U.S. patent number 3,680,840 [Application Number 04/889,188] was granted by the patent office on 1972-08-01 for boom sheave assembly.
This patent grant is currently assigned to Manitowoc Engineering Company. Invention is credited to David J. Pech.
United States Patent |
3,680,840 |
Pech |
August 1, 1972 |
BOOM SHEAVE ASSEMBLY
Abstract
A boom sheave assembly is provided wherein a sheave shaft is
supported by a plurality of struts which are loaded substantially
only in tension. The boom sheave assembly is pivotally mounted to
position a beam, strong in bending, in alignment with the direction
of the forces applied to a load implement.
Inventors: |
Pech; David J. (Manitowoc,
WI) |
Assignee: |
Manitowoc Engineering Company
(Manitowoc, WI)
|
Family
ID: |
25394656 |
Appl.
No.: |
04/889,188 |
Filed: |
December 30, 1969 |
Current U.S.
Class: |
212/232;
212/347 |
Current CPC
Class: |
B66D
3/06 (20130101); B66D 2700/028 (20130101) |
Current International
Class: |
B66D
3/00 (20060101); B66D 3/06 (20060101); B66d
001/36 () |
Field of
Search: |
;254/192,194,195
;212/3,58,59,48,39 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
Primary Examiner: Aegerter; Richard E.
Claims
I claim:
1. A crane comprising
a boom;
means for elevating the boom with respect to an underlying surface
including means for preventing elevation of the boom beyond a
predetermined angle with respect to the underlying surface;
a boom sheave assembly comprising a shaft having an axis; a
plurality of sheaves thereon; a beam above the shaft; a plurality
of depending struts, connecting the beam and the shaft,
substantially wholly supporting the shaft and stressed
substantially only in tension in response to a load applied to the
shaft; and means connecting the beam and the boom for pivotally
mounting the sheave assembly on the boom; the pivotal mounting
means including arms extending from the beam and cooperative
pivotal connections, between the arms and the boom, defining a
pivot axis positioned between the beam and the shaft axis;
a load line reeved over the sheaves; and
an implement operatively connected to the load line and movable
with respect to the sheave assembly for handling a load.
2. The crane of claim 1 wherein the arms and the struts reside on a
common radius relative to the shaft.
3. The crane of claim 2 wherein the beam, shaft and pivotal
connections reside substantially in a common plane.
4. The crane of claim 1 wherein the plurality of struts includes
struts at opposite end portions of the shaft and at least one
intermediate strut connected to the shaft between two of the
sheaves.
Description
With the advent of cranes capable of lifting substantial loads, it
is necessary to increase the load handling capacity of the boom
sheave assembly. Typical boom sheave assemblies for less heavily
loaded booms comprise a plurality of sheaves mounted on a sheave
shaft with the opposite ends of the sheave shaft mounted on the
boom. The most elementary approach taken by the prior art to
increase the load bearing capacity of a boom sheave assembly has
been to increase the size of the sheave shaft to handle the larger
loads.
Along with the trend to greater crane capacities, it has been the
practice to increase the number of lines between the boom sheave
assembly and a traveling block. There have consequently been more
sheaves mounted on the sheave shaft thereby necessitating a longer
shaft to accommodate the additional sheaves. Longer sheave shafts
have aggravated the bending of the shaft. It will be apparent that
increasing the diameter of the sheave shaft to accommodate greater
loads and particularly to accommodate greater bending loads, has
obvious practical limits.
One approach of the prior art to minimize bending of the sheave
shaft is to support the sheave shaft intermediate the ends thereof
by one or more cantilevered struts. Since these struts of the prior
art extend between the sheaves, the struts must be relatively
narrow and consequently cannot have a substantial flange thereon
imparting substantial resistance to bending. Since a cantilevered
mounting is a relatively weak securement for a strut of this
nature, this approach of the prior art has not been altogether
satisfactory.
This invention comprises a boom sheave assembly having a beam
parallel to the sheave shaft, which is strong in bending, with the
sheave shaft being secured thereto by a plurality of depending
struts which are loaded substantially only in tension. The beam is
pivotally mounted on the crane boom so that load forces applied to
the sheaves pivot the beam to position the same coplanar with the
direction of the applied loads.
It is an object of this invention to provide a boom sheave assembly
of maximum strength consistent with low weight.
Another object of the invention is to provide a boom sheave
assembly wherein a sheave shaft is supported intermediate the ends
thereof by a plurality of struts stressed substantially only in
tension.
A further object of the invention is to provide a boom sheave
assembly comprised of a beam to position the same in alignment with
forces applied to the sheaves.
Still another object of the invention is to provide a crane having
a boom thereon equipped with a sheave assembly of the
aforementioned type.
IN THE DRAWINGS:
FIG. 1 is a side elevational view of a high capacity crane equipped
with a boom sheave assembly of the invention;
FIG. 2 is an enlarged side elevational view of the boom sheave
assembly of FIG. 1;
FIG. 3 is a front view of the boom sheave assembly of FIG. 2,
certain parts being broken away for clarity of illustration;
and
FIG. 4 is a cross-sectional view of the boom sheave assembly of
FIGS. 2 and 3 taken substantially along line 4--4 of FIG. 3 as
viewed in the direction indicated by the arrows.
Attention is directed to FIG. 1 wherein there is illustrated a
crane 10 having a boom 12 pivotally mounted to a carrier 14. The
carrier 14 is supported by an underlying ring 16 and is secured to
an upper works 18 for rotation therewith. Interconnecting the boom
12 and the carrier 14 are suitable boom stops 15 which act to
prevent elevation of the boom 12 beyond a predetermined angle with
respect to the underlying ground surface. This type of crane is
described in more detail in the application of Daniel E. Beduhn,
Ser. No. 704,488, filed Feb. 9, 1968, now U.S. Pat. No. 3,485,383
and assigned to the assignee of this application.
