Note: Descriptions are shown in the official language in which they were submitted.
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LABELLING STATION FOR LABELLING OBJECTS, SUCH AS BOTTLES
BACKGROUND OF THE INV~NTION
1. Field of the Invention:
This invention relates to a labelling station for objects,
in particular bottles, with several stations located behind one
another along a track, comprising an adhesive or glue application
apparatus, a label supply station and a label transfer station.
The invention has at least one extracting element which can rotate
on a rotating support and be moved past the stations during each
rotation of the support.
The extracting element has an outwardly-curved receptacle
surface to receive the label as the extracting element moves or
rolls past the stations. The drive mechanism for each extracting
.. , . . . . . . . . . ~ , .
element is a cam drive, which comprises common, stationary double
cam discs for all the extracting elements with the cams located
on one side of the drive mechanism and in two different planes,
one plane being above the other and at some distance from the other.
Two sets of followers are mounted on the drive shaft or on a
bearing shaft which is coupled with the drive shaft by means of a
support element. The positive, directed movement of each extracting
element over its entire revolution as the support rotates i9
protected by means of a form-fit with the two cam surfaces.
2. Bac ~ :
The prior art includes various cam-controlled drive
mechanisms to turn the extracting elements in labelling machines
at the various stations in the same direction with different
angular velocities over the entire orbit.
In a first drive system of the prior art (German Patent No.
24 36 003 P2), the extracting elements are always driven by a
pair of lever arms, which are guided with a follower in a closed
grooved cam. The partly-overlapping grooved cams are in different
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planes, to allow for an unobstructed path while guided by the
lever arms. Each follower is clearly guided or directed as posi-
tioned on the two flanks of the corresponding grooved cam. The
grooved cams are configured so that the one follower is under
torque when the other follower is in an idle position. However,
such a drive mechanism has not been used in actual practice.
Further, it has not been possible to utilize in actual practice
another drive mechanism for a labelling machine of the type described
above (German Patent No. 27 09 521 Al). In the description of
the drive mechanism in this patent, there are two cam discs with
outside cams located in two planes, one plane above the other.
There is a set of two followers, each of which correspond to the
two cam discs in two different planes. The two pairs of followers
are offset on the upper and lower side of a disc by 90 degrees in
relation to one another. The disc is supported by a bearing
shaft which extends to the plane between the cam discs. It cannot
be determined from the prior art whether precautions have been
taken in the design of the drive mechanism to provide for a collision-
free passage area, for example, an open space which the bearing
shaft does not enter. According to the present invention, the
open space or collision-free area is preferably located outside
the radial areas of the cam disc adjacent to the bearing shaft.
According to U.S. Patent No. 42 98 422, a labelling machine
of the type described above, but with another drive mechanism,
has been used in actual practice . In this labelling machine,
the cam drive mechanism is designed as a lantern gear transmission,
with two sets of lantern gear teeth located on the inside of the
double cam disc which disc is in the shape of a ring-like body.
The support element, which supports one set of the followers
designed as lantern wheels on its two sides, is located between
the two lantern gears on the end of the drive shaft of the extracting
element with the drive shaft extending to the end point. The
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points of the teeth of this lantern gear are cut off to provide
for a collision-free passage of the drive shaft along the lantern
gear on the shaft side. With this type of drive mechanism, of
course, a non-uniform rotation of the extracting elements can be
achieved, but the cost and complexity of the lantern gear trans-
mission is quite high. A further disadvantage is that the radial
diameter of the lantern gears cannot be very compact on account
of the minimum width of the individual teeth required.
OBJECT OF_THE INVENTION
The object of this invention is to create a labelling station
with a simpler drive mechanism, which has a more compact structure
and provides an open space to maintain a collision-free, smooth
operation of the machinery. This object is accomplished with a
,labelling,station in which the drive or bearing shaft ends in ,
front of the plane of the first cam lying closest to this shaft.
Further, the followers which correspond to the other or second
cam, are mounted on a bridge element lying between the first and
second cams. The bridge element is supported by spacer elements
mounted on the support element. The spacer elements lie outside
the area covered by the motion of the first cam. It is particu-
larly advantageous if the followers, which are already present,
comprise the spacer elements.
SUMMARY OF THE INVENTION
The labelling station in accordance with the invention can
be designed with a compact structure and with a simple
configuration of the cams, since both cams with their actuators
can extend into the area of the drive or bearing shaft of the
followers. According to the present invention and of particular
advantage, the spacer elements need not be designed as followers.
BRIEF DESCRIPTION OF THE DRAWINGS
The invention will be further explained below with reference
to the following drawings.
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Figure laa is a schematic overhead view of a labelli ~ ~ 23 94
station.
Figure lab is an overhead schematic view of a cam drive
mechanism for an extraction element.
Figure lac is an axial cross section of the cam drive
mechanism shown in Figure lab along Line I-I in Figure lab.
Figure lad illustrates the labelling station shown in Figure
laa in a schematic, overhead, expanded, partly modified view.
Figure la is a sectional, elevational view of two glue segments
which are simultaneously mounted on the drive shaft of the preferred
labelling machine including various features of the invention.
Figure lb is an elevational view, partially in section, of
the lowest one of the two glue segments shown in Figure la.
Figure lc is a bottom view, partially in section, of the
. .
glue segment of Figure lb as seen when viewed in the direction of
the arrow A.
Figure ld is a sectional, elevational view of one of the
distance elements shown in Figure la.
Figure le is a top view of the distance element of Figure
ld.
Figure lf is a top view, partially in section, of one of the
glue segments of Figure la as installed on the drive shaft including
a preferred pin installed on the shaft to insure proper orientation
of the glue segments.
Figure lg is a sectional view of the glue segment of Figure
lf as seen alon~ line VII - VII.
Figure 1 is a schematic overhead view of a preferred labelling
machine including various features of the invention.
Figure 2 is a fragmentary overhead schematic view of one of
the cam drive mechanisms for one of the extraction elements in
Figure 1.
Figure 3 is a cross section of the cam drive mechanism shown
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in Figure 2 as generally seen along Line I-I in Figure 2.
Figures 4 through 6 are overhead and smaller scale views of
the labelling machine shown in Figure 1 including specific rela-
tionships and features of the invention.
Figure 7 is a schematic top view of the cams of the labelling
machine illustrated in Figure 1 including the teeth or junctions
formed at the overlapping areas of the cams.
Figure 8 is a view similar to that of Figure 5 of an alterna-
tive labelling machine.
Figure 9 is a view similar to that of Figure 7 of cams of
the labelling station of Figure 8 including the teeth or junctions
formed at the overlapping of the cams.
Figure 10 is a diagram for the angular velocity and angular
acceleration of one of the extraction elements of the labelling
station illustrated in Figure 1 including three extracting elements
and three transfer regions on the gripper cylinder.
Figure 11 is a schematic overhead view of another preferred
labelling machine.
Figure 12 is a fragmentary cross-sectional view of a preferred
cam transmission mechanism of the labelling machine as seen along
the line I-I of Figure 11.
Figure 13 is a schematic overhead view, on a smaller scale,
of the labelling machine illustrated in Figure 11, with the outside
cams shown raised.
Figures 14 and 15 are schematic, fragmentary views of the
labelling machine shown in Figure 11 in two phases of the rolling
of an extracting element past an adhesive application roller.
Figures 16 and 17 are schematic, fragmentary views of the
labelling machine shown in Figure 11 in two phases of the rolling
of an extracting element past a label box.
Figures 18 and 19 are schematic, fragmentary views of the
labelling machine shown in Figure 11 in two phases of the rolling
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of an extracting element past the gripper cylinder.
Figure 20 is an end view of a support element for the follow-
ers o~ a cam drive designed as a lantern gear mechanism.
Figure 21 is a cross-section of the support element of Figure
20 taken along line A-B.
Figure 22 is a cross-section of the support element of Figure
21 taken along line C-D.
Figure 23 is an end view of a different support element for
followers of a conventional cam drive mechanism.
Figure 24 is a cross-section of the support element of Figure
23 taken along line E-F.
Figure 25 is a top view of a labelling station with a follower
guided in a grooved cam.
Figure 26 is a cross-section of the labelling machine of
Figure 25 taken along line I-I.
Figure 27 is a top view of a labelling machine with followers
guided on two one-sided outside cams.
Figure 28 is a cross-section of the labelling machine of
Figure 27 taken along line II-II.
Figure 29 is a schematic plan view of a labelling machine.
Figure 30 is a cross-sectional view of a support of the
labelling machine of Figure 29 which employs different drives for
the extracting elements than that of Figure 29,
Figure 31 is a top view of the central portion of the support
illustrated in Figure 30.
Figure 32 is a cross sectional view of a support of the
labelling machine illustrated in Figure 29.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
The labelling station illustrated in Figure laa consists of
a plate-shaped support 12, on which three extracting elements 22. 32'
42 are located at equal angles relative to each other and form a
circular path, that is, rotate along circular track 392' Each
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extracting element 22. 32' 42 has a cylindrically curved receptacle
surface 52 for receiving a label, and is mounted on a support
plate 12 with a drive shaft 62 extending through the support
plate 12. The center point of the drive shafts of all the
extracting elements lies on the circumference of the circular
track 392 formed by the position of the extracting elements on
the support plate 12.
When the support plate 12 is rotated in the direction of the
arrow 72' the extraction elements 22. 32' 42 are forced to rotate
by a drive mechanism, described herein, in the direction of ~he
arrow 82, that is, in a direction opposite to the support plate
2 .
