Roll lift and transfer apparatus

The disclosure is directed to apparatus (11) for lifting, maneuvering and transferring a roll of material to an independently supported shaft (93). The apparatus is adapted for suspension from an overhead crane and comprises an elongated frame (12) the lower end of which is pivotally connected to a torque assembly (14) that includes a center probe (15). The center probe includes a plurality of radially expanding teeth (49) that engage the inner surface of the roll core and retain it on the center probe (15). An actuator (13) of the extensible-retractable type is pivotally connected between the upper end of the elongated frame (12) and one end of the torque arm assembly (14). Extension and retraction of the actuator (13) causes the torque arm assembly (14) and center probe (15) to move between substantially vertical and horizontal positions. The extreme end of the center probe includes a coupler (61) that releasably interlocks with a coupler (94) secured to the end of the machine shaft (93). The couplers permit the center probe and machine shaft to be interlocked in coaxial relation. A circular vacuum plate (67) is axially movable by pneumatic actuators (82, 83) between a retracted position in which a roll of material may be received on the center probe, and an extended position in which the roll of material is forceably transferred from the center probe to the machine shaft (93).

TECHNICAL FIELD 
The invention is generally related to apparatus for lifting and maneuvering 
a roll of material having an externally accessible axial opening, and is 
specifically directed to apparatus of this type which is capable of 
transferring a roll of material to and from an independently supported 
shaft, such as the shaft of a winding/unwinding machine. 
BACKGROUND OF THE INVENTION 
Many products, such as paper, film, foil, textile, sheet metal, rope, yarn 
and wire are wound on rolls, coils, reels or spools which weigh from 50 to 
10,000 pounds. Many cannot be lifted or maneuvered manually and require 
the intervention of some type of powered lifting apparatus. 
A number of power lifting devices and related structures are known. See, 
for example, U.S. Pat. Nos. 3,263,938, 3,391,876, 3,423,120, 3,445,076, 
3,734,328, 3,758,144 and 4,154,470, all of which issued to Herbert F. 
Dalglish. 
A problem often encountered with the lifting and maneuvering of such heavy 
rolls of material is the transfer from the lifting apparatus to the shaft 
of a coil winding/unwinding machine. Typically, such a machine includes a 
rotatable shaft that is horizontally disposed and supported in cantilever 
fashion. The roll is maneuvered by the lifting apparatus so that its axis 
is horizontally disposed, and the lifting apparatus is thereafter brought 
to the winding/unwinding machine with the center probe of the lifting 
apparatus and the shaft of the machine in coaxial alignment. 
Assuming that the operator can maintain the lifting apparatus in this 
aligned position, the roll is then physically transferred from the lifting 
apparatus to the shaft by physical strength. If the roll is particularly 
heavy, more than one operator may be necessary to push the roll from the 
lifting apparatus to the machine shaft. This task is not only difficult 
because of the size and weight of the rolls, but it is also difficult and 
dangerous. Alignment of the machine shaft with the center probe is easily 
lost, and if the lifting apparatus is supported from a single point on an 
overhead crane, continued registration is particularly difficult. Further, 
even when the center probe and machine shaft are aligned, it is possible 
for the roll to be dropped from its elevated position during the transfer 
process, and this is always dangerous to the operator or operators 
involved. 
SUMMARY OF THE INVENTION 
The present invention is the result of an endeavor to overcome these 
problems. 
The invention is embodied in a roll lifting apparatus of the type disclosed 
in the aforementioned U.S. Pat. No. 4,154,470. This apparatus is 
particularly suited for suspension from a movable overhead crane, and 
includes a center probe that may be moved by an actuator between 
substantially horizontal and substantially vertical positions. Mechanical 
retention means are associated with the probe that increase its effective 
diameter after the probe has been inserted into the actual core opening, 
permitting the roll to be lifted from either a vertical or horizontal 
at-rest position. 
The invention resides in the combination with the roll lifting apparatus of 
means for engaging the lifted roll and forcing it from the center probe 
after alignment with a machine shaft or the like has been achieved. In the 
preferred embodiment, the inventive apparatus includes coupling means for 
releasably connecting the center probe and machine shaft together before 
the transfer operation begins. 
In the preferred embodiment, the roll transfer or unloading device 
comprises a large, circular plate that is concentrically disposed in 
encircling relation to the center probe and axially movable relative 
thereto between a retracted position in which the roll of material may be 
received, and an extended position in which the roll is forceably 
transferred from the probe. The circular plate is provided with means for 
creating a vacuum between the plate and the roll end, which serves to 
assist the mechanical roll retention means associated with the probe 
means, and also to preclude telescoping of the material on the roll. 
