Note : Les descriptions sont présentées dans la langue officielle dans laquelle elles ont été soumises.
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The present invention relates to a torque multiplier
assembly that is portable, compact, and may be easily and
conveniently disposed adjacent a nut, bolt or similar
threaded elements to removably engage the same.
The present invention may provide a torque multiplier
assembly that is capable of exerting the same maximum
torque on a nut, bolt head, or other rotatable elementl
as my prior invention described in U.S. Patent No. 3,564,955
entitled "High Torque Wrench Assembly" that was granted on
February 23, 1971, but one that has the operational advantage
that it is more compact, lighter in weight than my prior
high torque wrench, and does not require a torque indicating
device as a part thereof.
The present invention may provide a torque multiplier
assembly that is actuated by a conventional elongate low
torque output wrench that may be manually adjusted to provide
any one of a number of maximum torques and the torque output
of the present torque multiplier assembly being the torque
input of the torque wrench multiplied by a ~actor that is
inherent to the gear structure of the torque multiplier
assembly.
The present invention may also provide a torque
multiplier assembly that is used only when a relatively
torque output is required, and the user of the invention
being free to use the lightweight low torque producing
wrench in its normal manner when not being used to actuate
the torque multiplier assembly.
The present invention may also provide a torque
multiplier assembly in which the torque produced thereby may
be more accurately determined as to the magnitude thereof
than is possible with the torque wrench described in my
previous patent, which prior art invention includes a
torque indicating device of the torsion bar type.
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FIG. 1 is a perspective view of the invention
fully illustrating one side thereof, and the view also includ-
ing a low torque output wrench used in actuating the torque
multiplier assembly, as well as a stabilizing bar that may
be used to maintain the torque multiplier in a fixed position
relative to the rotatable element to which torque is being
applied,
FIG. 2 is a second perspective view of the torque
multiplier assembly illustratin~ a second side thereof,
FIG. 3 is an end elevational view of the torque
multiplier assembly,
FIG. 4 is a second end elevational view of the torque
multiplier assembly with the torque output element removably
engaging a socket wrench which, in turn, engages a nut or
bolt head of the element that is to be rotated,
FIG. 5 is a front elevational view of the torque
multiplier assembly,
FIG. 6 is a transverse cross-sectional view of the
torque multiplier assembly taken on the line 6-6 of FIG. 5, and
FIG. 7 is a second transverse cross-sectional view
of the torque multiplier assembly taken on the line 7-7 of
FIG. 5.
The torque multiplier assembly A of the present
invention as may best be seen in FIGS. 1, 2, 6 and 7 is actua-
ted by a conventional elongate torque wrench B that has a
head C and the wrench being commercially available. The torque
multiplier assembly A is preferably held in a stabilized
stationary position when imparting torque to a desired rotat-
able element by use of a stabilizing rod D shown in FIG. 1
or other anchoring means.
The torque wrench B includes an elongate handle
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10 that has a rotatable portion 12 that moves longitudinally
relative the handle as the portion 12 is rotated. The
handle 12 has a first scale 14 over which the free edge
portion 12a of the rotatable portion 12 moves as the handle
10 is rotated. The first scale 1~ has num~ers 14a thereon
which indicate the maximum torque that can be applied to a
rotatable element by use of the head C. Torque wrenches B
of the above-described type are commercially available and
are normally designed to provide not over fifty foot pounds
of torque through the head C. The head C includes a torque
imparting means 16 which may be either a protuberance of
non-circular transverse cross-section or a recess that is
likewise not of circular transverse cross-section. The
torque imparting means 16 as may be seen in FIG. 6 is
adapted to removably engage a torque receiving member 18 as
shown in FIG. 6 that is of non-circular transverse cross-
section, and is a part of the torque multiplier assembly A.
The torque wrench B is of such structure that when the
maximum torque for which it is set is reached the torque
wrench becomes inoperative into far as producing additional
torque.
The torque multiplier assembly A as may be seen
in the drawings includes first and second housing half
portions E and El that have first and second abutting
surfaces 20 and 22. First and second transverse bores 24
and 26 are formed on the peripheral portions of the housing
half portions E and E', with the second bores having threads
on the interior thereof that are engaged by cap screws 28
that serve to hold the two housing half portions in abutting
contact.
The first and second housing half portion~ E and
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E' have an opening 30 of substantial diameter extending
transversely therethrough, which opening is defined by
first circular side walls-32 formed in the first and second
housing half portions E and E'. The first and second
housing half portions E and E' have an elongate opening 34
therein that is tangential to the opening 30, with the
elongate opening 34 being defined by a second circular side
wall within the first and second housing half portion E and
E'.
A heavy torque output shaft 38 is provided that
has a longitudinal slot 42 therein that is engaged by a key
40, with the key also engaging a radially aligned slot 44
formed on the interior surface of a cylindrical hub 46 of a
worm gear 48 as shown in FIGS. 6 and 7. The worm gear 48
has teeth 50 on the outer periphery thereof.