During this rotation of the support plate 12, the extraction
elements 22. 32' 42 move past, rolling-off each of the various
.. .. . . . . . . . . . . . . . . . . . . . ............... . . . . .
stations, comprising a glue roller 12 rotating in the direction
of the arrow 92' a stationary label box 112 with a stack of labels
inside, and a gripper cylinder 132 rotating in the direction of
the arrow 122.
At the first station, an adhesive or glue is applied to the
receptacle surface 52 of each extraction element 22, 32~ 42 by
the adhesive or glue roller 102. At the second or next station,
the top label is extracted from the label stack as a result of
the adhesive action of the adhesive on the receptacle surface 52
as the receptacle surface 52 moves or rolls past the top label
contained in the label stack box 112. As the support plate 12
continues to rotate, the label is next conducted to the third
station containing the gripper cylinder 132. The gripper cylinder
~32 takes the freshly glued label off the receptacle surface 52
and transfers the label, in a manner not shown herein, to objects
such as bottles. The objects or bottles are also moving past the
gripper cylinder 132, in a manner not shown herein.
In order for the receptacle surface 52 to roll past the
variously configured stations 102, 112, 132, the speed of the
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rotating movement of each extraction element 22, 32' 42 in the
direction of the arrow 82 needs to be accelerated or increased
and decelerated or decreased as required. The drive mechanism
illustrated in detail in Figures lab and lac is designed to
adjust accordingly the speed of the rotating extraction elements.
The drive shaft 62, mounted on and extending through the
support 12, has a gear wheel 152 on its end below the plate-
shaped support 12. This gear wheel 152 meshes with a larger gear
wheel 162. The larger gear wheel 162 is part of a support element
172 which sits on the lower end of a bearing sha~t. 182. The
shaft 182 is also mounted in the support 12. The support element
172 consists of an external body 17a2 and an internal body 17b2.
The two bodies 17a2, 17b2 have radially-oriented claws which
engage one another, and between which, covering the entire surface,
.
is a thin elastic insert 17C2 of damping material.
The gear wheel 162 is rigidly connected with the outside
body 17a2, Two diametrically-opposite followers are fastened
underneath to outside body 17c2. Each follower consists of a
bearing neck 18a2, 19a2 and a roller 18b2, l9b2 mounted on the
followers so that the followers can rotate. Since the elastic
intermediate insert 17C2 is located between the outside body 17a2
and the inside body 17b2, a decoupling of the gear wheel 162 and
the followers is possible if needed or required.
The bearing necks 18a2, 19a2 support and hold a ring-shaped
bridge element 202 which is positioned below the necks 18a2,
l9a2. Two followers, diametrically opposite one another and
offset by 90 degrees from the followers 18a2, 18b2, l9a2, l9b2,
are underneath and fastened to the bridge element 202. These
followers also consist of bearing necks 21a2, 22a2 and rollers
21b2, 22b2, respectively.
The two sets of followers, 18a2, 18b2, l9a2, l9b2 and 21a2,
21b2, 22a2, 22b2, correspond to a double cam disc 23 having two
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outside cams 23a, 23b. This double cam disc 232 is rigidly connected
via a support bridge 242 with the machine frame 252 of the labelling
station.
As shown in Figure lab and indicated b~ dotted lines in
Figure lac, the outside cams 23a2, 23b2 lie in partial segments
in the vicinity of the axis of the bearing shaft 182. A
shaft-free or open space 262 is created as a result of a design
wherein the bridge element 202 is located in the vicinity of the
outside cam 23a2 and is located in the center between the
followers 18a2, 18b2 and l9a2, l9b2. According to the present
design, the drive or bearing shaft 182 will not enter the open or
free space 262. Further, the vicinity or area of the lower
outside cam 23b2 will not be entered or affected by the operation
of bearing shaft 182. Thus, the cams 23a2, 23b2 can be optimally
.. . . . . . . . . . . . . . . . ................... . . . . .
configured over their entire length, and the complete drive
mechanism can be compactly designed with economical components.
As shown in Figure lad, the arrangement of the three
stations J comprising the adhesive or glue roller 102, the label
box 112 and the gripper cylinder 132, divides the support plate
12 into three preferably similar sectors. In Figure lad, these
sectors are shown bounded by the long-short dashed, radial lines
running and extending through the center of the stations 102,
112, 132 from the center of support plate 12. In the sector
between the adhesive or glue roller 12 and the gripper cylinder
132, there are two extreme points 32~ 312 of the outside cams
23b2, 23a2, respectively. In the sector between the adhesive
roller 12 and the label box 112, there is one extreme point 322
o~ the outside cam 23b2. Similarly, in the sector between the
label box 112 and the gripper cylinder 132, there is one extreme
point 332 of the outside cam 23a2.
At least one of these extreme points, extreme point 322 in
the embodiment, lies outside the track or circular path 342 of
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the mid-point of the axis of bearing shaft 182 in the support
element 172. Track 342 corresponds to the circumference of the
circle on which the mid point of the axis of drive or bearing
shaft 182 lies.
The load-bearing portions of the outside cams 23a2, 23b2 for
each pair of followers are illustrated by dashed lines in Figure
lad. The non-load-bearing and therefore not developed cams,
which are adjacent to these developed cams 23a2, 23b2, are illus-
trated by the dotted lines. These cams 352' 362' 372~ lie, for
the most part outside the track 392 Circular track 392 corres-
ponds to the circumference of a circle wherein the mid-point of
the axis of the drive shaft 62 of the extracting element lies.
Track 392~ track 342 and the support element plate 172 are concen-
tric with the radius of track 342. The radius of track 342 is
slightly less than the radius of the track 392.
In Figure lad the ratio of the radius a of the circular
track 342 to the radius b of the orbit or circular path of the
followers located on the support element 172 is preferably 3 to 1.
A pair or set of followers 18a2, 18b2, l9a2, l9b2 are thus
engaged with the cam 23a2 when a translation transmission is
located between the drive shaft and the support element and has a
translation ratio of preferably 1 to 3, when the axis of the
drive shaft 62 of the extracting element is located outside the
track 342 on the support element 172, preferably on track 392'
and when the extracting element is centrally position in front of
the label box 112,
;In summary, one aspect of a design resides broadly in a
labelling station for objects, such as bottles, with several
;stations located behind one another along a track, comprising an
adhesive or glue application apparatus, a label feed station and
a label transfer station. There is at least one extracting element
for the labels, mounted so that it can rotate on a rotating support
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plate and can be moved past the stations during each rotation of
the support. The extracting element has an outwardly-curved recept-
acle surface for receiving the label when the extracting element
moves or rolls past the stations. The drive mechanism for each
extracting element is a cam drive, which comprises common, stationary
double cam discs for all the extracting elements with cams located
on one side in two planes, above one another and at some distance
from one another. Two sets of followers are mounted on the drive
shaft or on a bearing shaft coupled with it by means of a support
element. The positive movement of each extracting element over
its entire revolution when the support rotates is protected by
means of a form-fit with the two cam surfaces,
The design is also characterized by the fact that the drive
or bearing shaft 182 ends in front of the plane in which the
first cam 23a2, being the cam closest to the shaft 182 lies.
The followers 21a2, 21b2, 22a2, 22b2, which correspond to the
other second cam 23b2, are mounted on a bridge element 202 which
liès between the two cams 23a2, 23b2. The bridge element 202 is
supported by spacer elements 18a2, l9a2 on the support element
172. The spacer elements 18a2, l9a2 lie outside the open, shaft-
free space 262 which space is entered and affected by the
movement of the first cam 23a2.
This above described design may also include a labelling
machine which has the preferred glue segments as described herein.
As seen in Figures la, lb and lc, two glue segments 11,21
are installed on and attached to a common drive shaft 31. Each
of the preferred glue segments 11,21, which includes a convex
curved glue take-up surface 41~51~ is, according to a design, to
be mounted in an adjustable manner on the shaft 31. The glue
segments 11,21 are respectively formed of carriers 81,91 which
are rigidly bolted to foundations 61,71 of the curved glue take-up
surfaces 41'51- Because of the possibility of different bottle
and label configurations, a design is directed to a means for
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properly supporting and spacing the glue segment 11 formed of the
combined carrier 8l and foundation 61 and the glue segment 21
formed of the combined carrier 91 and foundation 71 As will
been seen, each foundation 61,71 is rigidly bolted to its respective
carrier 8l,9l with the carrier 81,91 being the primary portion of
the glue segment which is secured to the drive shaft 31. It
should also be noted, as seen in Figure la, that, basically, the
carrier can be installed on the shaft 31 with the corresponding
foundation disposed either upwardly or downwardly to properly
locate the curved glue take-up surface thereon for accepting
labels and applying them to a bottle.
Consequently, it is the object of a design to provide a
means for mounting the glue segments on the shaft 31 with a proper
orientation and with proper axial spacing between the glue segments
and on the drive shaft. As a result, each of the carriers 8l,9
includes a hole 12l,131 for disposition around the drive shaft
31. Additionally, the carriers 81,91 respectively include axial
bores 10l,11l which are substantially located at the center of
curvature of the convex curved take-up surfaces 41~51. While the
holes 121,131 are intended to basically support the glue segments
on the shaft, the axial bores 101,11l will be utilized for proper
axial spacing of the glue segments 11,2l along the shaft 31 and
will further be employed to provide means for ensuring that, when
properly positioned, the glue segments 1l,21 will be secured
against further axial movement.
