U.S. patent number 3,708,937 [Application Number 05/075,886] was granted by the patent office on 1973-01-09 for trapezoidal telescoping crane boom.
This patent grant is currently assigned to Walter Kidde & Company, Inc.. Invention is credited to Russell L. Sterner.
United States Patent |
3,708,937 |
Sterner |
January 9, 1973 |
TRAPEZOIDAL TELESCOPING CRANE BOOM
Abstract
A crane boom comprises plural extensible and retractable
telescoping sections each of which is trapezoidal in cross section.
The trapezoidal cross sectional shape imparts to a boom of given
weight greater lifting capacity or longitudinal rigidity and
greater lateral stability than any other cross sectional shape. The
trapezoidal cross section allows for a much more efficient
placement of wear pads between boom sections and web stiffeners on
the sides and bottoms of the sections. Adequate internal space is
provided for boom extending and retracting means whether hydraulic
or mechanical.
Inventors: |
Sterner; Russell L.
(Greencastle, PA) |
Assignee: |
Walter Kidde & Company,
Inc. (Clifton, NJ)
|
Family
ID: |
22128568 |
Appl.
No.: |
05/075,886 |
Filed: |
September 28, 1970 |
Current U.S.
Class: |
52/118; 52/848;
52/115; 212/350 |
Current CPC
Class: |
B66C
23/705 (20130101) |
Current International
Class: |
B66C
23/70 (20060101); B66C 23/00 (20060101); B66t
011/00 (); E04h 012/34 () |
Field of
Search: |
;52/111,114,115,116,117,118,121,632 ;212/55 ;182/2 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
|
|
|
|
|
|
|
1,171,016 |
|
Jan 1958 |
|
FR |
|
644,753 |
|
Jul 1962 |
|
CA |
|
1,492,931 |
|
Jul 1967 |
|
FR |
|
1,009,373 |
|
Nov 1959 |
|
DT |
|
Primary Examiner: Abbott; Frank L.
Assistant Examiner: Braun; Leslie A.
Claims
I claim:
1. A telescoping crane boom comprising a base section for the boom
having means to pivot it about one end thereof, at least one
additional extensible and retractable boom section telescopically
engaged within the base section with means connected thereto
adapted to load only the outer free end of the crane boom, power
means to extend and retract the telescoping boom, all sections of
the telescoping boom being trapezoidal in transverse cross section
and including upwardly converging side webs, a relatively narrow
top plate secured to the side webs and a relatively wide bottom
plate unit secured to the side webs, a reinforcement for the top
plate of at least the base section of the boom adjacent the forward
end of the base section to resist stresses produced thereon by
extension and loading of the next forwardmost boom section having
upper wear pads bearing against the top plate of the base section,
and said reinforcement comprising an overlayplate mounted on said
top plate, and a pair of side reinforcing bars adjacent the overlay
plate and near the tops of the side webs and secured thereto and to
said top plate.
2. The structure of claim 1, and plural longitudinally spaced web
stiffeners secured to said side webs of at least said base section
of the boom.
3. The structure of claim 2, and additional transverse
longitudinally spaced web stiffeners for said bottom plate unit
secured thereto.
4. The structure of claim 3, and a pair of longitudinal side
reinforcing bars extending along the lower corners of at least said
base section of the boom and secured to said side and bottom web
stiffeners, said side webs and bottom plate unit formed of
relatively thin gage material for lightness.
5. The structure of claim 4, and all of said web stiffeners
comprising channel bars having their open sides facing and abutting
the webs to which they are welded.
6. A telescoping crane boom comprising a base section for the boom
having means to pivot it about one end thereof, at least one
additional extensible and retractable boom section telescopically
engaged within the base section with means connected thereto
adapted to load only the outer free end of the crane boom, power
means to extend and retract the telescoping boom, all sections of
the telescoping boom being trapezoidal in transverse cross section
and including upwardly converging side webs, a relatively narrow
top plate secured to the side webs and a relatively wide bottom
plate unit secured to the side webs, a pair of laterally spaced
wear elements on the bottom plate unit of at least said base
section near the forward end thereof to receive directly the bottom
plate unit of the next forwardmost additional boom section, and
said wear elements disposed directly under the side webs of said
next forwardmost additional boom section for transmitting forces
directly thereto.
7. The structure of claim 6 in which the cross sectional height of
any boom section is unity and the width of said top plate is from
0.35 to 0.6 of unity and the width of said bottom plate unit is
from 0.8 to 1.1 of unity.