The circular vacuum plate is moved between the retracted and extended 
positions by a plurality of pneumatic actuators that are carried by the 
main frame and operable by the operator through a control valve. 
Preferably, the coupling means comprises a first coupler disposed at the 
end of the center probe and a second coupler adapted for connection to the 
machine shaft. The two couplers matably interlock by dropping the first 
coupler end from above into the second coupler. This provides a strong 
interlocking engagement, maintaining the center probe and machine shaft in 
coaxial relation, but also permits simple release by raising the roll 
lifting apparatus after roll transfer has been accomplished. 
Preferably, the first coupler is spring loaded into a projecting position 
and retractable within the center probe when it engages a fixed object, 
such as the floor or other supporting surface for the roll. Thus, for 
example, if the roll of material is being stored on one end (i.e., with 
the core axis vertically disposed), the center probe is inserted until the 
vacuum plate engages the top end of the roll. Where the roll is of lesser 
axial length than the center probe, the first coupler will engage the 
floor or other roll supporting surface and withdraw into the center probe 
until the roll is lifted from the supporting surface. As the roll is 
lifted, the first coupler projects beyond the end of the roll, thus 
insuring that it will be exposed for coupling with the second coupler. 
With the use of the inventive apparatus, a single operator may lift a heavy 
roll of material from its supporting surface, maneuver it adjacent the 
machine shaft to which the roll is to be transferred, cause the probe and 
shaft to be coupled and transfer the roll from the center probe to the 
machine shaft quickly and efficiently.

DESCRIPTION OF THE PREFERRED EMBODIMENT 
With initial reference to FIGS. 1-3, a roll lift and transfer apparatus is 
represented generally by the numeral 11. Apparatus 11 comprises an 
elongated frame 12, an elongated actuator 13 that is pivotally connected 
at its upper end to the elongated frame 12 and a torque arm assembly 14. 
The rear end of the torque arm assembly is pivotally connected to the 
lower end of the elongated actuator 13. The elongated frame 12 is 
pivotally connected to the torque arm assembly 14 so that extension and 
retraction of the actuator 13 causes the torque arm assembly 14 to swivel 
between substantially vertical and substantially horizontal positions. 
A probe assembly bearing the general reference numeral 15 (FIGS. 2 and 3) 
projects axially forward from the torque arm assembly 14, and as described 
in further detail below, is constructed for insertion into and retainable 
engagement with the core of a roll to be lifted. 
Apparatus of this type is disclosed and claimed in U.S. Pat. No. 4,154,470, 
which issued to Herbert F. Dalglish on May 15, 1979. 
The elongated frame assembly 12 specifically comprises a pair of elongated 
frame members 16, 17 that are rigidly held in spaced, parallel relation by 
a rectangular plate 18 (FIG. 1) and the pivotal connection to the torque 
arm assembly (FIG. 3). 
With additional reference to FIG. 1a, a second rectangular plate 19 is 
welded between the frame members 16, 17 at their upper end. A pair of 
smaller plate members 21, 22 are welded to the rear side of plate 19, 
projecting perpendicularly therefrom in spaced relation. Two pairs of 
aligned bores are formed in the plates 21, 22 and respectively receive 
transverse pivot pins 23, 24. The upper pin secures an end link 25 used 
for connecting the apparatus to an overhead crane or the like. 
The lower pivot pin 24 serves as the pivotal connection between the frame 
12 and actuator 13. This is accomplished by securing a lug 26 to the upper 
end of the actuator 13 with a transverse bore through which the lower 
pivot pin 24 projects. 
Actuator 13 comprises a reversible electric motor 27 that is carried within 
a housing 28. The pivot lug 26 is secured to the housing 28. 
A tubular body 29 projects downwardly from the housing 28 adjacent the 
electric motor 27. An extensible and retractable tube 31 is slidably 
carried within the tubular body 29. Extension and retraction of the tube 
31 is effected through a gearing arrangement (not shown) including a gear 
and pinion set coupled to a jack screw and nut that travels with the 
extensible tube. The actuator further includes a bidirectional brake that 
prevents movement when the motor is not turning, and a slip clutch that 
protects the actuator from overload. Reference is made to U.S. Pat. Nos. 
3,559,499, 3,587,796 and 3,704,765 for further details of the actuator. 