Generally, for this purpose, it should be noted that, the
wall of the carriers 81,9l located between axial bores 101,11l
and receptacle or holes 121,131 includes continued axial slits
14l,15l. The slits or slots 14l,15l have a circumferential width
and allow defection of the carriers 8l,9l in a manner which can
allow the interior dimensions of the holes 12l,13l to be selectively
reduced. Diagonally through the wall, there is provided a bore
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161,171 which partly intersects its corresponding axial bore
101,111. Tension bolts 181,191 are respectively used to selectively
produce the desired deflection of the carrier 81,91 in the area
of the holes 121,131 for fastening of carriers 81,91 onto drive
shaft 31' Each tension bolt 181,191 includes a lever 201, as
shown in Figures lb and lc, to selectively rotate the bolt and to
apply the force needed to maintain the carriers 81,91 against
undesired axial movement along the shaft 31~
In order to establish the axial position of each of the glue
segments 11,21, there is disposed in each axial bore 101,111 a
bushing 211,221. Each of the bushings 211,221 respectively includes
transverse or diagonal recesses 231,251 and 241,261. The recesses
231,251 and 241,261 can be selectively used for alignment with
and receipt of the tension bolts 181,191 therein. As a result,
the particular bushings 211,221 can be selectively prepositioned
within their respective axial bores 101,111. ~enerally, such a
configuration allows some selectivity and multiple use of dif-
ferent bushings in different bores of different glue segments.
AdditiGnally, such a configuration allows, with proper planning,
for the glue segments to be preselected for installation on the
shaft in either an upward or downward orientation relative to the
foundation and take-up surface thereon.
As seen in Figure la, the lower glue segment 21 includes the
bushing 221 disposed within the bore 111 as the bolt 191 extends
through the recess 241. With such an arrangement, the bushing
221 includes a base element which is disposed within the bore 111
and a spacing element extending outwardly from the bore 111 in an
axial direction toward a ring or collar 321 installed on the
shaft 31. The preferred spacing element of the bushing 221 includes
a collar 281 having an abutting surface at the lower region thereof
for making contact with the ring 321.
When the preferred configuration of Figure la is being formed
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and the glue segments 11,21 are initially installed on the shaft
31' the bolt 191 is loosened but still properly maintains the
axial position of the bushing 221 therein. After the collar and
the abutting surface thereon is positioned against the ring 321,
the bolt 191 is tightened to generally deflect the carrier 91 at
the slit 151 to create tension between the carrier 91 and the
shaft 31 to prevent any axial displacement from the desired axial
position as established by the bushing 221. As will be seen
later, there is included means for properly circumferentially
orienting each of the glue segments 11,21 on the shaft 31 to
prevent undesired relative rotation therebetween.
As the upper glue segment 11 is being installed, the
particular bushing 211 installed in the bore 101, includes a
spacing element thereof in the form of a collar 271 to establish
proper axial spacing between the glue segments 11,21. The collar
271 includes a lower abutting surface which makes contact with an
upper rim 311 of the carrier gl in order to properly axially
locate the glue segment 11 on the shaft 31. Again, after proper
axial positioning, the bolt 181 can be tightened to secure the
glue segment 11 against undesired axial movement from the desired
axial position as established by the bushing 211.
It can be seen, from the embodiment as described hereinabove,
that the preferred configuration for supporting each of the glue
segments 11,21 requires the establishment of a basic radially
extending surface at a predetermined location axially on the
drive shaft 31. The basic radially extending surface for the
glue segment 21 is the ring 321. By proper selection of the
amount of extension of the spacing element of the bushing 221,
the axial position of the entire glue segment 21 can be established
and maintained on the shaft 31. Similarly, after the glue segment
21 is properly located, the upper surface thereof provides a
radially extending surface disposed at a predetermined location
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axially on the drive shaft 31 for the establishment of the axial
position of the glue segment 11 on the drive shaft 31 by the
proper selection of the spacing element disposed in the bore 10l
thereof. Consequently, it can be seen that the preferred config-
uration provides a convenient means for alternatively employing
different forms and sizes of bushings in order to conveniently
establish spacing of the glue segments while assuring the spacing
will be quickly retained when the glue segments are installed on
the shaft 31. It might be noted, for example, that the collar
27l of the bushing 21l is preselected for proper extension from
the bore 101 so that an edge 291 will make abutting contact with
the lower surface of its carrier 81. On the other hand, the
bushing 221 is disposed within its bore 111 in a manner such that
the collar 281 thereof extends from the bore 111 without any need
for such abutting contact with the lower region of the carrier 91
As seen in Figures ld and le, a preferred bushing 211
includes the collar 271 having an extended portion 331 at one
side. The extended portion or projection 331 includes a concave
recess 341 The concave recess 341 is adapted to partially
encircle the shaft 31 in order to provide a larger support
surface around the shaft 31 for better support by, and contact
with, a support surface such as that provided by the ring 321 as
shown in Figure la. Additionally, by providing the projection
331 and recess 341' the preferred configuration for the bushing
211 ensures that it will be properly oriented within the bore of
the carrier for proper alignment of the recesses 231,251 for
receipt of the tensioning bolt therein.
As discussed hereinabove, the basic configuration of the
preferred embodiment, as previously described, could be selectively
disposed on the shaft with the preselected bushing extending from
either side of the bore. Such flexibility is desirable in order
to be able to use various components to establish the desired
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spacing. However, once the proper bushing has been selected and
installed, the selected configuration should be readily installed
with only one orientation on the shaft. As a result, the preferred
embodiment includes, as seen in Figures lf and lg, means for
ensuring that a particular glue segment will only be positioned
with one orientation on the shaft after the various components
thereof are properly selected. As mentioned above, the glue
segments are mounted on the shaft 31 with a matching keyway 351
on the shaft and the carrier. With a key installed in the keyway
351' each of the glue segments 11,21 is prevented from rotating
relative to the shaft 31. With the glue segments prevented from
rotation by the keyway 351 and key therein, the movement from the
desired axially position is prevented, as discussed above, by the
tightening of the bolt 181 or 191.
To insure that the glue segments are installed properly on
the shaft, an additional keyway 361 is provided in the holes
121,131. The additional keyway 361 is disposed circumferentially
to one side of the keyway 351. The additional keyway 361 is for
alignment of a pin 36bl on the shaft 31 for within a groove 36
of the keyway 361. As seen in Figure lg, the pin 36bl need not
be specifically disposed within the groove 36al after the particular
glue segment is fully installed on the shaft 31. It is only
essential that the pin 36bl be initially aligned with the groove
36al as the glue segment is initially being installed. Once properly
orientated, the glue segment can be moved axially, downwardly on
the shaft 31 in a proper orientation so that the key can then be
installed in the keyway 351 Proper orientation, as the glue
segment is initially being installed, will insure proper orienta-
tion after it is proper axially positioned on the shaft.
In further summary, a design includes an attachable glue
segment 11 or 21 which is attachable to drive shaft 31. Each
segment 11,21 respectively consists of a curved glue take-up
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surface 41~51; an axial bore 101,111 which is located in the
center of the curvature of the glue take-up surface 41~51; and an
attached axial connecting receptacle or hole 121,131 for the
drive shaft 31. A wall which is located between the axial bore
101,111 and the connecting receptacle 121,131 is continually
slotted and contains a tension bolt 181,191 which is located
diagonally to the slot. A design is characterized by the fact
that a bushing 211,221, which is inserted into its corresponding
axial bore 101,111, contains a collar 271,281 or spacing element
~hich serves as a distance establishing element and is supported
on the rim 291 of axial bore 101 or another abutment 301 of the
glue segment 21. The glue segments 11,21 are secured against
movement in an axial direction by clamp bolts 181,191 located
within the axial bore 101,111. These bolts may be either self-
locking or self-tapping.
The glue segments may be characterized by the fact that the
collars 271,281, on one side, have an overhang 331 with a concave
recess 341 which matches the contour of drive shaft 31.
The glue segments may also be characterized by the fact
that, between the connecting receptacles or holes 121,131 and the
drive shaft 31~ there is a keyway 351~ which locks the segments
against rotation. In addition, there is a peripherial one sided
keyway 361.
An example of a labelling machine in which a design may be
used is described as follows:
The labelling station illustrated in Figures 1 to 5 consists
of a plate-shaped support 1, on which three extracting elements
2, 3, 4 are located at equal angles. Each extracting element 2,
3, 4 has a cylindrically curved receptacle surface 2', 3', 4' for
a label and is mounted between the latter and the center point of
its curve on a respective drive shaft 6, 7, 8 in the support 1.
When the support l is rotated in the direction of the arrow 9,
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the extraction elements 2, 3, 4 are forced to rotate by a drive
mechanism (described below) in the direction of the arrow 10,
which is opposite to the directional rotation of the support 1.
During this rotation of the support 1, the extraction elements
2, 3, 4 move past various stations. The stations include a glue
roller 12 rotating in the direction of the arrow 11, a stationary
label box 13 with a stack of labels inside, and a gripper cylinder
14 rotating in the direction of the arrow 15. Each of the extrac-
tion elements 2, 3, 4 executes a roll-off movement at the individual
stations. First, adhesive is applied to the receptacle surface
2', 3', 4' of each extraction element 2, 3, 4 by the adhesive
roller 12. While rolling past the front label of the stack of
labels in the label box 13, the front label is extracted from the
label stack as a result of the adhesive action of the adhesive on
the receptacle surface 2', 3' 4'. As the support 1 continues to
rotate, the label is conducted to the gripper cylinder 14, which
removes the label from the receptacle surface 2', 3', 4' and
transfers it in a manner not shown herein to objects, such as
bottles, moving past the gripper cylinder 14.