8. The structure of claim 6, and a pair of upper wear elements
interposed between the top plates of the two boom sections and
being located substantially directly above side side webs of the
next forwardmost additional boom section for transmitting forces
directly thereto whereby the side webs function substantially as
columns to absorb said forces, and means to retain the upper wear
elements on the next additional forwardmost boom section.
9. A telescopic crane boom as set forth in claim 6 in which said
bottom plate unit of at least one of said boom sections includes a
pair of longitudinal reinforcing bars extending along the lower
corners of the boom section connected beneath the side webs
thereof, and a bottom web of relatively thin gage material
connected between said pair of longitudinal reinforing bars.
Description
BACKGROUND OF THE INVENTION
Heretofore in the art, the booms and boom sections of telescoping
crane booms, such as the type used on mobile carriers and
constructed to be extended and retracted by hydraulic rams or
cables in conjunction with hydraulic rams, or the like, have been
generally rectangular in cross-section. Two or more box-shaped boom
sections are correspondingly proportioned so that they
telescopically slide in each other to provide a boom of appropriate
length. Generally, booms are constructed of between two to five
telescopic boom sections.
As rectangular cross-section booms have been designed to lift loads
of greater weight the vertical walls of the boom sections have been
made higher, increasing the rectangular cross-section and putting
more material in the vertical walls to increase the rigidity of the
boom in the longitudinal direction and thus increase the strength
of the boom. It has been found, however, that the height to which
the rectangular cross-section can be increased is limited by the
width of the rectangular cross-section. When a rectangular boom
carrying a load is extended, and particularly when the boom is
rotated on its carrier in the extended position, the nose of the
boom has a tendency to twist about the longitudinal axis of the
boom and lay over on its side. To combat this, the rectangular
cross-section of the boom is made wider and in some cases the
cross-section is square in shape. However, it has been found that
while this provides greater lateral rigidity to the boom, it adds
excessive weight to the boom itself, such that rectangular
cross-section booms cannot be made wide enough to give proper
lateral rigidity without adding a disproportionate amount of
excessive weight to the boom.
A rectangular cross-sectioned boom also has other design
limitations. A crane boom is primarily a cantilevered beam, a
moment carrying member, and in a telescopic boom the telescoping
sections must fit closely inside each other with as little side,
top and bottom play as possible. The width is therefore limited to
such an extent that there is not sufficient room to properly
stiffen the vertical web members of the rectangular cross-section,
so that all stiffening is obtained in the thickness of the metal
used. Massive shear forces are therefore present at the points of
concentrated loads when the boom is in extended position, that is,
within the socket area or overlap area of adjacent extended
telescopic sections.
Additionally, excessive transverse stresses are developed on the
top and bottom members of the rectangular cross-sectioned boom
sections. Adjacent telescopic sections are guided and supported
within each other normally by means of rollers or wear pads on the
inner end of one section bearing on the inside of the top member of
the section into which it slides, and on the outer end of each
section bearing on the outside of the bottom member of the adjacent
section housed therein. Because of the configuration of one
rectangular member nested within another rectangular member the
wear pads or rollers, which are points of concentrated loads
between sections, are located a substantial distance inwardly from
the side walls of the rectangular sections and with such a
configuration it is impossible to locate the wear pads beneath the
vertical web members of the succeeding boom section. For this
reason, in rectangular cross-section booms, the wear pads between
adjacent sections cause excessive transverse bending stresses to be
developed in the top and bottom members of a rectangular
cross-sectioned boom.
The boom art therefore requires a break-through in the design of
telescopic booms which will enable the strength and rigidity to
weight ratio in both longitudinal and lateral directions to be
substantially increased, thus enabling a boom of a given weight to
be capable of lifting considerably heavier loads than a prior art
boom of the same weight. Triangular cross-sectioned telescopic
booms have been used in machinery where the majority of the load is
along the longitudinal axis of the boom, but such an arrangement,
while it approaches a solution to the design problem of lateral
rigidity, since the base of the cross-section is much wider than
the apex of the triangular cross-section, it is not suitable for
use in a cantilevered crane boom which functions as a load carrying
beam. A boom having a cross-section of an equilateral triangle with
longitudinally extending chord members of equal cross-sectional
area in each corner of the triangular configuration provides a good
column design which efficiently functions as a compression member
but it will not efficiently function as a cantilevered load lifting
beam. The main reason is that the chord at the apex of the
triangular cross-section cannot provide sufficient track or bearing
area for the wear pads of the adjacent inner section and tremendous
concentrated forces would, therefore, be present at the apex of the
triangular section. Additionally, a triangular cross-section
restricts the inner area available in a boom for the positioning of
the operating hydraulic cylinders to such a great extent that this
restriction alone makes a triangular cross-sectional boom
impracticable.