Motor 27 is energized through an electric power line 32 and control of the 
motor is accomplished through a control box 33 having a forward/reverse 
switch 34. Control box 33 is removably mounted on the tubular body 29, and 
is connected to the motor 27 through an electric control line 35. Control 
line 35 is of sufficient length to permit removal of the control box 33 
from the unit for remote control purposes. When the control box 33 is in 
its mounted position, the control line 35 is wound on a pair of brackets 
36 suitably mounted on the tubular body 29. 
With reference to FIGS. 2 and 3, the torque arm assembly 14 comprises a 
pair of heavy, elongated plate members 37, 38 that are held in spaced, 
parallel relation by a rectangular plate 39 that is welded on the bottom 
edges thereof, and a larger plate 42 having tapered sides that is welded 
to the top edges thereof. The tapered plate member 42 extends axially 
beyond the ends of the elongated plates 37, 38, and a collar block 43 
underlies the plate 42, being welded thereto as well as the ends of the 
elongated plates 37, 38. 
As best shown in FIG. 3, the lower ends of the spaced frame members 16, 17 
of elongated frame 12 are pivotally secured to the collar lock 43 by bolts 
44, 45, respectively. 
With reference to FIGS. 2, 3 and 6, the probe assembly 15 comprises a 
stationary cylindrical member 46 one end of which is rigidly secured to 
the collar block 43 by the bolts 44, 45 (FIG. 3). The probe assembly 15 
further comprises a cylindrical shell or sleeve 47 that is sized for 
sliding movement axially of the cylindrical member 46. The rear end of the 
cylindrical sleeve 47 is secured to an elongated plate 48 that is 
transversely disposed of the probe assembly axis. As constructed, the 
cylindrical sleeve 47 and elongated plate 48 are capable of axial movement 
together relative to the stationary cylindrical member 46. 
A plurality of teeth 49 of angular cross section are carried by the 
cylindrical member 46 for rockable movement radially inward and outward. 
In their radially outermost positions (FIGS. 2 and 3), the teeth 49 
project through appropriately disposed window openings 51 in the 
cylindrical sleeve 47. The teeth 49 are normally urged radially inward by 
resilient means (not shown) so as to be withdrawn from the openings 51. As 
shown in FIGS. 2 and 3, the forward side of each tooth 49 is angular, so 
that rearward sliding movement of the sleeve 47 relative to the 
cylindrical member 46 enables each tooth 49 to rock within the associated 
opening 51 and thereby retract under the influence of the resilient means. 
In this position, the lower internal edge of the opening 51 is maintained 
in contact with the retracted tooth 49 even though it is radially 
withdrawn. Locking means may be included to maintain the sleeve in this 
position. 
Forward sliding movement of the sleeve 47 causes the edge of the associated 
opening 51 to move against the transverse rearward edge of each tooth 49, 
causing it to rock forwardly against the bias of the resilient means and 
to project from its associated opening 51 for engagement with the core of 
the roll to be lifted. Reference is made to U.S. Pat. No. 3,423,120, which 
issued to Herbert F. Dalglish on Jan. 21, 1969 for further details of the 
structure and operation of probe assemblies of this type. 
With continued reference to FIGS. 2 and 3, a pair of stationary handles 52, 
53 are rigidly secure to the underside of plate 39 to permit an operator 
to maneuver the apparatus 11. As shown in FIG. 3, the handles 52, 53 
extend transversely of the torque arm assembly 14. 
Pivotally mounted to the underside of torque arm assembly 14 (at plate 39) 
is a third handle 54 that is disposed just forward of the handle 52. An 
elongated linkage rod 55 has one end pivotally connected to the handle 54 
at an intermediate point thereof, with the other end extending forwardly 
for slidable insertion into a cylindrical connector 56 (FIG. 2). The 
forward end of connector 56 is pivotally connected to an ear 57 that is 
secured to the elongated plate 48. Internally of the connector 56 is a 
spring and spring retainer (not shown) the purpose of which is to normally 
urge the linkage rod 55 and handle 54 forwardly. This function is assisted 
by a coil spring 58 which is compressibly disposed between the handles 52 
and 54 (FIG. 3). 
As constructed, squeezing the handle 54 relative to the handle 52 draws the 
linkage rod 55 rearwardly, which in turn retracts the elongated plate 48 
and cylindrical sleeve 47 relative to the stationary cylindrical member 
46. This permits the teeth 49 to rock radially inward out of engagement 
with the lifted roll. 
