U.S. patent number 3,598,440 [Application Number 04/808,183] was granted by the patent office on 1971-08-10 for rotatable container-hoisting apparatus.
This patent grant is currently assigned to Fruehauf Corporation. Invention is credited to George W. Cooper, Charles D. Ramsden.
United States Patent |
3,598,440 |
Ramsden , et al. |
August 10, 1971 |
ROTATABLE CONTAINER-HOISTING APPARATUS
Abstract
Hoisting apparatus for cargo containers that permits the
containers to be oriented in any rotative position so that
containers can be positioned as desired in container cells, on dock
surfaces, and like locations. A cable guiding system in which the
spacing between the several vertical cable runs in the system can
be altered between a relative widely spaced, highly stable position
and a relatively closely spaced position at which the cable guiding
structure can enter into container cells without contacting the
walls that define the cell. An auxiliary frame adapted to be
mounted between the cable guiding structure and a conventional
container-engaging spreader frame, which auxiliary frame is adapted
to rotatively position a spreader frame and container engaged
thereby. The auxiliary frame includes sensors to determine the
degree of load imbalance, if any, of a container engaged thereby,
and a counterweight and a drive system for the counterweight that
positions the counterweight so as to compensate for any imbalance
arising from an eccentrically loaded container.
Inventors: |
Ramsden; Charles D. (Alameda,
CA), Cooper; George W. (San Leandro, CA) |
Assignee: |
Fruehauf Corporation (Detroit,
MI)
|
Family
ID: |
25198091 |
Appl.
No.: |
04/808,183 |
Filed: |
March 18, 1969 |
Current U.S.
Class: |
294/81.3;
212/274; 212/331; 212/279; 294/81.4 |
Current CPC
Class: |
B66C
19/002 (20130101); B66C 13/08 (20130101); B66C
1/101 (20130101) |
Current International
Class: |
B66C
13/04 (20060101); B66C 19/00 (20060101); B66C
13/08 (20060101); B66C 1/10 (20060101); B66c
001/00 () |
Field of
Search: |
;294/67,67.1A,67,4,81,8C,81SF ;212/10,11,125,14 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
Primary Examiner: Hornsby; Harvey C.
Claims
We claim:
1. In combination with a generally rectangular spreader frame that
includes thereon means for engaging a cargo container and means
connected to the frame at at least two spaced-apart points thereon
for raising and lowering the frame, the improvement that includes
apparatus for counteracting such imbalance as may exist in a
container engaged by the frame, said apparatus comprising a
counterweight, means for mounting said counterweight on said
spreader frame for movement along a path intermediate said
spaced-apart points, means for comparing the force due to gravity
at said two points, and means responsive to said force comparing
means for moving said counterweight toward the one of said two
points that has the least force applied thereto.
2. The invention of claim 1 in combination with first and second
blocks attached to said frame, each said block including a yoke
pivotally mounted therein, a sheave supported in each said yoke,
said sheaves being positioned at said two spaced-apart points on
said frame, means for limiting the degree of pivotal movement of
said yokes so that the force on said limiting means is proportional
to the tension on cables trained around said sheaves supported in
said yokes, a hydraulic load cell mounted to each said limiting
means, said load cells constituting an element of said force
comparing means and having hydraulic outputs at a pressure
proportional to the force applied thereon by said yokes, means
including electrical contacts for closing said contacts in response
to a pressure differential in said hydraulic outputs, and a motor
connected in circuit with said contacts for driving said
counterweight along said path.
3. The invention of claim 2 in combination with means including a
normally closed contact for opening said contact when a
differential pressure exists between said load cells, said normally
closed contact constituting an interlock circuit which is opened
when an unbalanced condition is sensed by the apparatus.
4. Container-hoisting apparatus for raising and lowering a
container that has a relatively long length dimension and a
relatively short width dimension into a vertically elongate open
top stowage cell that has similar dimensions in a horizontal plane,
said hoisting apparatus comprising a rectangular spreader frame
having length and width dimensions approximately equal to the
container and the cell, means on said spreader frame for engaging
the container, means for hoisting the spreader frame, said hoisting
means including at least two depending tension members attached to
the spreader frame at at least two points that are spaced apart by
a distance no greater than the width of the cell so that said
spreader can be lowered into the cell without interference, said
hoisting means further including first and second means for guiding
said tension members into at least two depending runs at the upper
end of said two depending tension members; and means for
positioning said first and second means towards and away from one
another to adjust the space between said depending tension members
at their upper end to a distance that is no greater than the width
of the cell, and a counterweight movable relative said frame for
compensating for unbalanced loads in said container.