Therefore, up until the present time, the art is without a solution
to the problem of a more efficient design for a telescopic boom
which will enable the art to move on and produce telescopic booms
capable of lifting greater loads than is presently possible with
known designs.
SUMMARY OF THE INVENTION
In accordance with the present invention, a telescoping preferably
hydraulically operated crane boom of the type commonly used on
mobile carriers is provided. The boom is characterized by the fact
that the several boom sections are trapezoidal in cross section and
preferably the wider base of the trapezoid is lowermost and its
sides, which are of equal length, converge upwardly. The trapezoid
is symmetrical and has its major axis disposed in a vertical plane.
This construction greatly increases the lifting efficiency of the
crane boom and its economy in terms of lifting capacity to weight
ratio. In comparison to other cross sectional forms, the total boom
and its sections are more rigid in the longitudinal direction or in
the plane in which the lifted load is suspended. The boom is also
more stable laterally and more resistant to lateral deformation and
twisting. When a heavy load is suddenly released, as when dumping a
bucket of concrete, vertical whipping or springing upwardly of the
boom is greatly lessened due to the greater rigidity inherent in
the trapezoidal shape. In comparison to other specific cross
sectional shapes commonly employed, as much as 50 per cent more
lifting capacity can be obtained or three times as much rigidity in
the vertical plane and up to seven times more rigidity
laterally.
The trapezoidal configuration possesses other marked advantages
over rectangular and other shapes. Additional room is provided for
side and bottom web stiffeners and for front and rear lateral
guides without increasing the space between telescoping sections
which must be maintained to a minimum. Additionally, the wear pads
or bearings between adjacent sections of the boom may be located
substantially in direct alignment with the reinforced side webs and
this important feature has not been possible with other cross
sectional shapes, including rectangular. The trapezoidal shape also
provides adequate internal chamber space for hydraulic rams and
associated components.
BRIEF DESCRIPTION OF DRAWING FIGURES
FIG. 1 is a front perspective view of a retracted trapezoidal
telescoping crane boom embodying the invention;
FIG. 2 is a side elevation of the boom facing in the opposite
direction to that depicted in FIG. 1;
FIG. 3 is a plan view of the retracted boom;
FIG. 4 is a bottom plan view thereof;
FIG. 5 is an enlarged front end elevational view of the boom;
FIG. 6 is a similar rear end elevational view;
FIG. 7 is an enlarged fragmentary cross section taken on line 7--7
of FIG. 3;
FIG. 8 is a similar section taken on line 8--8 of FIG. 4;
FIG. 9 is a side elevational view of the boom extended, on a
considerably reduced scale;
FIG. 10 is an enlarged side elevational view of the portion A in
FIG. 9;
FIG. 11 is a similar view of the portion B in FIG. 9;
FIG. 12 is a similar view of the portion C in FIG. 9;
FIG. 13 is a similar view of the portion D in FIG. 9; and
FIG. 14 is an enlarged transverse vertical section taken on line
14--14 of FIG. 10.
DETAILED DESCRIPTION
Referring to the drawings in detail, wherein like numerals
designate like parts throughout, the numerals 20, 21, 22 and 23
designate, respectively, the base section, inner mid section, outer
mid section, and the fly section of the telescoping boom assembly.
As shown particularly in FIGS. 1, 5 and 6, each of the individual
boom sections is trapezoidal in cross section and in each case the
wide base of the trapezoidal boom section is lowermost and the
upwardly converging sides are of equal length so that the trapezoid
is symmetrical about its neutral axis. The trapezoid, forming the
basis of the cross sectional shape of each of the boom sections, is
elongated in the vertical plane, FIG. 5, that is to say, the depth
of the trapezoid in the vertical plane through its center is
greater than its maximum width at the base.
As best shown in FIG. 9 where the boom assembly is fully extended,
the sections 20, 21 and 22 possess a number of common structural
features, to be described in detail, whereas the fly section 23,
while possessing the characteristic trapezoidal shape, differs in
its details from the other boom sections.