Secured to the free end of the boom 12 is a boom sheave assembly 20
made in accordance with this invention. A load line 22 is
operatively connected to a drum 24 on the upper works 18 and is
reeved through the sheave assembly 20 to an implement 26
illustrated as a traveling block. The path of the load line 22 is
defined by a plurality of guide sheaves 28 as is customary.
Referring to FIGS. 2-4, the boom sheave assembly 20 comprises as
major components a load supporting beam 30, mounting means 32 for
securing the assembly 20 to the boom 12, a sheave shaft 34, a
plurality of sheaves 36 and a plurality of struts 38 securing the
shaft 34 to the beam 30.
The beam 30 is illustrated as a deep rectangular box having walls
40, 42, 44, 46 secured together by suitable weldments 48. The ends
of the box beam 30 are closed by end caps 50, 52 secured by
weldments 54. The beam 30 consequently has a major axis of bending
strength 56 disposed on a radius of the sheave shaft 34 and a minor
axis of bending strength 58 perpendicular to the major axis 56.
Although a rectangular box beam is illustrated, it will be apparent
that a square box beam, an I-beam, a T-beam, a tube or any other
structural member strong in bending may be used.
Referring to FIGS. 2 and 3, the mounting means 32 is illustrated as
comprising a pair of arms 60, 62 secured adjacent opposite ends of
the beam 30 and providing a pair of socket forming members 64, 66.
The members 64, 66 are aligned with a pair of complementary socket
forming members 68, 70 provided at the top of the boom 12 with a
pair of pins 72, 74 securing the socket forming members 64, 66, 68,
70 together. Suitable means, such as cotter keys or the like, may
be provided to retain the pins 72, 74 in position. The members 64,
66 define a pivot axis spaced from the shaft 34, the importance of
which will be explained hereinafter. It will be seen that the
mounting means 32 not only constitutes means for mounting the beam
30 and the assembly 20 on the boom 12, but also constitutes means
for pivotally mounting the beam 30 and the struts 38 in a manner
more fully described hereinafter.
Each of the sheaves 36 comprises a suitable bearing 76 rotatably
mounting the sheave 36 on the shaft 34. Suitable lubrication
connections 78 may be provided for the bearings 76. Annular sealing
plates 80 are secured to the hub of the sheave 36 and operate to
retain lubricant in the bearing 76. The plates 80 also act as
bearings to accommodate any relative rotation between adjacent
abutting sheaves 36. As will be apparent from the insuing
description, the plates 80 also act as a bearing between the struts
38 and the sheaves 36 adjacent thereto.
As shown best in FIGS. 3 and 4, the struts 38 are secured at the
upper end thereof to the beam 30. The lower end of each strut 38
provides an aperture 82 closely receiving the sheave shaft 34. A
pair of end fittings 84, 86 captivate the shaft 34 in the apertures
82 of the struts 38. Suitable connections 88 affix the end fittings
84, 86 to the ends of the shaft 34. The generally circular end
fittings 84, 86 are provided with a straight segment 90, 92 which
cooperate with an abutment 94, 96 affixed to the outer struts 38.
It will be apparent that the segments 90, 92 and the abutments 94,
96 prevent rotation of the shaft 34.
Since the sheave shaft 34 is supported at a number of spaced
locations along the length thereof, the deflection of the shaft 34
in bending is substantially reduced. It will be noted that the
struts 38 depend from the beam 30 and are free from features which
would induce substantial bending forces therein.
When the crane 10 is hoisting a load in a purely vertical
direction, the forces applied to the shaft 34 resolve into a
vertical force vector 98 shown in FIG. 2. It will be apparent that
the stresses resulting in the struts 38 are substantially only
tensile in nature. It will also be apparent that the loads applied
to the beam 30 are in alignment with the major axis of bending
strength 56. It will be further apparent that when the angle of the
boom is changed, as is common in crane operation, the boom sheave
assembly 20 will remain vertical with the load in line with the
major axis of the beam 30.
It will be apparent that the crane 10 is called upon to handle
other than purely vertical loads, for example when a load is
rotated about the axis of the upper works 18 or when a load is
lifted from a location other than immediately below the boom top.
The forces applied to the shaft 34 resolve into a non-vertical
force vector 100 which radially extends from the shaft 34. Since
the pivot axis defined by the members 64, 66 is spaced from the
shaft 34, a counter clockwise moment is induced in the boom sheave
assembly 20 to rotate the beam 30, the struts 38 and the shaft 34
to align the force vector 100 with the beam 30, the struts 38 and
the shaft 34. Without the movable connection provided by the
mounting means 34, it will be apparent that the force transmitted
to the struts 38 would not be substantially only in tension but
instead would include a substantial bending force thereby
converting the struts 38 into cantilevered beams. Since the struts
38 are substantially weaker when mounted as a cantilevered beam
rather than as a pendant support, it will be seen that the capacity
of the boom sheave assembly 20 would be substantially reduced. In a
similar fashion, the forces applied to the beam 30 would no longer
be in alignment with the major axis of bending strength 56 thereby
decreasing the load bearing capacity of the beam 30 and
consequently detracting from the capacity of the boom sheave
assembly 20. It will accordingly be apparent that the movable
connection provided by the mounting means 32 is of significant
utility.
* * * * *