In order for the receptacle surface 2', 3', 4' to roll past
the variously configured stations 12, 13, 14, it is necessary for
the rotation of each extraction element 2, 3, 4 in the direction
of the arrow 9 to be accelerated and decelerated. For this purpose,
the extracting elements 2, 3, 4 respectively include pinions 17,
18, 19 which are respectively mounted on the drive shafts 6, 7,
8. The pinions 17, 18, 19 are respectively connected with larger
gear wheels 20, 21, 22, which are mounted in the direction of
rotation behind the corresponding extracting element 2, 3, 4 by
means of bearing shafts shown in Figures 2 and 3 in the support 1.
Each larger gear wheel 20, 21, 22 is part of a cam drive
mechanism. Each of these cam mechanisms has the same structure,
so that the following description can be limited to a single cam
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drive mechanism but is equally applicable for the others.
The larger gear wheel 20 preferably consists of two gear
wheels which can be rotated and fixed in relation to one another
to remove play therebetween~ The gear wheel 20 is part of a
support element 51, which sits on the lower end of the bearing
shaft 50 mounted in the support 1. The support element 51 consists
of an outside body 51a and an inside body 51b. The two bodies
51a, 51b have radially oriented claws, which are engaged with one
another. Between the claws is inserted a thin elastic insert 51c
made of damping material.
The gear wheel 20 is rigidly connected to the upper part of
the outside body 51a. On the underside of the outside body 51a
are fastened two diagonally-opposite followers respectively consis-
ting of a bearing neck 25a, 26a and a roller 25b, 26b rotatably
mounted thereon. Because of the elastic insert 51c between the
outside body 51a and the inside body 51b, there is thus a decoupling
for the gear wheel 20 and the followers 25a, 25b, 26a, 26b.
The bearing necks 25a, 26a support, on their underside, a
bridge element 52 in the shape of a ring. On the underside of
the bridge element 52 are fastened two followers geometrically
opposite one another and offset by 90 degrees from the followers
25a, 25b, 26a, 26b. These followers also respectively consist of
a bearing neck 23a, 24a and rollers 23b, 24b located thereon.
The two sets of followers 23a, 23b, 24a, 24b, 25a, 25b, 26a,
26b correspond to a double cam disc 53 having two cams 27, 28
with outside camming surfaces. This double cam disc 53 is rigidly
connected via a support bridge 54 with the machine frame 55 of
the labelling station. The cams 27, 28 have the shape of ovals
indented on both long sides, and are oriented crossways to one
another.
As shown in Figure 2 and as indicated by dashed lines in
Figure 3, partial segments of the outside regions of the cams 27,
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Z~D~ 23
28 lie in the vicinity of the path of the axis of the bearing
shaft 50. However, because of the design with the bridge element
52 lying between the outside portion of the cams 27, 28, in the
vicinity of the outside portion of the upper cam 28 in the center
between the followers 25a, 25b, 26a, 26b, a shaft-free space 56
is created. In the vicinity of the outside portion of the lower
cam 27, the drive or bearing shaft 50 is terminated and does not
extend into the level lower cam 27. As a result, the outside
portion of the cams 27, 28 can be optimally configured over their
entire length so that the entire drive mechanism can be compactly
designed with economical components. At each point of the outside
portion of the cams, at least one follower is under torque and at
least one follower is providing counter support, so that there is
always a defined rotational position for the extraction element.
.. . . . .
As shown in Figures 4-6, the arrangement of the three sta-
tions, which include the adhesive roller 12, the label box 13 and
the gripper cylinder 14, divides the support 1 into three sectors.
In the drawing, these sectors are limited by the dotted lines
running through the center of the stations 12, 13, 14. In the
sector between the adhesive roller 12 and the gripper cylinder 14
there are two extreme points 30, 31 respectively of the outside
regions of the cams 27, 28. In each of the sectors between the
adhesive roller 12 and the label box 13, on the one hand, and
between the label box 13 and the gripper cylinder, on the other
hand, there is always one extreme point 32, 33 of the outside
regions of the cams 27, 28. All the extreme points 30, 31, 32,
33 lie practically on the track or path 34 of the mid-point or
center of the bearing shaft (not shown) with its support elements
for the followers 23, 24, 25, 26 mounted thereon. Only the extreme
point 33 lies somewhat outside this track or path 34 of the mid-point
or center. The radius a of the track or path 34 of the mid-point
preferably has a radius of about 3 to about 1 to the radius b of
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the orbit of the followers 23, 24, 25, 26, The translation ratio
between the pinions 17, 18, 19 and the larger gear wheels 20, 21,
22 engaged therewith is preferably about 1 to about 3.
As also shown in Figures 4-6, the extreme points 30, 31, 32,
33 of the outside regions of the cams 27, 28 are determined by
the fact that each cam 27, 28 is comprised of two overlapping
cams. While the cam segments formed are illustrated in dashed
lines, the cam segments which are not formed, and which supplement
these formed cam segments are shown in dotted lines. The dotted
line represents the path of each of the followers 23, 24 and 25,
26 when the corresponding other followers 24, 23 and 26, 25 are
in contact with and guided along a path of the surface of the
respective cams 27, 28 represented by the dashed lines.
Figures 5 to 7 show principally the geometric relationships
of the two cams 27, 28, which are vertically and rotationally
offset from one another with each essentially forming an oval
indented on both sides.
Figure 7 shows principally the teeth or junctions 36 to 38
formed by the two outside curves of the cams 27, 28 in the overlap-
ping area. While the narrower teeth or junctions 36, 37 lie
within an obtuse angle a, which is bordered by the radial rays or
lines Sl, S2 emanating from the mid-point T of the support and
running through the extreme points 31, 33 of the outside region
of the cam 28. The extreme points 30, 32 of the outside region
of the other cam 27 lie on a straight line G, which runs generally
close to or approximately through the mid-point T of the support.
As shown principally by Figure 6, the followers 23 to 26 of
one of the support elements 51 interact with the teeth or junctions
36 to 39 formed in the overlapping area of the two cams 27, 28.
There are distances c, d respectively between the contact points
of the followers on the flanks of a narrow teeth or junctions 36,
37, when connecting lines V2, V2 running through the mid-points
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of the followers are perpendicular to the respective radial rays 4
or lines R2, R3 emanating from the support mid-point T and running
through the polnt of the corresponding teeth 36, 37. The distances
c, d are 30~ to 40~ less than the distances e, f of the contact
points of the respective followers on the flanks of the wide
teeth or junctions 38, 39. Again, the distances e, f are estab-
lished connecting lines V3, V4 running through the mid-points of
the followers is perpendicular to the respective radial rays or
lines R3, R4 emanating from the mid-point T of the support and
running through the point of the corresponding teeth 38, 39.
Figures 5-7 also show that, on one hand, the points of the
narrow teeth or junctions 36, 37 and on the other hand, the points
of the wide teeth or junctions 38, 39 are respectively at compara-
ble radial distances from the mid-point T of the support. More
, . . . . . . . .. . .. . . . . . .. . . . . . . . . . _ . . _ . . . .
specifically, the radial distances of the narrower teeth 36, 37
are greater than those of the wide teeth 38, 39.
The diagram in the top of Figure 10 shows the angular velocity
of the extracting element and the diagram at the bottom of Figure
10 shows the angular acceleration of the extracting element during
a rotation of the extracting element support by 360 degrees around
its circumference. The sectors I, III and V respectively represent
the roll-off areas at the label box, the gripper cylinder and the
adhesive application roller. The sectors II, IV and VI respective-
ly represent the intervening intermediate areas. The diagram
shows that in all the regions, the angular velocity only reaches
a maximum in each of the rolling regions I, III and V, and a
minimum in each of the intermediate regions II, IV and VI. In
the intermediate region VI, the region between the adhesive appli-
cation roller 12 and the label box 13, the angular velocity even
becomes negative, which means that the direction of rotation is
briefly reversed. The cams are thereby configured so that the
maxima and minima always occur approximately in the central portion
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of the individual regions so that the movement sequence is optimized.
The acceleration diagram shows that in the rol.l-off regions I and
V, where rolling contact takes place in the entire region, the
acceleration and thus also the load is significantly less than in
the adjacent regions. Only in the vicinity of the gripper cylinder
is the acceleration approximately as great as in the adjacent
regions. It should be noted that here, the two surfaces do not
actually roll along one another over the entire region, but are
only following one another.
The labelling station in accordance with Figures 8 and 9
differs from that illustrated in Figures 1 to 7 only in that the
support element with the followers precedes the extracting element
and tha~ the gripper cylinder has a larger diameter. The illus-
trations in Figures 8 and 9 are similar to those in Figures 5 and
7 of the labelling station shown in Figure l. Since the relation-
~hips with regard to the design of the cams 27, 28 are the same
in principle, additional explanations in terms of Figures 1, 2,
3, 4, 5, 6, 7 and 10 should be unnecessary. The equivalent compon-
ents of Figures 8 and 9 relative to the components of Figures 5
and 7 are identified by the same reference numbers plus an apostrophe.
Although the specific velocities and accelerations of the extract-
ing elements for the machine of Figures 8 and 9 would be different
from those shown in Figure 10 for the machine of Figure 1, the
same rotational principals would still exist.
As generally described above, the preferred labelling machine
for objects, such as bottles or the like, includes several stations
located behind one another along a track. The stations include
an adhesive application apparatus 12, a label feed station 13 and
a label transfer station 14. The machine includes at least one
extracting element 2, 3, 4 for the labels, mounted so that it can
l .,
rotate on a rotating support l and be moved past the stations 12,
13, 14 during each rotation of the support 1. The extracting
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element has an outwardly-curved receptacle surface 2', 3', 4' for
the label which rolls along the stations 12, 13, 14. The drive
for each extracting element 2, 3, 4 is a cam drive, which comprises
common, stationary double cam discs 53 for all the extracting
elements 2, 3, 4 with cams 27, 28 located in two planes with one
above and at some distance from the other. In some embodiments,
the two sets of followers 23, 24, 25, 26 may be mounted on each
of the drive shafts 6, 7, 8 of the extracting elements 2, 3, 4.