A pair of laterally spaced anti-friction roller
bearing assemblies 52 are provided, each of which assemblies
includes a number of tapered rollers 54 that rotatably
engage a bearing cup 56 and bearing cone 58. The shaft 38
20 as may best be seen in FIG. 7 has a torque output plug 60
of non-circular transverse cross-section projecting outwardly
from one end thereof and a torque output recess 62 extending
into the shaft 38 from the opposite end thereof.
A pair of oil seals 64 are disposed within the
first and second housing portions E and E' as shown in
FIG. 7 to encircle the shaft 38, with the oil seals being
removably held in position within the housing portion by a
pair of retainer seals 66. A pair of retainer rings 68
are provided that abut against the retainer seals 66, and
30 the retainer rings removably engaging grooves 70 that extend
into the first circular side wall 32. The worm gear 48 is
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held in a fixed longitudinal position on the shaft 38 by a
pair of tranversely spaced retainer rings 67 that engage
grooves 69 formed in the shaft 38.
A pair of laterally spaced, anti-friction ball
bearing assemblies 72 are provided, with each assembly
including an outer race 74, inner race 78 and a numbe~ Gf
balls 76 situated therebetween. A worm 80 is provided that
has cylindrical end portions 82, with each of the end
portions being rotatably supported by the inner races 78
of the anti-friction ball bearing assemblies 72~ The worm
80 and the anti-friction ball bearing assembly 72 as can best
be seen in FIG. 6 are mounted in the elongate opening 34
defined between the first and second housing half portions E
and E'.
A torque receiving plug 18 projects outwardly
from one end of the worm 80, which plug is of non-circular
transverse cross-section. A torque receiving cavity 18
extends inwardly into an opposite end of the worm 80. The
ball bearing assembly 72 as may best be seen in FIG. 6
are maintained in a fixed position within the first and
second housing half portions E and E' by a pair of longitu-
dinally spaced ring-shaped retainers 88 that engage
circular grooves 90 formed in the half housing portions.
Two transversely aligned lugs 92 project outwardly
from the half housing portions E and E' as shown in FIGS. 6
and 7, with each lug having a semi-circular groove 94
extending therethrough, with the grooves cooperating to
provide a first cylindrical opening 96. The first opening
96 may be removably engaged by the stabilizing rod B as
shown in FIG. 1. The pair of lugs 92 also have transversely
and axially aligned second openings 98 therein, which
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openings may be engaged by a chain or the like (not shown)
to hold the torque multiplier assembly A in a substantially
stationary position during the time that it is being used
to supply torque through the plug 60 or recess 62 shown in
FIG. 7. In FIG. 4 the plug 60 is shown in removable
engagement with a conventional socket wrench 100, which
wrench 100 is in turn in~engagement with a nut or bolt head
102 to which it is desired to impart a high torque either
in loosening or rotating the same.
The elongate torque wrench B has a longitudinally
extending first numbered scale 14 thereon over which the
rotatable portion 12 moves as the latter is rotated, with
the free edge portion 12a of the portion 12 when transversely
aligned with a graduation of scale 14 indicating the maximum
torque in foot pounds that can be delivered by the torque
wrench B. The gradua~ions 14 have numbers 14a imprinted
on the handle B that indicate the magnitude of the torque.
~ he handle B preferably has a second longitudinal
scale 15 thereon opposite the scale 14, with numbers 15a
of the second scale indicating the torque output of the
torque multiplier assembly A. Each number 15a is obtained
by multiplying the number 14a opposite thereof by the factor
previously described. Once the factor has been determined
it may be used to obtain all of the torque output numbers
on the second scale 15, for the friction between the gears
and bearing assemblies will not vary appreciably over the
entire range of the low torque input to the multiplier
assembly A.
The torque wrench B may be used individually over
the entire low torque range thereof in a conventional
manner. When a higher torque is required the torque multiplier
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assembly A is placed in direct engagement with a socket
wrench as shown in FIG. 4 to apply a desired high torque
to a nut or bolt head 102. The torque multiplier assembly A
is held in a non-rotatable position relative to the nut or
bolt head 102 by use of the stabilizer rod D, or a chain or
restraining element (not shown) that extends through openings
98 and is secured to a suitable anchor. The torque wrench B
is now placed in operative engagement with the multiplier
assembly A, and the wrench portion 12 rotated for it to
move longitudinally on the handle 10 until the free edge 12a
thereof is tranversely aligned with the graduation 15 that
indicates the maximum torque output that will be exerted by
the plug 60 or recess 62 when the torque wrench is exerting
the maximum torque input 14a for which it is set. The torque
wrench B exerts torque on torque multiplier assembly A by
being pivoted upwardly and downwardly relative thereto as
shown in FIG. 4.
The torque multiplier assembly A is illustrated as
having a projecting torque receiving member 18 of non-circular
tranverse cross-section on one end of worm 80 and a torque
receiving recess 18 on the opposite end thereof, each of
which may receive input torque from the torque input member
16 of head C of torque wrench B. The direction of rotation
of torque output plug 60 is controlled by changing the
direction in which torque is imparted to worm 80 by torque
wrench B. From the prior description of torque multiplier
assembly A it will be apparent that lubricant may be d~sposed
within the housing portions E and E', and retained therein
by the oil seals 64.
The use and operation of the torque multiplier
assembly A has been previously described in detail and need
not be repeated.