5. Container-hoisting apparatus for raising and lowering a
container that has a relatively long length dimension and a
relatively short width dimension into a vertically elongate open
top stowage cell that has similar dimensions in a horizontal plane,
said hoisting apparatus comprising a rectangular spreader frame
having length and width dimensions approximately equal to the
container and the cell, means on said spreader frame for engaging
the container, means for hoisting the spreader frame, said hoisting
means including at least two depending tension members attached to
the spreader frame at at least two points that are spaced apart by
a distance no greater than the width of the cell so that said
spreader can be lowered into the cell without interference, and a
counterweight movable relative said frame for compensating for
unbalanced loads in said container, and means operably connected to
at least a plurality of said depending tension members for
detecting the difference in tension at said plurality of tension
members and means responsive to said detected tension differences
for positioning said counterweight.
Description
This invention relates to hoisting apparatus for hoisting cargo
containers during transportation of such containers between a dock
or like cargo storage area and a ship or like transport vessel.
A typical cargo container is of rectangular configuration in plan.
Container ships and like vessels adapted for transporting cargo
containers are provided with vertically extending walls that define
cells which in the plan aspect have a shape similar to and slightly
larger than the container so that the containers can be stacked one
on top of another in the cells. In order to utilize most
efficiently the volume in a ship's hold, a portion of the cells are
oriented with their longest dimension longitudinal of the ship and
another portion of the cells are oriented with their longest
dimension athwartship, or transverse of the length of the ship. It
is desirable to provide a single hoisting structure that can load
containers into the cells irrespective of the orientation of a
particular cell, and although copending commonly assigned Pat.
application Ser. No. 643,993, discloses a rotatable device for
achieving variable positioning of containers, such device cannot
enter into all container cells. The apparatus of the present
invention achieves improved operation over the subject matter of
said copending patent application and provides a loading apparatus
that is somewhat more versatile than such previously described
apparatus, since the present invention provides apparatus capable
of entry into cells irrespective of the orientation of the
cells.
The environment in which the present invention finds particular
utility includes a generally horizontally extending crane boom that
extends outwardly from a tower into a position overlying a ship or
like transport vessel. Mounted on the boom is a pair of parallel,
spaced-apart track rails. A carriage is rollably supported on the
rails and the carriage has supported thereon a plurality of cable
guide sheaves to guide the cable downwardly to permit raising and
lowering of a load. As described in U.S. Pat. No. 3,102,642, four
separate cable runs between the carriage and the load are desirable
to achieve load stability. Maximum spacing between the cables
affords stability to the load.
The permissible spacing between the cables is limited, however, by
the distance between the cell walls, because the cables cannot be
so widely spaced apart that they contact or rub the cell walls.
Moreover, the permissible spacing between the cables depends on
whether a container supported by the cables is positioned for
loading into a longitudinally extending cell or into a transversely
extending cell.
According to the present invention, a carriage is provided that has
means thereon for varying the spacing between the cables that
depend from the carriage. Thus, the cables can be adjustably spaced
apart to attain maximum possible stabilization without causing
interference with the cell walls.
The lower ends of the hoisting cables engage a so-called
quick-change headblock which includes sheaves through which the
cables are trained as well as means for effecting engagement of the
cargo container or like load to be hoisted.
The present invention provides a quick-change block that affords
adjustment of the spacing between the cable sheaves thereon so that
containers engaged thereby can be positioned for entry into either
longitudinally or transversely elongate cells.
Because, as pointed out above, many ships have some container cells
that are oriented longitudinally and some container cells that are
oriented transversely, it is desirable to provide a
container-engaging structure that can be rotatably or pivotally
driven to position the container for entry into either a
longitudinally elongated cell or a transversely elongated cell.
Pat. application Ser. No. 643,993 referred to above discloses a
rotatable structure for rotating or positioning containers for any
orientational position on a dock or like flat surface. The present
invention includes a rotatable device that is so sized that it can
enter into cells irrespective of the orientation of the cell. To
permit accomplishment of such mode of operation, the depending
cables must be relatively closely spaced to one another since they
must be no greater than the width, the shortest dimension, of the
cell. Closely spaced cables do not afford optimum stability to
containers, particularly when the containers are eccentrically
loaded. According to the present invention, a counterweight is
provided on the spreader frame that engages the containers, and a
sensing system for sensing the differential tension in the cables
is employed for controllably positioning the counterweight to
compensate for any unbalanced condition in the container. Thus the
relatively close spacing of the cables does not preclude efficient
balanced operation of the apparatus.