The base section 20, which is the outermost of the boom sections
and therefore has the largest trapezoidal cross section, embodies a
top plate 24 extending for its entire length and relatively thin
side walls or webs 25 which diverge downwardly from the
longitudinal edge portions of the top plate in a symmetrical manner
with respect to a theoretical central vertical plane through the
boom. The base section 20 further comprises a relatively thin
bottom web 26 bounded along its longitudinal edges by continuous
bars or rails 27 of increased thickness and rigidity. The elements
26 and 27 make up the lower base of the trapezoidal base section
20. The elements 24 through 27 are all integrally joined in a very
secure manner by welding.
At spaced intervals along the length of the base section 20, side
web stiffeners 28 are provided on the outer faces of the side webs
25 and welded thereto with their upper and lower ends welded to the
top plate 24 and bars 27, respectively. As clearly shown in FIG.
14, the web stiffeners 28 lie within the longitudinal edges of the
elements 24 and 27. As shown in FIG. 7, each web stiffener 28 is a
channel member having its open side facing the adjacent side web
25. In a similar manner, bottom web stiffeners 29 are provided at
spaced intervals along the bottom web 26 to reinforce the same
against buckling and, as shown at FIGS. 3 and 4, the stiffeners 28
and 29 may be disposed at similar locations along the boom section
20. While the spacing of the web stiffeners is not extremely
critical, they are preferably spaced apart by distances which
approximate the depth of the trapezoidal boom section to which they
are applied. FIG. 8 illustrates the channel construction of the
bottom web stiffeners 29 whose open sides face the web 26.
The base section 20 is equipped at its rear end with a suitably
reinforced main pivot unit 30 for the entire boom which is
attachable in a conventional manner to the mobile carrier. Near its
mid point and on its bottom, the boom base section is also equipped
with a reinforced connector 31 for the boom lifting cylinder
indicated in phantom lines at 32 in FIG. 2. At its forward end, the
base section 20 carries an underslung transverse box member 33
which receives the lower forward wear plates or pads 34 and their
conventional holders.
At the forward end region of the base section 20 where this section
receives the extended inner mid section 21 in socketed
relationship, and is therefore subjected to great stresses, the top
plate 24 is reinforced by an overlay plate 35. Additionally, in
this region, side longitudinal reinforcing bars 36 are employed
preferably between the forward four web stiffeners 28 and directly
under the top plate 24 to greatly reinforce the welded joints so as
to resist the greatest wear pad stress. Suitable diagonal braces 37
are also preferably employed on opposite sides of the base section,
as shown in the drawings, to render the structure further rigid in
the critical region of high stress. At the extreme forward end of
the base section 20 and depending from its top plate 24 is a
stabilizing means 38 for the inner mid section 21 when the boom is
fully retracted, preventing the boom sections from shifting
laterally or twisting relative to one another.
The inner and outer mid sections 21 and 22 of the telescoping crane
boom are very similar in construction to the base section 20 except
that they are not equipped with the elements 30 and 31 and are of
successively smaller trapezoidal cross sectional shape for close
interfitting relationship with each other and with the base section
20. It is therefore believed that it is unnecessary to completely
describe the boom mid sections 21 and 22, and in the drawings
primed and double-primed reference numerals corresponding to the
numerals employed for various components of the base section 20 are
used to designate the identical parts in the inner and outer mid
sections 21 and 22. Except for differences in size, the
construction and functioning of these various detailed elements on
the boom sections 20, 21 and 22 are identical.
The inner and outer mid sections 21 and 22 contain one other
feature of difference from the base section 20 in that both of the
former are provided at their rear ends and tops with laterally
spaced wear pads 39 mounted in holders 40, FIG. 6, having
reinforcing and bracing means 41 and 42 at the rear end of the
particular boom section. The base section 20 requires no upper wear
pads since it does not operate inside of another boom section.
It may now be observed by referring particularly to FIGS. 5 and 6
that with the trapezoidal construction of the individual boom
sections, the lower wear pads 34, 34' and 34" may be located
directly under the side webs 25, 25' and 25" so as to receive
directly the forces or loads transmitted through these webs. This
advantageous arrangement of wear pads or rollers, in some cases, is
not readily attainable when rectangular cross sectional boom
sections are employed because the lower pads as well as the upper
pads must be arranged somewhat inwardly of the side webs. In such
cases, when the boom is loaded, the top and bottom plates or webs
of the boom sections have a tendency to distort or bow
transversely, and in this respect, one of the significant
advantages of the trapezoidal configuration is that it allows the
placement of the lower forward wear pads directly under the side
webs of the next innermost boom section.