Preferably, the two sets of followers 23, 24, 25, 26 are mounted
on each of the bearing shafts 50, which is coupled with each of
the drive shafts, by means of a support element 51. By means of
a form-fit with the two cams 27, 28, the followers produce positive
movement of each extracting element 2, 3, 4 over its entire revolu-
, , ,,,tion,when the,support,l rotates. ,The labelling,,machine,is charac- ,,
terized by the fact that each bearing shaft 50 ends in front of
the plane in which the first cam 28 closer to the shaft 50 lies.
The followers 23, 24 which correspond to the other second cam 27
are mounted on a bridge element 52 lying between the two cams 27,
28. The bridge element 52 is supported by spacer elements 25a,
26a on the support element 51. The spacer elements 25a, 26a lie
outside the area 56 covered by the relative movement of the first
cam 28.
The labelling machine can include the followers 25, 26 of
the first cam 28 encompassing the spacer elements 25a, 26a. The
two followers 23, 24, 25, 26 which correspond to each set are
located opposite one another in relation to the axis of the drive
or bearing shaft 50, and the followers 23, 24 of the one set are
radially offset by 90 degrees from the followers 25, 26 of the
other set. The followers 25, 26 may have pivots 25a, 26a, as the
bridge element 52 is supported on its one side by the pivots 25a,
26a corresponding to the first cam 28, and on its ather side
supports the pivots 23a, 24a corresponding to the second cam 27.
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20~2394
The followers 23, 24, 25, 26 preferably include rollers 23b, 24b,
25b, 26b which are mounted on the pivots 23a, 24a, 25a, 26a.
The labelling machine may also be characterized by the fact
that the double cam disc 53 which has cams 27, 28 is located
inside the orbit with the followers 23, 24, 25, 26, and is con-
nected by means of a support bridge 54 located under the followers
23, 24, 25, 26 with the machine frame 55. Additionally, the
support element 51 of the followers 23, 24, 25, 26 may consist of
an external body 51a supporting the followers 23, 24, 25, 26 and
an internal body 51b connected with it by means of an insert 51c
made of elastic damping material. The two bodies 51a, 51b are
positively engaged with one another in the vicinity of the insert
51c by means of radially oriented claws. The body 51a supporting
the,followers,.23., 24, 25, 26,may,support a drive pinion 20.
Still further, the labelling machine may be characterized by
the fact that of the radial extreme points 30, 31, 32, 33 of the
outside surfaces of the two cams 27, 28, two extreme points 30,
31 lie in the sector between the gripper cylinder 14 and the
adhesive roller 12. The other two extreme points 32, 33 respec-
tively lie in the other two sectors formed between the label
transfer station designed as a gripper cylinder 14, the label
supply station designed as a label box 11, and the adhesive appli-
cation apparatus designed as the adhesive roller 10. At least
one of the extreme points 30, 31, 32, 33 of the two outside cams
27, 28 may lie outside the path 34 of the mid-point of the support
element 51 of the followers 23, 24, 25, 26.
The preferred labelling machine may be characterized by the
fact that with a transmission located between the drive shaft 6
of the extracting element 2 and the support element 51, a trans-
lation ratio may be about 1 to about 3. When the axis of the
drive shaft 6 of the extracting element 2 is outside the path 34
of the mid-point of the support element 51, and the central position
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2012394
of the extracting element is in front of the labelling supply
station designed as a label box 11, a pair of followers 23, 24 is
engaged by means of both followers 23, 24 with the outside cam
27, The ratio of the radius a of the path of the mid-point 34 of
the support element 51 to the radius b of the orbit of the followers
23, 24, 25, 26 on the support element 51 may be about 3 to about 1.
The labelling machine may be further characterized by the
fact that the non-load-bearing cam path segments of the cams 27,
28 described by the followers 23, 24, 25, 26 lie for the most
part outside the path 35 of the mid-point of the drive shaft 6 of
the extracting element 2,
The preferred labelling machine may include the following
features:
The extreme points 31, 33 of one of the two outer cams
27, 28 may lie on rays Sl, S2 emanating radially outward
from the center point T of the support to enclose an obtuse
angle a therebetween.
Of the teeth or junctions 36, 37, 38, 39 which are
formed in the overlapping areas of the two outer cams 27, 28
and with which simultaneously the followers 23, 24, 25, 26
of both sets interact, the narrower teeth 36, 37 lie inside
the obtuse angle a.
The obtuse angle a is 120 degrees to 160 degrees, in
particular 140 degrees.
The extreme points 30, 32 on the other outside cam 27
lie on a straight line G running near or approximately
through the mid-point of the support T.
The distance c, d between the contact points of the
followers 23, 24, 25, 26 on the flanks of one of the narrow
teeth or junctions 36, 37 formed by the overlapping regions
of the two cams 27, 28 is about 30Z to about 40% less than
the corresponding distance e, f for a corresponding wide
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201~39~
tooth or junction 38, 39, when the connecting line running
through the mid-point of the followers 23, 24, 25, 26 in
contact with the tooth or junction 36, 37 is perpendicular
to the radial ray or line Rl, R2 emanating from the mid-
point T of the support and running through the point of the
tooth 36, 37.
The extreme points 30, 31, 32, 33 tend to lie on a
circle 34 around the mid-point of the support T.
The points of the teeth 36, 37, 38, 39 formed by the
overlapping areas of the outside cams 27 t 28 lie inside the
circle 34 for the extreme points 30, 31, 32, 33 and are at a
different radial distance from the circle or mid-point T of
the support.
The radial distances of the peaks of the narrow teeth
36, 37 formed by the overlapping areas of the two outer cams
27, 28 from the mid-point T of the support are substantially
equal.
The radial distances between the peaks of the wide
teeth 38, 39 formed by the overlapping areas of the two
outside cams 27, 28 and the support midpoint T are
substantially equal.
The radial distance between the points of the narrow
teeth 36, 37 formed by the overlapping areas of the two
outside cams 27, 28 is greater than the radial distance of
the wide teeth 38, 39.
The labelling station may be further characterized by the
fact that, because of the outside curve of the two cams 27, 28,
the angular velocity of each individual extracting element 2, 3,
4 in the roll-off area of the stations 12, 13, 14 reaches only a
maximum, and in the intermediate areas in between, it reaches
only a minimum.
The maxima and minima of the angular velocity always lie
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201~9~
approximately in the center of the roll-off area or of the interme-
diate area. The minimum angular velocity in the intermediate
areas is less than one-half the maximum angular velocity in the
roll-off areas. The angular velocity is preferably greatest in
the vicinity of the gripper cylinder 14. The rotational motion
of each individual extracting element 2, 3, 4 is decelerated to
at least zero in at least one intermediate region and is then
accelerated once again up to the roll-off velocity.
As generally seen in Figure ll, the preferred labelling
machine comprises a plate-shaped support 1 , on which there are
four extracting elements 2 , 3 , 4 , 5 at equal angles to one
another. Each extracting element 2 , 3 , 4 , 5 has a cylin-
drically curved receptacle surface 2' , 3' , 4' , 5' for a label
and is mounted between the surface and the midpoint of its curvature
.. .. .
by means of a drive shaft 6 , 7 , 8 , 9 in the support 1 . When
the support l rotates in the direction of the arrow 10 , the
extracting elements 2 , 3 , 4 , 5 are respectively rotated by
means of a drive mechanism, as to be described below, in the same
direction, in the direction of the arrows 11 , 12 , 13 , 14 ,
which is in the direction opposite to that of the support l .
During the rotation of the support 1 , the extracting elements
* * * *
2 , 3 , 4 , 5 are rolled past various stations including an
adhesive application roller 15 rotating in the direction of the
arrow as shown thereon, a stationary label box 16 with a stack
of labels inside it, and a label transfer cylinder or gripper
cylinder 18 rotating in the direction of the arrow 17 . Each
extracting element executes a rolling motion as it rolls past the
individual stations. Initially, adhesive is applied to the recepta-
cle surfaces 2' , 3' , 4' , 5' of each extracting element 2 ,
3 , 4 , 5 by the adhesive application roller 15 . As the extracting
element rolls past the outer label of the stack of labels in the
label box 16 , the outer label is extracted from the label stack
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as a result of the adhesive action of the adhesive on the recepta-
cle surface 2' , 3' , 4' , 5' . As the support 1 continues to
rotate, the extracting element is conducted to the gripper cylinder
18 , which takes the label from the receptacle surface 2' , 3' ,
* *
4' , 5' and for subsequent transfer of the label to objects
being moved past the gripper cylinder 15 , such as bottles or the
like (not shown).
In order for the receptacle surface 2' , 3' , 4' , 5' to
roll past the variously-configured stations 15 , 16 , 18 , it is
necessary to accelerate and decelerate the rotation of each
extracting element 2 , 3 , 4 , 5 in the direction of the arrow
11 , 12 , 13 , 14 . For this purpose, each extracting element
2 , 3 , 4 , 5 is respectively connected by means of a pinion
19 , 20 , 21 ! 22 sitting on its respective drive shaft 6 , 7 ,
8 , 9 with a larger gear wheel 123 , 124 , 125 , 126 . Each
gear wheel is mounted in the direction of rotation behind its
* * * *
corresponding extracting element 2 , 3 , 4 , 5 by means of a
bearing shaft (not shown) in the support 1 .
