Note: Descriptions are shown in the official language in which they were submitted.
13237 ~8
The present invention relates to constant velocity
universal ~oints for connecting drive and driven members and,
more particularly, the invention relates to universal ~oints
embodying means for achieving constant velocity drive between the
drlve and driven members when the members are in high speed
operation, offset at an angle, or have misalignment between the
members. The apparatus achieves this with roller balls which are
free to rotate in any direction. A multiplicity of such joints
can be cascaded, or connected in serles, to increase the degree
~0 of offset or misalignment that can be accommodated between the
drive and driven members and/or the spacing therebetween. One
embodiment of the system allows the ball ~oint to readily
separate, thus making a quick positive disconnect.
Many efforts are shown ln the known prior art to
achieve better transmlssion of torque. These usually involve
either a Cardan-type ~oint, such as shown in U.S. Patent No.
4,156,354, or a constant velocity ~oint of the type shown in U.S.
Patent No. 2,910,84S. Each of these devlces lnvolve transmisslon
of torque between rotative members and can be said to involve an
inner ~oint member fixed to one of the rotative members, and an
outer ~oint member fixed to the other of the rotatlve members.
23768
U.S. Patent No. 4,156,354 shows a high-speed, high-torque
transmitting joint where the torque is transmitted through roller bodies
interposed between inner and outer joint members wherein the roller bodies
are equidistantly spaced circumferentially of the joint assembly, with each
S roller body being received in planar recesses in the inner joint member for
radially slidable engagement relative thereto. This construction increases
the complexity and size of the joint, and requires close maintenance of sur-
façe finish and other manufacturing tolerances. Because of these reasons
and the increased friction resulting from the sliding relationship of the
planar surfaces, this type of joint has decreased smoothness of operation,
while at the same time having increased manufacturing costs.
U.S. Patent No. 2,910,~45,shows a constant velocity universal
~oint intended for connecting two rotative members only where angularly
misaligned joints are to be found, and not where axially aligned or slightly
misaligned joints are to~ found and, therefore, shows a ~oint limited in its
usefulness. Further, the joint utilizes spherical drive members restrained
to rotate about journals provided on the drive member. The restrainlng of
the drive members provides increased fr~ction, which is unsatisfactory in a
universal ~oint.
What is needed to solve the above problems present in the prior
art is an improved constant velocity universal ~oint usable for angular and
axial misalignment and having increased smoothness of operation due to the
elimination of planar surfaces on the drive members and wh1ch can be made
~ with lower manufactur~ng costs because of less crit~cal tolerances and sur-
; 25 face finishes.
In addition, increased friction results because of the sliding
relationship of the planar surfaces. For these reasons, it provides a
generally unsatisfactory solution to the problem of torque trans~iss~on.
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1323768
U.S. Patent No. 2,910,845 utilizes spherical drive
members restrained to rotate about ~ournals provided on the drive
member which again causes increased friction and is
unsatisfactory.
Brlefly, the present invention may be described as a
constant velocity universal ~oint for transmitting driving torque
including a pintle-type inner ~oint member fixed to one of the
rotative members and an outer~ member fixed to the other of the
rotative members, with a plurality of roller balls recelved in an
aperture in the inner ~oint member, and having the roller balls
engaged in groove means in the outer ~oint member, with a
spherical portion of at least one of each of the roller bodies
being in contact with a spherical portion of at least one other
roller bodles in a manner whereby the roller bodies provide
mutual support for each other inwardly of the inner ~oint member
towards the center of the ~oint. A quick disconnect version of
the invention is also shown. Additionally, a cascaded ~oint made
up of a multiplicity of such universal ~oints is also shown.
The combination of the unrestricted rotation of the
roller balls in the inner ~oint member, the mutual support
provided by the roller ball cluster, and the movement of the
roller balls in the grooves placed about the clrcumference of the
outer member provides for constant velocity torque tranmission
with a minimum of effort and vibration. The joint will remain a
constant velocity joint until the inner ~oint member is
articulated past approximately eight ~8) degrees, which it ls
contemplated will cover a large number of uses for the present
invention.
Thus, the present inventlon provides a constant
velocity universal ~oint having unrestricted rotation of the
roller balls utilized therein.
13237~
The present invention also provides a constant velocity
universal ~oint having the roller balls utilized therein travel
in rectilinear grooves in the outer member thereof, the
rectilinear grooves having cylindrical ball contact surfaces~
The present invention agaln provides that the roller
balls used in transmitting torque in a constant velocity
universal jolnt are all in contact with each other.
The present invention further provides that the plane
of torque transmission of the universal joint does not reamin
perpendicular to the axis of rotation as the ~oint is
articulated.
The present invention again provides a constant
velocity universal ~oint with lower manufacturing costs than
present day devices.
The present ir.vention also provides a constant velocity
universal ~oint which eliminates the use of planar drive surfaces
in the transmission of torque.
