reach the transfer point therebetween shown in FIG. 15, follower roller 
112 is at the entrance edge 68a of exit ramp 68, whereby continued 
rotation of rotor R3 counterclockwise and rotor R2 clockwise in FIG. 15 
results in the follower roller 112 engaging exit ramp 68 which has the 
same radius of curvature relative to the axis of rotor R3 as exit end 70 
of the cam segment, whereby shuttle 32 is released from rotor R2 and 
transferred to rotor R3 for movement therewith about the axis thereof to 
the next transfer point in the same manner as described hereinabove. As 
will likewise be appreciated from the foregoing description, the 
escapement arm 106 on the shuttle is controlled relative to shuttle 
retaining rollers 142 on drive gears 78 in the same manner as described 
above during movement of the shuttle to and through the transfer point 
between preceding and succeeding gears. 
While considerable emphasis has been placed herein on a preferred 
embodiment of the invention, it will be appreciated that many changes can 
be made in the preferred embodiment and that other embodiments can be 
devised without departing from the principals of the invention. In 
particular in this respect, it will be appreciated that a cam track can be 
devised which would enable the shuttle to shift as necessary for the 
transfer thereof between adjacent rotors through the use of a single 
follower, such a cam track for example including radially inner and outer 
portions interengaging with the follower. Further, it will be appreciated 
that the followers in the preferred embodiment could be other than 
rollers, the latter being preferred for minimizing sliding frictional 
interengagement and wear between the component parts. These and other 
modifications of the preferred embodiment as well as other embodiments of 
the invention will be apparent and suggested from the foregoing 
description of the preferred embodiment, whereby it is to be distinctly 
understood that the descriptive matter herein is to be interpreted merely 
as illustrative of the present invention and not as a limitation.