The above, as well as other objects, features and advantages of the
present invention will be more apparent after referring to the
following specification and accompanying drawings in which:
FIG. 1 is a partially schematic elevation view showing a
cargo-hoisting apparatus with the cables disposed at a widely
spaced position;
FIG. 2 is a view similar to FIG. 1 with the cables closely spaced
for entry into a transversely extending cell;
FIG. 3 is a plan view taken along line 3-3 and drawn at a somewhat
enlarged scale;
FIG. 4 is a plan view of a rotatable intermediate spreader frame
according to the present invention;
FIG. 5 is a side elevation view of the intermediate frame of FIG.
4;
FIG. 6 is an end elevation view of a frame of FIG. 4;
FIG. 7 is a fragmentary view at enlarged scale of the supporting
structure of FIG. 6;
FIG. 8 is a side view of FIG. 7;
FIG. 9 is a diagrammatic view showing the load imbalance sensors;
and
FIG. 10 is a schematic view of the load imbalance sensors and
counterweight drive mechanism of this invention.
Referring more particularly to the drawings, reference numerals 12
and 14 indicate structural members of a crane boom that is held in
elevated horizontal position by a tower structure, not shown, in a
position overlying a ship or like transport vessel. The crane boom
is typically supported so that it projects out from a wharf
transversely or athwartship of a vessel situated alongside the
wharf. Secured to members 12 and 14 are track rails 16 which are
shown as I-beams in the drawing. Supported on track rails 16 for
rolling movement thereon is a carriage 18 which has wheels 20 that
are adapted to roll along the track rails. Carriage 18 pivotally
supports yokes 22, each of which has paired sheaves 24 which
sheaves guide horizontal cable runs (not shown) into plural
vertically extending runs indicated at 26a, 26b, 26c, 26d, 27a,
27b, 27c, and 27d. The horizontal space between vertical runs 26a
and 26b on the one hand, and 27a and 27b on the other hand, is
governed by the spacing between paired sheaves 28 and paired
sheaves 30. Sheaves 28 are carried on a subcarriage 32 which is
transversely slidable along guide members 34 that are an integral
part of frame 18. A similar undercarriage 36 supports sheaves 30.
Guide members 34 are shown in the drawings as I-beams and
undercarriages 32 and 36 are dimensioned so that they slide between
the upper and lower flanges of the I-beam section. For moving the
undercarriages 32 and 36 between the relatively widely spaced
position shown in FIG. 1 and the relatively closely spaced position
shown in FIG. 2 there is provided a motor 38 coupled to a drive
sheave 40 through a speed-reducing gear 42. See FIG. 3. In
engagement with drive sheave 40 are plural drivebelts 44 that are
trained around double transfer sheaves 46. Idler sheave 48 at the
extremities of carriage 18 support in cooperation with double
transfer sheaves 46 drivebelts 50. One reach of each drive chain 50
is connected to a carriage 32, 36 by means of a connector 52. Thus
it will be seen that energization of motor 38 will effect movement
of undercarriages 32 and 36 toward and away from one another along
guide members 34.
Cable runs 26a, 26b, 26c, 26d, 27a, 27b, 27c, and 27d support at
their lower ends a pair of quick-change headblocks 54 and 56.
Certain details of these blocks are disclosed in U.S. Pat.
application Ser. No. 675,448. Block 56 is typical and includes an
outboard sheave 58 and an inboard sheave 60 (see FIG. 6). The
quick-change headblocks also include locking devices 62 that serve
quickly to lock onto the headblock suitable load-engaging
apparatus, a specific form of which will be described in more
detail hereinafter. To illustrate the versatility of the apparatus
of the present invention, headblocks 54 and 56 are shown in FIG. 1
in engagement with a conventional spreader frame 64 and in FIG. 2
in engagement with an improved rotatable auxiliary frame 66 made in
accordance with the present invention.