Since various load capacities and lengths of booms are involved in
practice, precise sizes and dimensions of the trapezoidal sections
are somewhat variable. However, proportional limits can be defined.
Using the vertical height of the trapezoidal section, FIG. 14, for
unity, then the width of the top plate 24 will measure from 0.35 to
0.6 of unity and the bottom assembly or plate including the
elements 26 and 27 will measure from 0.8 to 1.1 of unity. Also, as
is well known, all beams including cantilever beams have a neutral
axis and for greatest beam efficiency, the masses above and below
the neutral axis should be nearly as equal as possible and these
masses should be as distant as possible from the neutral axis. The
theoretical neutral axis of the trapezoidal base section 20 is
indicated at 43 in FIG. 14 for illustrative purposes. The mass
above this axis including the top plate 24 is approximately equal
to the mass below the neutral axis including web 26 and bars 27 and
associated elements. As is apparent in FIG. 14, the major mass
elements 24 and 26-27 are located as far as possible on opposite
sides of the neutral axis.
While the forwardmost or fly section 23 of the boom has the same
characteristic trapezoidal shape and embodies a similar top plate
44, side webs 45, and bottom web 46 reinforced at its edges by
longitudinal bars 47, the various web stiffeners and bracing on the
base section 20 and mid sections 21 and 22 is unnecessary and need
not be employed. This is true because the fly section 23 is
customarily extended during use only when relatively light loads
are being handled and not under heavy loads. Therefore, the fly
section is never subjected to the high degrees of stress that the
other boom sections receive. Since the fly section 23 has no boom
section telescoped within it, it also requires no forward wear
plates or pads similar to the pads 34, 34' and 34". However, the
fly section 23 does require and is equipped with the upper rear
bearing pads or rollers, in some instances, and these are
conventional elements in the art. The fly section carries the
conventional nose assembly 48 shown in phantom lines in FIGS. 2 and
13.
The telescopic crane boom may be extended and retracted by any
desired hydraulic means or by mechanical cable means, or the like.
Preferably, it is hydraulically operated and a preferred operating
means of this character is illustrated somewhat schematically in
phantom lines in the drawings. Referring particularly to FIGS. 10
through 13, the piston rod 49 of the first ram is secured as at 50
to the back of base section 20 and the cylinder 51 of this first
ram is pivoted at 52 to the rear of inner mid section 21, the
forward end of this ram cylinder extending freely into the inner
mid section 21, FIG. 11.
A box element 53 is pivoted at 54 to the rear of outer mid section
22 and extends forwardly with a free end terminating adjacent the
forward end of the outer mid section, FIG. 12. The cylinder end 55
of another ram is pivoted at 56 to the rear end of inner mid
section 21 and extends forwardly into and through the box 53 and
the rod end 57 of this ram is pivotally connected at 58 to the
forward terminal end of the box 53, as shown in FIG. 12.
Finally, the cylinder end 59 of a third ram, FIG. 11, is pivotally
connected at 60 to the rear end of outer mid section 22 and the
forward end of this cylinder 59 terminates within and near the
forward end of mid section 22. The rod 61 of this third ram extends
forwardly into the fly section 23, FIG. 13, and is pivotally
connected therewith at 62. The arrangement provides for full
extension of the boom as illustrated in FIG. 9 and the full
retraction thereof to the condition shown in FIGS. 1 and 2 and all
adjusted positions in between the two extremes. Preferably, each of
the hydraulic rams, above-described, is an individually actuated
double acting ram.
As shown in the drawings, the boom fly section 23 is preferably
reinforced between its side webs 45 with a centrally located
transverse brace web 45' which extends continuously for the full
length of the fly section. Additionally, front lateral guides or
pads 63, 63' and 63" are provided on opposite sides of the base
section 20 and inner and outer mid sections 21 and 22 to stabilize
and guide the interfitting boom sections laterally. Similarly, rear
lateral guides or pads 64, 64' and 64" are provided on opposite
sides of the two boom mid sections and the fly sections 23, FIG.
6.
The terms and expressions which have been employed herein are used
as terms of description and not of limitation, and there is no
intention, in the use of such terms and expressions, of excluding
any equivalents of the features shown and described or portions
thereof but it is recognized that various modifications are
possible within the scope of the invention claimed.
* * * * *