Each of the larger gear wheels 123 , 124 , 125 , 126 is
part of a cam transmission mechanism. Each of the cam
transmis6ion mechanisms has the same design, so that the
following description is directed to the cam transmission
mechanism corresponding to the extracting element 2 as
illustrated in detail in Figure 12.
On the lower end of the bearing shaft 25 of the cam
transmission mechanism for the larger gear wheel 125 mounted in
* *
the support 1 is a support element 24 without any relative
rotation therebetween. The support element 24 consists of an
* * *
outside body 24a and an inside body 24b . The outside body 24a
has claws or fingers pointing inward, and the inside body 24b
has claws or fingers pointing outward and lying between the claws
pointing inward. Between the two bodies 24a and 24b , and thus
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also between the engaged claws or fingers thereof, there is an
insert 24c made of elastic material.
The outer body 24a , on a radially recessed upper projection
thereof, supports the larger gear wheel 125 , which consists of
two gear wheels 23a , 23b which can be rotated to eliminate any
play therebetween them. The wheels 23a and 23b are fastened to
the outer body 24a by means of threaded fasteners (not shown).
On the underside of the support element 24 are fastened two
opposite followers 26 , 27 respectively consisting of a bearing
pin 26a , 27a and a roller 26b , 27b mounted for rotation
thereon. The bearing pins 26a , 27a are integrally connected to
the non-recessed lower part of the support element 24 . As can
be seen in Figure 12, and also in Figure 11, the roller 26b with
its outer periphery projects beyond the arc of the gear wheel
* *
125 , 23a , 23b . With such a geometry, it would not be possible
to achieve a sturdy embodiment with a two-piece construction, in
which the corresponding bearing pin 26a would have to be
installed in a hole in the support element 24 .
Both of the bearing pins 26a , 27a , at the undersides
thereof, support a bridge element 30 in the form of a ring, on
the under side of which are fastened two opposite followers 28 ,
29 . Although only follower 28 is shown, the followers 28 , 29
* * *
are offset from the followers 26 , 27 . The follower 28 also
consists of a bearing pin 28a and a roller 28b mounted for
rotation thereon. Each of the followers 26 -29 , as shown in
Flgure 11, are offset from adjacent followers by an angle which
is between 70 degrees and 110 degrees and is not necessarily
* *
equal to 90 degrees. Moreover, the followers 26 -29 are at a
different radial distance from the axis of the bearing shaft 25
and, therefore, are engaged by means of different lever arm
lengths. In each plane there is one follower with a long lever
arm and one follower with a short lever arm. Corresponding to
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the two sets of followers 26 -29 is a double cam disc 31 with
two outside cams 32 , 33 having outside operating surfaces.
This double cam disc 31 is rigidly connected by means of a
* *
support bridge 34 within the machine frame 35 of the labelling
machine. The outside cams 32 , 33 have the basic shape of ovals
indented on both long sides, and are oriented crossways to one
another.
As shown in Figure 11 and indicated by a dotted line in
* *
Figure 12, the outside cams 32 , 33 lie with partial segments
thereof in the vicinity of the axis of the bearing shaft 25 .
Because of the design with the bridge element 30 lying between
* *
the outer cams 32 , 33 , a shaft-free space (not sbown) has been
created in the vicinity of the outside cam 32 in the center
between the followers 26 , 27 . Of course, the bearing shaft 25
.. . . . . .. . . . . . . . .. .. .
does not extend into the vicinity of the lower outside cam 33 .
As a result, the outside cams 32 , 33 can be optimally and
economically configured over their entire length into compact
components. At each point of the outside curves of the cams 32 ,
33 , there is at least one follower transmitting torque and at
least one follower providing support from the other side, so that
there is always a defined rotational position for the
corresponding extracting element.
Figure 13 shows, by way of example for a cam transmission
mechanism, a fixed equivalent cam surface 36 and the correspond-
ing moving equivalent cam surface 37 . The fixed equivalent cam
surface 36 and the moving equivalent cam surface 37 represent
cams in which there would be relative rolling contact on a point
by point basis between the two cam surfaces thereof. The fixed
*
equivalent cam surface 36 has the same axis as and represents
the cams 32 , 33 while the moving equivalent cam surface 37 has
the same axis as and represents the same motion about the axis as
the followers 26 -29 . As a result, the fixed equivalent cam
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surface 36 and the moving equivalent cam surface 37 would
follow the same relative motions as the cam transmission realized
with the two outside cams 32 , 33 and the corresponding
followers 26 -29 . In other words, the center axis of both the
followers 26 -29 and the moving equivalent cam surface 37 would
evolve about the center of the cams 32 , 33 or the fixed
equivalent cam surface 36 at the same rate. Further, the
changing relative rotation about the center axis of the followers
26 -29 and the moving equivalent cam surface 37 would be
identical in either case.
As seen in Figure 13, the axes of all the followers 26 -29
lie within the movable equivalent cam surface 37 , while portions
of their periphery outer surfaces remain outside the movable
equivalent cam surface. Figure 13 also shows that the orbit RL
... . . .. .. .... .. .
of the bearing shaft 25 lies inside the orbit RA of the drive
shaft 6* of the extracting element. This geometry also
contributes to the compact structure.
Figures 14 and 15 show the engagement of the followers when
one of the extracting elements 2 is being aligned with the ad-
hesive application roller 15 . At the beginning of the rolling
sequence shown therein, the two followers 27 , 28 are engaged
and transmitting torque, and the follower 26 , with a long lever
arm, provides support from the other side. In this initial
phase, which is particularly important for the application of the
adhesive, there is an optimal guidance as a result of the double
engagement of the two followers with short lever arms and the
supporting follower with a long lever arm. In the rest of the
rolling sequence, where the requirements for the guidance of the
extracting element 2 are no longer as critical, the engagement
of one of the followers with a short lever arm can be eliminated.
The instant just prior to the loss of engagement with follower
27 is depicted in Figure 15.
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In the vicinity of the label bo~ 16 , as seen in Figures 16
and 17, the two followers 26 , 29 with a large lever arm are
shown in the engaged state. From the beginning of the rolling
sequence until at least the middle, the follower 26 closest to
the bearing shaft transmits torque, while the follower 29
provides support from the other side. Because of the proximity
of the follower 26 with a long lever arm to the bearing point,
the result is also a very precise guidance.
Of all the stations 15 ~ 16 , 18 , at the station of the
gripper cylinder 18 , the guidance of the extracting element 2
is at its least critical at the beginning of the rolling
sequence. Accordingly, as seen in Figure 18, the follower 29
with a long lever arm, the one which is the farthest from the
bearing shaft 25 ! transmits torque. However, this guidance,
which is not as optimal when compared to the torque-transmitting
followers on the other stations, is altogether sufficient.
During initial alignment for gripping the label from the
extracting element 2 and for some portion of the rotation beyond
the initial. alignment, as seen in Figure 19, the two followers
27 , 28 with short lever arms act to provide support from the
other side for the follower 29 .
As generally described above, the preferred labelling
machine of Figures 11 through 19 for objects, such as bottles or
the like, with several stations located behind one another along
a track. The stations include an adhesive application roller
15 , a label box 16 and a label transfer cylinder 18 . The
machine includes at least one extracting element 2 , 3 , 4 , 5
for the labels, mounted so that it can rotate on a rotating
support 1 and be moved at a different angular velocity past the
,~ * * * *
stations 15 , 16 , 18 during each rotation of the support 1 .
The extracting element has an outwardly-curved receptacle surface
2', 3', 4', 5' for the label which rolls along the stations 15 ,
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16 , 18 . The drive for each extracting element 2 , 3 , 4 , 5
is a cam drive mechanism, which comprises common, stationary
double cam discs 31 for all the extracting elements 2 , 3 , 4 ,
* * *
with cams 32 , 33 located in two planes with one above the
other. Two sets of two followers 26 , 27 , 28 , 29 , which are
angularly offset from one another and are mounted on each of the
drive s~afts 6 , 7 , 8 , 9 or on a bearing shaft 25 coupled
with each of the drive shafts by means of a support element 24 .
By means of a form-fit with the two cams 32 , 33 , the followers
produce positive movement of each extracting element 2 , 3 , 4 ,
over its entire revolution when the support 1 rotates. The
labelling machine is characterized by the fact that the axes of
all the followers 26 , 27 , 28 , 29 is located inside a moving
equivalent cam surface of the cam mechanism while at least one of
the followers 26 , 29 lies partly outside the moving equivalent
cam surface.
The labelling machine portions of all of the followers 26 ,
27 , 28 , 29 lying partly outside the moving equivalent cam
surface. At least some of the followers 26 , 27 , 28 , 29 may
be offset from one another by an angle which is not equal to 90
degrees and have lever arms of different lengths.
Preferably, either two followers 26 , 29 include large
lever arms, or two followers 27 , 28 include small lever arms
with one follower 26 , 29 having a large lever arm for engagement
w~th the cams 32 , 33 .
The labelling machine is preferably characterized by the
following engagement alternatives:
a) With the adhesive application roller 15 , two followers
27 , 28 with small lever arms are engaged for transmitting
torque, and one follower 26 with a large lever arm for
supporting from the other side.
b) With the label box 16 , one follower 26 with a large
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lever arm is engaged for transmitting torque, and one follower
*
29 with a large lever arm for supporting from the other side.
c) With the label transmission cylinder 18 , one follower
*
29 with a large lever arm is engaged for transmitting torque,
* *
and two followers 27 , 28 with small lever arms for supporting
from the other side.