Extending between quick-change headblocks 54 and 56 is an
adjustable frame that includes lateral segments 68 adapted to
telescope into a central frame 70. Headblocks 54 and 56 are shown
in FIG. 1 in their extreme extended position and in FIG. 2 in their
extreme retracted position. Carried on central frame 70 is a cable
bucket 71 into which an electrical control cable 72 coils as the
headblocks are raised and from which the electrical control cable
pays out as the headblocks are lowered. Locking pins 73 (see FIG.
5) cooperate with suitably positioned holes in segments 68 and
central frame 70 to lock the segments 68 in the extended position,
the retracted position, or any desired intermediate position.
FIG. 1 shows a container C positioned between a forward cell wall
74f and an aft cell wall 74a. Container C is engaged by a spreader
frame 64 which spreader frame has upstanding connector elements 64c
for engagement by quick-change headblocks 54 and 56. The headblocks
are widely spaced in FIG. 1 because the longest dimension of the
cell, i.e., the distance between walls 74f and 74a, is oriented
longitudinally of the vessel of which the cell is a part. In FIG. 2
a forward cell wall 75f is spaced from an aft cell wall 75a by a
distance equal to the width of container C'. The cell residing
between walls 75f and 75a is oriented with its longest dimension
transversely of the longitudinal dimension of the vessel. Lateral
segments 68 are telescoped into central frame 70 so that headblocks
54 and 56 are sufficiently close to one another to fit between cell
walls 75f and 75a. Because the distance between connecting elements
64c on spreader frame 64 is fixed, an intermediate rotatable
auxiliary frame 66 is provided for placement between headblocks 54
and 56 and spreader frame 64.
Intermediate rotatable auxiliary frame 66, as can be seen in FIG.
5, includes an upper frame element 76, a lower frame element 78,
and a rotary drive apparatus 80 therebetween for joining the upper
and lower elements together and for establishing the relative
rotational position therebetween. Extending upwardly from frame
element 76 are connector elements or plates 82 which are formed for
engagement with quick-change headblocks 54 and 56 in order that the
rotatable auxiliary frame 66 can be quickly removed from the
hoisting apparatus when it is not needed. Depending from lower
frame element 78 are quick-change connector elements 84 which
engage with complementary elements 64c projecting upwardly from a
spreader frame 64'. Spreader frame 64', although of a size
different from spreader frame 64, is otherwise identical in
structure and function. Rotating mechanism 80 is similar to the
structure described in the above-mentioned Pat. application Ser.
No. 643,993. More specifically, rotating mechanism 80 includes a
motor 86 that powers a slewing drive formed by a pinion 88 enmeshed
with a ring gear 90 which is rigid with lower frame element 78.
Ring gear 90 is formed on the interior face of a bearing race 92
which is attached to lower frame element 78 by means of crossbeams
94. A second bearing race 96, which is secured to upper frame
element 76, constrains antifriction balls 97 so that the upper and
lower frame elements can be rotated relative one another. Thus when
motor 86 is energized, lower frame element 78 is rotated with
respect to upper frame element 76 so that a load attached to the
lower frame element is rotated with respect to the hoisting cables,
carriage 18, and rails 16.
Because quick-change headblocks 54 and 56 are spaced relatively
closely when engaged with connector plates 82 of upper frame
element 76, an unbalanced load condition in a container could, if
not compensated for, cause the container to tilt to such a degree
that it would not properly fit between the cell walls. For
compensating for such unbalanced condition, a movable counterweight
98 is employed. The counterweight is disposed between side rails
100 of lower frame 78 and has flanged wheels 102 projecting
laterally therefrom for rolling engagement on the side rails. The
position of counterweight 98 along rails 100 is established by a
motor 104 which drives a pair of cable drums 106 and 108 through a
reducing gear or transmission 110. Cables 112 each have a bight
wrapped around drums 106 and 108 and have their ends attached to
opposite sides of the counterweight as indicated at 114 in FIG. 5.
Each cable 112 is guided around opposed sheaves 116 and 118 so that
as drums 106 and 108 are rotated, counterweight 98 is moved along
side rails 100. An idler sheave 118 is provided for each cable 112
to guide the cable clear of rotary drive mechanism 80.
Motor 104 is actuated to move counterweight 98 only when an
unbalanced load condition exists. For sensing the presence of such
unbalanced condition, the sheaves in headblocks 54 and 56 are
carried by yokes 120 that are mounted in the headblocks for pivotal
movement around a pivot pin 122. Yokes 120 are pivotable about the
axis of pivot pin 122 between an extended position shown in FIG. 6
and a retracted position shown in FIG. 8. Locking pins 124, 126,
and 128 are provided for retaining the yokes in a desired position,
locking pins 124 and 126 being provided for holding the yokes in
the extended position, and locking pin 128 being provided for
retaining the yokes in the retracted position. When the apparatus
is being employed with an ordinary spreader frame, as shown in FIG.