With reference to FIG. 6, the stationary cylindrical member is considerably 
shorter than the cylindrical sleeve 47, but its effective length is 
extended by a coupler 61. Coupler 61 has a diameter the same as that of 
the cylindrical member 46, and it is also slidably disposed within the 
cylindrical sleeve 47. However, it is normally retained in the position 
shown in FIG. 6; viz., projecting beyond the end of sleeve 47. 
Coupler 61 is capable of retraction into the cylindrical sleeve 47. It is 
formed with a blind axial bore 62 sized to receive the head of an 
elongated bolt 63. Bolt 63 is screwed into a threaded bore 64 extending 
axially in the end of cylindrical member 46. A spring 65 is disposed in 
compression between the cylindrical members 46 and the coupler 61, urging 
the coupler 61 into its projecting position as shown. However, if the 
coupler 61 engages another object (e.g., the floor when the probe assembly 
15 is moving vertically downward), it will retract into the cylindrical 
sleeve 47. 
With reference to FIGS. 2-5, a large, circular vacuum plate assembly is 
represented generally by the numeral 67. The assembly 67 comprises an 
annular backing plate 68 through which a flanged hub member 69 projects 
rearwardly. The inside diameter of the hub 69 corresponds to the external 
diameter of the sleeve 47, permitting the assembly 67 to slide axially of 
the probe assembly 15. 
A composite circular flange 71 projects forwardly from the periphery of 
annular plate 68. The flange 71 comprises an underlying support section 
formed from the same material as the annular plate 68 (preferably cast 
metal) and a seal formed from a resilient material such as rubber. 
A second circular seal 72 is secured to the periphery of the hub member 69. 
The outer faces of the seals 71, 72 lie in the same plane, and with 
contact with a planar surface (such as the end of a roll of material), an 
annular vacuum chamber is defined thereby. 
Extending radially between the seals 71, 72 are a plurality of composite 
ribs 73-78, each of which comprises an underlying support section and a 
resilient sealing strip. However, as shown in FIG. 4, the ends of each of 
the ribs 73-78 is spaced from the respective seals 71, 72 to permit vacuum 
communication throughout the annular vacuum chamber when contact with the 
end of a roll of material is made. Further, and as best shown in FIG. 5, 
the axial dimension or thickness of the ribs 73-78 is slightly less than 
that of the seals 71, 72. This permits a full communication of vacuum, 
while resisting telescoping of the roll of material radially within the 
annular vacuum chamber. 
With reference to FIGS. 2 and 4, a nipple 79 projects from the rear surface 
of the annular plate 68 and communicates with the annular vacuum chamber. 
A hose 81 connects the nipple 79 with a source of vacuum. 
Reference is made to the aforementioned U.S. Pat. No. 3,758,144, which 
discloses a vacuum center lift of this general type. 
With reference to FIGS. 2, 3 and 5, a pair of pneumatic actuators 82, 83 
are mounted at the outboard end of the elongated plate 48, projecting 
rearwardly therefrom. The actuator 82 includes an extensible rod 82a that 
projects through the plate 48 and is threaded into a connector 84 welded 
to the back face of annular backing plate 68. Actuator 83 has a similar 
rod 83a connected to a connector 85. 
As constructed, the actuators 82, 83 are employed to force the vacuum plate 
assembly 67 axially between a first retracted position (see the full lines 
in FIG. 3) in which a roll of material may be received on the probe 
assembly 15, and an extended position (see the phantom lines in FIG. 3) in 
which the roll of material is forced off the probe assembly 15. The stroke 
of the actuators 82, 83 is chosen as a function of the length of the probe 
assembly 15 so that the vacuum plate assembly 67 does not extend beyond 
the probe assembly 15. 
Extension and retraction of the pneumatic actuators 82, 83 is controlled by 
a conventional control valve 86 mounted to the bottom edges of plates 37, 
38 adjacent the plate 39, and having a manually operable handle 87. Valve 
86 is adapted for connection to a source of air under pressure and 
communicates with each of the actuators 82, 83 through a pair of 
supply/return lines (not shown). Handle 87 is operable to control valve 86 
from a neutral position (the position shown in FIG. 2) to extension and 
retraction positions in which the actuators 82, 83 are respectively 
extended and retracted. Preferably, the handle 87 is normally biased to 
the neutral position. 
With reference to FIGS. 6-8, coupler 61 defines a circular flange 91 at its 
extreme end of predetermined diameter and which is centered on the axis of 
the probe assembly 15. The flange 91 is spaced from the main body of 
coupler 61 by a stepped region 92 of lesser diameter that defines a 
circumferential groove 93. 