The labelling machine may be characterized by the fact that
the follower 26 transmitting torque to the label box 16 corre-
sponds to the cam 32 closer to the drive or bearing shaft 25 .
Additionally, each set of followers 26 -29 comprises one
follower 26 , 29 with a large lever arm and an opposite follower
* *
27 , 28 with a small lever arm.
The labelling machine is further characterized by the fact
that the orbit RA of the drive shaft 6 of the extracting element
2 is less than the orbit RL of the bearing shaft 25 of the
extracting element 2 . Still further, when the transmission
mechanism 19 -26 lies between the drive shaft 6 and the bearing
shaft 25 , at least one follower 26 with a large lever arm is
tangent to or projects beyond the arc of the gear wheel 123 ,
23a , 23b located on the bearing shaft 25 . Finally, the
followers 26 , 27 can consist of rollers 26b , 27b mounted on
bearing pins 26a , 27a , whereby the bearing pins 26a , 27a
located closest to the bearing shaft 25 are connected integrally
with the support element 24 , which supports the gear wheel 123 ,
23a , 23b on a radially recessed projection thereof.
The support element illustrated in Figures 20 through 22
includes an inside body 1 and an outside body 2 , which are
not in direct contact with one another. Insert 3 , made of
**
elastic material, is positioned in the space between bodies 1
and 2
Inside body 1 is designed to be fastened on a drive shaft
of an extracting element for labels. For this purpose, it has a
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middle part 4 and a sleeve 5 attached to one end. Middle
part 4 supports a number of claws 6 directed radially
outwardly along the circumference. The width of the claws 6 is
significantly less than the distance between claws 6
**
Outer body 2 has the basic shape of a basin with central
opening 7 , through which middle part 4 projects by means of
sleeve 5 . Outer body 2 has radially inwardly-directed claws
8 , which lie between claws 6 of inner body l . In each of
inner claws 8 there is hole 9 , which is used to hold the
bearing pivot of a cam follower. A threaded fastener (not
shown) is provided for insertion within radially threaded hole
11 in the outer wall 10 of the basin-shaped outer body 2 to
axially secure the bearing pivot inserted in hole 9 . End wall
12 , which covers the spaces between claws 8 is positioned on
the end side adjacent to outer body 2
There is a space on all sides between inner and outer bodies
1 and 2 . The space is between the engaged claws 6 and 8
between end wall 12 and the end side of claw 6 facing it and
between the inner annular surface of central opening 7 in outer
body 2 and outer annular surface 7a of inner body 1 . This
space is filled by elastic insert 3 , which is relatively thin.
The result is contact and support over a large area, which can
absorb the forces which occur in all axes without danger of over-
loading, while maintaining the damping action. For axial protec-
tion, radial holes 13 and blind holes 14 are positioned in
** ** **
the vicinity of claws 6 . Holes 13 and 14 are axially
aligned with one another in pairs and are filled by the elastic
** **
material of insert 3 . The elastic material of insert 3 is
installed jointly with the material for radial holes 13 and
blind holes 14 by injection.
The support element illustrated in Figures 23 and 24 has
essentially the same structure as the support element illustrated
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in Figures 20 through 22. Therefore, the following description,
primarily, discusses the differences between them.
In the embodiment depicted in Figures 23 and 24 only two
diametrically opposite claws 8a of the outer body 2a are
provided for the insertion of cam followers. The number of
inwardly directed claws 8a and outwardly directed claws 6a
engaged with one another is therefore reduced to four. Moreover,
outer body 2a has gear teeth on its periphery, so that the sup-
port element can also serve as a drive pinion. Finally, the
coaxial annular surfaces above one another of outer body 2a and
of inner body la are formed by coaxially overlapping sleeve-
shaped prosections 16 and 17 of the outer and inner bodies.
Compared to the inner annular surface in the embodiment
illustrated in Figures 20 and 22, the annular surfaces of the
. . .
embodiment of Figures 23 and 24 are significantly larger, which
increases the angular rigidity of both bodies la and 2a
Figures 25 through 28 show a labelling station which may
employ either of the æupport element described above. The label-
ling station includes a driven, rotating support 21 , with
extracting elements 22 through 25 mounted on it so that they
can pivot or rotate and stations positioned along the
~ `*
circumference of support 21 . These stations are adhesive
application roller 26 , label box 27 and gripper cylinder
28 . Extracting elements 22 through 25 are driven by a cam
transmission mechanism when support 21 rotates thereby rolling
elements 22 through 25 over the surfaces of stations 26
through 28
Each extracting element is mounted by means of bearing shaft
29 on support 21 . Pinion 30 is on bearing shaft 29 and
.~ ** *~
is engaged with two-part gear wheel 15 and 15a . The two-part
design is intended to offset the two parts, somewhat, from one
another resulting in an adjustment of the engagement which is
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free from play. Support element 2a , which includes two-part
** ~`*
gear wheel 15 and 15a , is rotationally connected to drive
shaft 31 which, in turn, is mounted in support 1
In the embodiment illustrated in Figures 25 and 26, the
support element is equipped with single follower 32 , which
includes bearing pivot 32a which supports rollers 32b and
** ** **
32c . Follower 32 is engaged in grooved cam 33 of
stationary cam support 34 . Rollers 32b and 32c are
unilaterally guided on opposite flanks 33a and 33b
When support 21 rotates, the support element and thus also
extracting element 22 is pivoted corresponding to the path of
grooved cam 33 , so that it rolls over the surfaces of the
individual stations 26 through 28 . This causes element 22
**
sequentially, to receive glue from application roller 26 , apply
the adhesive to the top label in label box 27 , remove the top
~ `"-
label from box 27 and transfer the label to gripper cylinder
28
The embodiment illustrated in Figures 27 and 28 differs from
the embodiment illustrated in Figures 25 and 26 in that the
support element is equipped with two followers 35 and 36
which support bridge element 37 . Bridge element 37 is also
equipped with two followers 38 , which are offset by
approximately 90 degrees from followers 35 and 36 . Figure 28
shows only one of the two followers. Corresponding to the two
pairs of followers are two overlapping and separate one-sided
outer cams 39 and 40 of common stationary cam support 41
** **
In the space between the two outer cams, 39 and 40 , is bridge
element 37 . Outer cams 39 and 40 have the basic shape of
indented ovals and are oriented crossways to one another. When
support 21 rotates-, the support element and the extracting
element are rotated in the same direction causing the extracting
** **
element to roll over the surface of stations 26 through 28
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Bridge element 37 allows outer cams 39 and 40 to be
completely filled thereby allowing the support element and the
extracting element 22 to be clearly guided. Bridge element
37 , thus, allows upper outer cam 39 to extend into vicinity
42 of the axis of the drive shaft 31
Although for purposes of illustration the cam followers
shown have been attached through a mounting to a support which is
then attached to a drive shaft, it is to be understood that the
followers may also be directly connected to the drive shaft. In
this embodiment the elastic dampening material would be
interposed directly between the mounting for the followers and
the drive shaft.
In summary, what is provided is a support element mounted on
** ** ** ** **
a shaft 31 for the followers 32 , 35 , 36 , 38 of a cam
drive mechanism, in particular a mechanism for a label extracting
element 22 to 25 and a labelling station, characterized by
the fact that the support element comprises an outer body 2
2a and an inner body 1 , la located inside it at some
distance from it on all sides, whereby the outer body 2 , 2a
has claws 8 , 8a directed radially inward, and the inner body
1 , la has claws 6 , 6a directed radially outward between
the inwardly directed claws and the space between the two bodies
1 , la , 2 , 2a is filled with an insert 3 , 3a of
elastic material, and that the inwardly directed claws 8 , 8a
~ `* **
of the outer body 2 , 2a are designed for the insertion of
** ** ** **
followers 32 , 35 , 36 , 38 . The support element is
characterized by the fact that the spaces between the claws 8
8a of the outer body 2 , 2a are enclosed by an end wall
12 , 12a and that between this end wall 12 , 12a and the
** ** ** **
end surfaces of the claws 6 , 6a of the inner body 1 , la
** **
facing it, elastic insert 3 , 3a is located.
Also, the support element is characterized by the fact that
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between the two bodies 1 , la , 2 , 2a there are annular
surfaces which extend axially, between which the elastic insert
** **
3 , 3a is located. Further, the support element is charac-
terized by the fact that the annular surfaces are formed by
sleeve-shaped projections 16 , 17 of the inner and outer
bodies 1 , la , 2 , 2a located coaxially above one another.
Additionally, the support element is characterized by the fact
that the annular surfaces make the transition gradually into the
radially inward surfaces of the inwardly-directed claws 8a of
the outer body, in the spaces containing the outwardly-directed
claws 6a of the inner body la and containing the claws 8a
of the outer body 2a
The support element is further characterized by the fact
** ** ~:* **
that there are several radial recesses 13 , 13a , 14 , 14a
.. . . . . . . .. . . . . . . . . . . . . . . .
in the inside and outside body 1 , la , 2 , 2a , which are
filled with a slug of elastic material connected with elastic
insert 3 , 3a . Also, the support element is characterized by
** ** ** **
the fact that the recesses 13 , 13a , 14 , 14a with the slug
are on the outside circumference of the support element.