1, unbalanced load conditions do not constitute a problem, and
yokes 120 are moved to the retracted position shown in FIG. 8 in
order to maximize the angle of convergence of the cables 26 and 27,
thereby to maximize the degree of damping of swaying motion. When,
however, the apparatus is being used for spreader frames and
containers that can be rotated to the position shown in FIG. 2,
yokes 120 are moved to the extended position shown in FIG. 6,
thereby to maximize stability against the effects of an unbalanced
load.
When undercarriages 32 and 36 are in the widely spaced position
shown in FIG. 1, container C is reasonably stable because of the
wide spacing of the cables in a direction longitudinally of the
container. In such condition it is desirable to have the angle
between cable runs 27a and 27b and cable runs 27c and 27d at a
substantial magnitude as shown in FIG. 8. Such position is
established by swinging the yokes 120 inwardly and locking them in
such position by means of locking pins 128. A substantial angle
between the cable runs is desirable in order to minimize swaying or
oscillation of the container in a direction in and out of the paper
as viewed in FIG. 1. When, however, the undercarriages 32 and 36
are moved to the relatively closely spaced position, as shown in
FIG. 2, to adapt the system to handle containers at a 90.degree.
position from that shown in FIG. 1, the maximum spacing between
cable runs 27a and 27b and cable runs 27c and 27d that can be
obtained is desirable to compensate as much as possible for load
imbalance. To achieve such condition, yokes 120 are moved to the
outer position of FIG. 6 and there retained by engagement of
locking pins 124 and 126. At such position an abutment 120a of yoke
120 moves into operative connection with load cells 130 and 132.
See FIG. 8. Thus the system for sensing container imbalance is made
active.
The system for positioning counterweight 98 is activated by
providing hydraulic load cells 130 and 132 at diagonally opposite
yokes 120. Hydraulic load cells suitable for this purpose are
available from the Martin Decker Company. The output of each load
cell, a hydraulic fluid pressure, is transmitted through flexible
hoses 134 and 136, respectively, to an electrohydraulic control
circuit 138 for actuating motor 104. Thus the pressure existing in
hydraulic line 134 is proportional to the load on cable runs 26a
and 26b, and the pressure in line 136 is proportional to the load
on cable runs 27c and 27d. The differential between the pressures
in lines 134 and 136 is proportional to the degree of imbalance of
the combined weight of the load, the apparatus for engaging the
load, and the counterweight 98.
Differential pressure switches 140, 142, 144 and 146 respond in
accordance with the magnitude and direction of differential
pressures between lines 134 and 136. The differential pressure
switches in one system designed according to the present invention
are known by the trade name Melatron switches. Pressure switch 140
includes a hydraulic element 140h, which includes an electrical
armature 140a movable between a normally closed fixed contact 140c,
and a normally open fixed contact 140b. Pressure switch 140 is
arranged so that when the pressure in hydraulic line 134 exceeds
that in hydraulic line 136 by a preselected increment, armature
140a is moved out of contact with fixed contact 140c and into
contact with fixed contact 140b. When the pressure in hydraulic
line 136 exceeds the pressure in hydraulic line 134, however, the
normally closed relationship between armature 140a and fixed
contact 140c is not affected.
Differential pressure switch 142 includes a hydraulic element 142h
to which is operatively connected an electrical armature 142a that
is movable between a fixed normally closed contact 142c and a fixed
normally open contact 142b. Differential pressure switch 142 is so
arranged that when the pressure on hydraulic line 136 exceeds the
pressure on hydraulic line 134, armature 142a is moved away from
fixed contact 142c toward fixed contact 142b.
Conductors 148 and 150 are series connected through armature 140a,
fixed contact 140c, armature 142a, and fixed contact 142c. It will
be appreciated that the existence of a pressure differential
between hydraulic lines 134 and 136 will open the series circuit
between conductors 148 and 150. Such conductors form an interlock
in association with the hoisting control apparatus (not shown) that
raises and lowers cables 26 and 27. Consequently, the raising of
cables 26 and 27 will be arrested when a severely unbalanced load
condition is sensed, and raising will be resumed only after the
unbalance is corrected by appropriate positioning of counterweight
98.