With specific reference to FIGS. 7 and 8, the shaft of a winding/unwinding 
machine to which the roll of material is to be transferred bears the 
general reference numeral 93. The extreme end of the shaft 93 is provided 
with a mating coupler 94 consisting of an annular segment 95 welded to the 
end of the shaft 93. As shown in FIG. 8, shaft 93 is tubular, and the 
upper edge of its extreme outer end is formed with a beveled surface 96 to 
facilitate entry of the flange 91 into its defined slot. 
Also as shown in FIG. 8, the outside diameter of circular flange 91 is less 
than the inside diameter of the shaft 93, and the diameter of the stepped 
region 92 corresponds to the inner diameter of the annular segment 95 to 
provide a snug fit. With the couplers 61, 94 in coupling engagement, the 
probe assembly 15 and shaft 93 are coaxially disposed. 
In operation, the apparatus 11 is suspended from a movable overhead crane 
or the like as shown in FIG. 1. To lift a vertically stacked roll of 
material and transfer it to a winding/unwinding machine, the operator 
first operates the switch 34 in control box 33 to retract actuator 13. 
This causes the torque arm assembly 14 and probe assembly 15 to assume a 
substantially vertical position with the probe assembly 15 pointing down. 
The overhead crane is then operated to orient the apparatus 11 over the 
selected roll of material. At this point, the handle 54 is squeezed 
relative to the handle 52 to cause retraction of the teeth 49, and the 
crane is lowered so that the probe assembly 15 enters the core of the 
roll. As the probe extends, the coupler 61 engages the floor or other 
supporting surface of the roll and withdraws or retracts into the sleeve 
47 against the bias of spring 65. 
When the vacuum plate assembly 67 engages the end of the roll, the handle 
54 is released and the teeth 49 are forced radially outward into a 
position biting into the inner surface of the roll core. Also at this 
time, vacuum is applied through the hose 81 to the vacuum plate assembly 
67 to insure that the roll of material will not telescope as it is raised. 
The crane is at this time operated so that the roll of material is lifted 
from its supporting surface, at which time the spring 65 urges the coupler 
61 outward to project beyond the roll. The operator then actuates the 
switch 34 of the control box 33 to extend the actuator 13 and move the 
torque assembly 14 and probe assembly 15 to a substantially horizontal 
position. 
At this point, the crane is operated to move the apparatus 11 and roll of 
material adjacent the shaft 93 to which the roll is to be transferred. The 
desired position of the roll of material, which is facilitated by the 
operator maneuvering the apparatus 11 with the handles 52, 53, is with the 
projecting coupler 61 slightly above the mating coupler 94, and with the 
probe assembly 15 and shaft 93 otherwise in general alignment. The crane 
is then lowered slightly so that the couplers 61, 94 matably engage with 
the probe assembly 15 and shaft 93 disposed in coaxial relation. 
The operator now releases the vacuum from vacuum assembly 67 and squeezes 
the handle 54 relative to the handle 52 to retract the teeth 49 in 
preparation for the roll transfer. The transfer is achieved by moving 
handle 87 to the extend position, which pressurizes the pneumatic 
actuators 82, 83, causing them to extend and drive the vacuum plate 
assembly 67 axially over the probe assembly. This moves the roll of 
material from the probe assembly onto the shaft 93. 
With the transfer complete, the valve 86 is operated by handle 87 to 
retract actuators 82, 83. At this point, the crane is raised to disengage 
coupler 61 from coupler 94, and the apparatus 11 is moved away for further 
operations. 
Transfer of a roll of material from the shaft 93 to the apparatus 11 is 
simply the reverse of the procedure described above. 
It will be appreciated that the apparatus 11 may be operated to lift a roll 
resting on its side on a supporting surface (i.e., with its axis 
horizontal), or to leave a roll of material on its side on the supporting 
surface. This is accomplished by leaving the actuator 13 in its extended 
position so that the torque assembly 14 and probe assembly 15 are always 
substantially horizontally disposed. Reference is made to U.S. Pat. No. 
4,154,470 with regard to the improved function of apparatus of this type 
in avoiding damage to the edge of a roll. 
As described hereinabove, it will be appreciated that the apparatus 11 is 
capable of lifting and transferring a roll of material of substantial 
weight through simple manipulation of a single operator with speed and 
efficiency, and without danger to the operator.