Further, the support element is characterized by the fact that
** ** ** **
the recesses 13 , 13a , 14 , 14a are aligned with one
another in pairs. Additionally, the support element is
characterized by the fact that the outer body 2 has a drive
~ `*
pinion 15
Also provided is a labelling station for objects, in
particular, bottles with several stations located behind one
another along a track, namely an adhesive application apparatus
26 , a label transfer station 28 , and with at least one
extracting element 22 to 25 for the labels, mounted so that
it can rotate on a rotating support 21 and be moved passed the
stations 26 , 27 , 28 during each rotation of the support
21 , which extracting element has an outwardly-curved receptacle
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surface for the label which rolls along the currently foremost
label in the label feed station 27 and the other stations
whereby the drive for each extracting element 22 to 25 is a
cam drive, which comprises common, stationary double cams 33
** ** ** ** ** **
33a , 33b , 34 , 39 , 40 , 41 for all the extracting
elements 22 to 25 and one or more interacting followers 32
** ** ** ,`*
35 , 36 , 38 which are mounted on the drive shaft 31 or on
**
a bearing shaft 60 coupled with it by means of a support
** ~* ** **
element 1 , 2 , la , 2a and which by means of the form-fit
** ** ** ** ** ** **
with the double cam 33 , 33a , 33b , 34 , 39 , 40 , 41
protect the rotational movement of each extracting element 26
to 28 when the support 21 rotates, characterized by the fact
that the driver bearing shaft 31 ends in front of the plane of
the followers 32 , 35 , 36 , 38 and the support element 1
** ** **
2 , la , 2a is designed for the optional insertion of a
single follower 32 , which is engaged with a double cam 33
33a , 33b , 34 designed as a grooved cam, or for the
** **
insertion of two followers 35 , 36 diametrically opposite one
another in relation to the axis of the drive shaft 31 where the
bearing shaft, which interact with a first one-sided cam 39 of
the touble cam 39 , 40 , 41 and support a bridge element 37
which is located between the first cam 39 and a second cam 40
located at some distance from it and which supports followers
38 off-set from the followers 35 , 36 of the first cam 39
by approximately 90 degrees in interacting with the second cam
40**.
The labelling machine illustrated in Figure 29 through 32
***
includes rotating transport table 1 , which moves containers
2 so that they may be labelled. The containers are moved on a
track, in the form of a circular arc, past gripper cylinder 3
. ,, ***
which transfers a label with adhesive to container 2 . Gripper
cylinder 3 takes the glued label from curved receptacle
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surfaces 4 of extracting elements 5 . Elements can rotate
eccentrically to curved receptacle surface 4 on support table
***
6 , or may be mounted so that they can rotate or pivot eccen-
trically to ~he support axis.
Each extracting element 5 is driven when support table
***
6 is in rotation by means of a transmission, which includes
***
cam disc 7 , which is common for all extracting elements 5
and which has ~wo outside cams, 7a and 7b , at different
heights and drive wheel 8 on which are mounted cam followers
*** *** *** ***
8a 9 8b , 8c and 8d . The driving of extracting
elements 5 , as ind~cated in Figure 20, can be accomplished
directly by means of transmission 120 and 121 . The
***
rotational or pivoting movement of extracting elements 5 is
not uniform, so that their receptacle surfaces can roll over
*** ***
adhesive application roller 9 , stationary label box 10 and
J.~_*
gripper cylinder 3 , in the same direction.
With the embodiment of a design as illustrated in Figures 29
and 32, the drive of each extracting element 5 is by means of
a cam transmission consisting of two outside cams, 7a and
***
7b which are positioned at different heights and followers
*** *** *** *** t~** ***
8a , 8b , 8c and 8d which ride on cams 7a and 7b
The transmission mechanism in the embodiment illustrated in
*** ***
Figure 30 consists of cam disc 19 with grooved cam slot l9a
and followers 18 in the form of rollers mounted on a lever arm
***
17
Support table 6 , as shown in Figure 30, has upper cover
plate lla , housing 11 and, underneath it and connected to
it, bearing structure 12 which is mounted on the outside
~**
circumference of the table 6 by means of angular roller
*** ***
bearing 13 . Bearing structure 12 is also used to mount
drive shafts 15 , which extend upward through cover plate
*** ***
lla and support extracting elements 5 , and to mount bearing
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shafts 16 which support followers 18 through lever arms
17 . Followers 18 engage closed grooved cam l9a , which
is common to all followers 18 , of the cam disc 19 . Closed
groove cam 19a is similar in construction to grooved cam 33
in Figure 25. Pinions 20 mesh with gear wheel 21 on drive
shafts 15 of the extracting elements 5 and are mounted so
that they do not rotate on the bearing shafts 15 . Gear wheel
***
21 meshes with a gear wheel of the synchronously driven
adhesive application roller 23
***
In central space 24 , left open by the drive and transmis-
sions of the extracting elements, between cover plate lla and
***mounting plate 25 , there is an axially retractable spur gear
coupled with one coupling half, 26 , which is fastened to
mounting plate 25 and the other coupling half, 27
Coupling half 27 is biased by coil spring 28 so that it is
normally held in direct contact with coupling half 26 when
hand lever 39 is lowered. For this purpose, coupling half
27 i8 in contact with annular disc 29 , which is supported
by central drive shaft 30 which is a hollow shaft. Hollow
drive shaft 30 extends downward through a central opening in
base plate 31 of machine frame 14 , where it is mounted and
***
supports belt wheel 32 which is normally connected to a drive
belt which extends from a drive (not shown).
Bumper 33 runs through hollow drive shaft 30 and has
stationary crosshead 34 on its upper end, which extends with
both legs through axial slits in drive shaft 30 and is
connected with coupling half 27 . Bumper 33 runs through a
central opening of marking disc 35 which, in turn, is inserted
in an opening of cover plate lla . On its free end, bumper
*** *** ***
33 supports marking wheel 36 with notch 37 which
corresponds to marks 38 on marking disc 35 . The spacing of
marks 38 coincides with the spur gear teeth of coupling halves
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26 and 27
To disengage the two coupling halves 26 and 27 , so
***
that support table 6 can be twisted relative to drive shaft
and with the marking ring 36 , bumper 33 ^ is lifted by
***
means of hand lever 39 , the lower end of which supports bumper
33 * .
Figure 30 illustrates the retracted state of coupling halves
*** ***
26 and 27 . After uncoupling, the labelling station, as
shown in Figure 29, can be rotated independently of the machine
drive and can be set up in the desired position for the label to
be transferred. The degree of misalignment can be read from
*** ***
markings 37 and 38
The embodiment illustrated in Figure 32 differs, as noted
above, from the embodiment illustrated in Figure 30 principally
in terms of the transmission. Figure 32, moreover, does not show
the coupling. The embodiment in Figure 32 is primarily intended
to show the compact construction, because in this embodiment the
transmission with the cams extends almost up to drive shaft 130.
For the sake of simplicity, in this embodiment, the same
identification numbers are used as in Figure 30, but are preceded
by the number 1.
In the embodiment illustrated in Figure 32, cam disc 119
is designed as a bridge element and supports two outside cams,
7a and 7b , in two different planes. Followers 8a
*** *** *** *** ***
8c , 8b and 8d interact with outside cams 7a and 7b
and are mounted on drive wheel 8 , which is engaged by drive
pinion 120 with pinion 121 positioned on the drive shaft of
extracting element 115 . Bridge element 140 , which is
*** ***
supported by the bearing pivot of the followers 8a and 8c
is provided to support the bearing pivots of the lower followers
*** ***
8b and 8d
; In summary, a design provides a labelling station of a
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labelling machine for containers, in particular bottles 2
*** ***
which have a support 6 , and a support table 11 . The
support 6 can be driven via a coupling 26 , 27 , by a
central drive shaft 30 , supports at least one extracting
***
element 5 and is moun~ed so that it can rotate in the machine
frame 14 . When the support 6 rotates, the extracting
***
element 5 which has in particular a curved receptacle surface
***
4 and is mounted on it eccentrically so that it cam rotate or
pivot around its own axis and is moved along a closed track past
*** *** ***
stations 3 , 9 , 10 for the application of adhesive to the
receptacle surface and for the storage and transfer of labels.
For each extracting element 5 , for whose rotating or pivoting
**~` ***
motion there is a transmission 16 -21 , in particular a cam
transmission, with a common transmission part, in particular a
. . . . . .... . . . ... . . . ....... . . ..
cam disc 19 mounted on the machine frame 14 for all the
*** *** ***
extracting elements 5 . The mounting 13 of the support 6
in the machine frame 14 is located exclusively on the outside
***
edge of the support 6
~nother aspect of the above design resides in that the
*** *** ***
coupling 26 , 27 between the drive shaft 30 and the
***
support 6 is located inside a central space inside the orbit
described by the transmission 16 -21 , between the cover
*** *** *** ***
plate lla of the support 6 and the parts 16 -21 of the
transmission engaged with one another.
StiLl another aspect of the above design resides in that a
non-rotating bumper 33 extends through the drive shaft 20
designed as a hollow shaft and which can move axially inside it
and to each is attached a spring-loaded coupling half 27 of
the axially retractable coupling 26 , 27 , the end of which
*** ~**
projects from the table 11 of the support 6 , together with
*** ***
the adjacent portion 35 of the table 11 , has alignment
*** ***
.arks 37 , 38
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A further aspect of the above design resides in that the
coupling halves 25 , 27 are engaged with one another by
*** ***
means of spur gear teeth 26a , 27a , the spacing of which
corresponds to the spacing of the alignment marks 38
All, or substantially all, of the components and methods of
the various embodiments may be used with at least one embodiment
or all of the embodiments, if any, described herein.
The invention as described hereinabove in the context of the
preferred embodiment is not to be taken as limited to all of the
provided details thereof, since modifications and variations
thereof may be made without departing from the spirit and scope
of the invention.
,, , , ,, , ,,, , . . . . . , , ,, . . . . , .. . ., . . . .. ., ,, , , - . .
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