Differential pressure switches 144 and 146 are provided for
effecting proper positioning of the counterweight. Differential
pressure switch 144 includes a hydraulic element 144h that is
connected to hydraulic lines 134 and 136 and that is adapted to
operate an armature 144a when the pressure in hydraulic line 134
exceeds the pressure in hydraulic line 136. The armature is
normally connected to a fixed contact 144c, but when such
differential pressure is sensed the armature moves into connection
with a fixed contact 144b. Differential pressure switch 146
includes a hydraulic element 146h that is connected to hydraulic
lines 134 and 136 and which is adapted to operate an armature 146a
from a normally closed contact 146c to a normally open contact 146b
only when the pressure in hydraulic line 136 exceeds the pressure
in hydraulic line 134. Thus, when the pressure in hydraulic line
134 exceeds the pressure in hydraulic line 136, a circuit is
established by pressure switch 144 through armature 144a and fixed
contact 144b; when pressure in hydraulic line 136 exceeds the
pressure in hydraulic line 134, a circuit is established by
pressure switch 146 through armature 146a and fixed contact 146b. A
power source exemplified schematically in FIG. 10 at 152 is
provided for connection through one or the other of such circuits.
The circuit including armature 144a and fixed contact 144b is
connected to a forward motor drive relay coil 154, and the circuit
including armature 146a and fixed contact 146b is connected to a
reverse motor drive relay coil 156. Operatively associated with
forward motor drive relay coil 154 are normally closed contacts
154a and 154b, and normally open contact 154c and 154d. Operatively
associated with reverse motor drive relay coil 156 are normally
closed contacts 156a and 156b, and normally open contacts 156c and
156d. A power source 158 has a positive terminal connected to one
side of contacts 154b and 154d, and a negative terminal connected
to one side of contacts 154a and 154c. Counterweight drive motor
104 has one of its armature terminals connected to one side of
contacts 156b and 156d, and the other of its armature terminals to
one side of contacts 156a and 156c.
As will be appreciated from FIG. 10, when both relay coils 154 and
156 are in a deenergized or quiescent state, the circuit between
power source 158 and counterweight drive motor 104 is open. When,
however, either of the relays is energized in response to the
presence of an unbalanced load condition, power source 158 is
connected to counterweight 104. When relay 154 is activated in
response to actuation of differential pressure switch 144 by an
increase of hydraulic pressure in line 134 over that in line 136, a
circuit from the positive terminal of power source 158 to the motor
is established through contact 154d and contact 156b, and a circuit
from the negative terminal of the power source to the motor is
established through contacts 154c and 156a. This circuit condition
causes counterweight 98 to be moved toward the right as viewed in
FIG. 5. Contrariwise, when coil 156 is energized, a circuit from
the positive terminal of power source 158 to the motor is
established through contacts 154b and 156c, and from the negative
terminal of the power source to the motor through contacts 154a and
156d. Such circuit condition causes the counterweight to be driven
leftwardly as viewed in FIG. 5. Simultaneous actuation of relays
154 and 156, a condition that might arise through some instability
in the hydraulic portions of the system, has no effect on the
position of counterweight 98 because no circuit is established
between power source 158 and motor 104 when both relays are
energized.
Actuation of motor 104 as described above continues until the
counterweight is positioned to compensate for the load unbalance
and restore equal pressure in hydraulic lines 134 and 136. When
equal pressure is restored, differential pressure switches 140,
142, 144, and 146 release with two consequences: counterweight
drive motor 104 ceases operation and the interlock constituted by
conductors 148 and 150 is reestablished to permit hoisting of the
load.
In operation with a container vessel in which all container cells
are elongate in a direction longitudinally of the vessel
(transversely of structural members 12 and 14 and track rails 16),
a conventional spreader frame 64 is attached directly to
quick-change headblocks 54 and 56 as shown in FIG. 1.
Undercarriages 32 and 36 are positioned at their outer or most
widely spaced position, at which the space between cables 26 and 27
is sufficiently large to lift a container C in straight orientation
even though the load in the container is unbalanced. This mode of
operation of the apparatus of this invention demonstrates that the
system is versatile.
In loading and unloading a vessel having transversely elongate
container cells, it is necessary to bring cables 26 and 27 toward
one another to clear cell walls 75f and 75a as seen in FIG. 2. For
establishing such relatively close spacing between the cables,
motor 38 is energized to bring undercarriages 32 and 36 to a
position such that sheaves 28 and 30 will guide cables 26 and 27
along vertical paths that are spaced from one another by a distance
less than the smaller dimension of the container cell.
Additionally, the space between quick-change headblocks 54 and 56
is reduced by removing pins 73 and telescoping segments 68 into
central frame 70. In the retracted position as can be seen in FIG.
2, the quick-change headblocks clear cell walls 75f and 75a.
Because the connector elements on spreader frame 64 are fixed,
quick-change blocks 54 and 56 are disengaged from such connector
elements for permitting the inward movement of the headblocks. The
connector elements on rotatable auxiliary frame 66 are spaced to
engage headblocks 54 and 56 in their relatively closely spaced
position and the auxiliary frame is attached to the headblocks when
the headblocks are moved to the closely spaced position.
Quick-change connector elements 84 on the lower element 78 of
auxiliary frame 66 are joined to the connector elements 64c on
spreader frame 64. By energization of motor 86, spreader frame 64
and a container C' engaged thereby can be positioned for handling
containers in either longitudinally elongate cells or transversely
elongate cells.
In lifting container C' in FIG. 2 into and out of a transversely
elongate cell, the apparatus is sensitive to unbalanced loads
within container C' because of the relatively close spacing between
the vertical cable runs. If the load in the container is
unbalanced, the tension in cable runs 26a and 26b is different from
the tension in cable runs 27c and 27d. See FIG. 9. Such difference
will be manifested at the outputs of hydraulic load cells 130 and
132. The difference in pressure arising from an unbalanced load is
manifested while slack in the cables is being taken up and before
the container actually moves. If it be assumed that the heaviest
portion of the load in container C' is adjacent to load cell 130,
the pressure in hydraulic fluid line 134 will exceed the pressure
in hydraulic line 136 and differential pressure switches 140 and
144 will be actuated. Activation of differential pressure switch
140 interrupts the interlock circuits through conductors 148 and
150 which in turn interrupts power to the hoisting motors through
conventional electrical circuitry, not shown. This system function
is desirable to prevent abrasion between the container and the
walls of a canted container cell, or to prevent, in extreme cases,
binding or jamming of the container in the cell.
Actuation of pressure switch 144 moves armature 144a to fixed
contact 144b so as to connect power source 152 to motor drive relay
coil 154. Energization of coil 154 establishes a connection between
power source 158 and counterweight drive motor 104, thereby driving
the counterweight away from the relatively heavy side of the
container and toward the relatively light side of the container.
When the counterweight has moved to a position at which the load
imbalance is compensated for, the tension in cables 26a, 26b, 27c,
and 27d equalizes, and the fluid pressure in hydraulic lines 134
and 136 correspondingly equalizes. Pressure switches 140 and 144
consequently deactivate so that movement of counterweight 98 is
terminated and the interlock circuit formed by conductors 148 and
150 is reestablished. Thus the container movement within the
container cell can proceed.
It will be noted that the lower frame element 78, along which
counterweight 98 is moved, rotates in unison with spreader frame 64
and any container engaged thereby. Consequently, balance, when once
established for a given container, will not be upset by rotative
movement of rotating mechanism 80.
Container C' can be deposited onto a pier surface or waiting
railroad car or the like in any desired orientation. When the
container is disengaged from spreader 64 the empty spreader will
not be raised unless and until counterweight 98 is moved to the
center of lower frame 78, because location of the counterweight 98
at an offcenter position will cause a pressure differential between
lines 134 and 136 opposite from that assumed above.
One system designed according to the present invention employs a
counterweight 98 weighing 41/2 tons; the length of side rails 100
available for supporting flanged wheels 102 is approximately 14
feet. Such system is satisfactory for handling containers having a
length of 20 or more feet and for compensating for unbalanced load
conditions in such containers.
Thus it will be seen that the present invention provides a system
for loading and unloading containers from ships or like vessels
that have longitudinally elongate cells, or transversely elongate
cells, or a combination of both. Not only is the apparatus of the
invention useful in newly constructed hoisting systems, but
existing systems can be adapted to employ the novel apparatus
without extensive modification.
Although one embodiment of the present invention has been shown and
described, it will be obvious that other adaptations and
modifications can be made without departing from the true spirit
and scope of the invention.
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