The present lnvention again provides a constant velocly
universal ~oint having increased smoothness of performance.
The present invention also provides a constant velocity
universal ~olnt having less critical manufacturing tolerances.
The present lnvention again provides an improved
constant velocity ~oint wh~ch is capable of transmitting torque
over a smaller moment arm than prlor art universal ~oints,
thereby providing smaller size ~oints with smoother operation.
The present invention further provides a constant
veloclty universal ~oint that can be connected in series with a
multipllclty o~ like universal ~oints in a cascaded ~olnt to
-- 4
~32~7 ~8
provide for relatively large amounts of offset or
misalignment between the drive and driven members which are
connected by such joints.
According to one aspect thereof the present invention
thus provides a constant velocity universal joint for
transmitting driving torque, said universal joint comprising:
an inner joint member having a central axis; three apertures
circumferentially disposed equidistant from each other in
said inner joint member along a plane substantially
perpendicular to said central axis, said three apertures
defining three equally spaced radially oriented segment
portions, each of said segment portions along said
perpendicular plane having at least two planar surface; three
lS torque transmitting spherical balls, one of each of said
three torque transmitting spherical balls received in one of
each of said three apertures for free rotatable movement
therein, said three spherical balls being arranged in said
three apertures with a spherical portion of each ball being
in direct abutting contact with a spherical portion of each
of the others of said three spherical balls such that each of
said ~pherical balls provides mutual support for the others
oP said spherical balls by said direct abutting contact
between said spherical portiona thereof, each of said
spherical balls further having a single point of contact with
one of said at least two planar surfaces of each of said
segment portions; an outer joint member having one end, an
. opposite end and thre~ spaced apart rectilinear grooves
- therein, each of said three spherical balls being arranged in
said three apertures to extend radially from within said
three apertures into engagement with said three spaced apart
rectilinear grooves in said one end of said outer joint
member to effect transmission of torque between said inner
and outer joint me~bers such that as torque is translated
from said inner to said outer joint member the force
translating said
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:
,~
13237 ~8
torque is applied to said three spherical balls at said single
point of contact between said planar surfaces of said segment
portions of said inner joint member and said three spherical
balls whereby frictional contact between said planar surfaces of
said segment portions of said inner ~oint member is minimized to
maximize the smoothness of said tor~ue being translated as well
as to permit each of said three spherical balls to move
unrestricted relative to a respective one of said at least two
planar surfaces of each of said segment portions to seek a single
point of contact along said respective one of said at least two
planar surfaces of each of said segment portions and
substantially balance the loads carried through each of said
three spherical balls, said three spherical balls further being
restricted to relative movement within limits defined by said
outer joint member and each other of said three spherical balls;
said inner joint member capable of articulating with respect to
said outer joint member; and one of said joint members being
adapted to receive torque and to transmit torque to the othsr of
said ~oint members when the other of said joint members is not in
axial alignment with said one of said ~oint members.
In one embodiment of the present invention the ~oint
further comprises a second inner ~oint member having a central
axis; three apertures circumferentially disposed equidistant
from each other along a plane substantially perpendicular to said
central axis, said three apertures defining three equally spaced
radially oriented segment portions, three additional spherical
balls being arranged in said three apertures of said second inner
~oint member to extend radially from within said three apertures
into engagement with said three spaced apart rectilinear grooves
in said opposite end of said outer ~oint member to effect
transmission of torque between said inner and outer ~oint
members. Desirably the ~oint further comprises a resilient
posltion pad mounted in said outer ~oint member between said
lnner ~o~.nt member and said second inner ~oint member.
Preferably the ~oint further comprlses a pair of end caps; one
- 5a -
13237~
of said pair of end caps being mounted to said one end of
said outer joint member with said inner joint member
extending therethrough, said other of said pair of end caps
being mounted to said opposite end of said outer joint member
with said second inter joint memher extending therethrough.
In another embodiment of the present invention said
inner joint member is partly contained within said outer
joint member and further comprising means to maintain said
inner joint member partly contained within said outer joint
member in driving engagement with said outer joint member.
Suitably the joint further comprises means within said outer
joint member in contact with each of said outer joint member
and said inner joint member to maintain friction on said
inner joint member. Desirably said three spherical balls are,
circumferentially equidistantly spaced about said constant
velocity,universal joint. Suitably each of said rectilinear
grooves is right circular cylindrical in shape in a
' transverse plane extending through said plurality of spaced
apart rectilinear grooves.
~,
; 20 In another aspect thereof the present invention provides
a constant velocity universal joint for transmitting driving
torque, comprising in combination: a barrel race having
groove means therein; a driveshaft received in one end of
said barrel race, said driveshaft further comprising:
aperture means in said driveshaft to receive a plurality of
' roller balls; and a plurality of roller balls received in
said aperture means for unrestricted movement therein; a
driver received in the opposite end of said barrel race, said
driver further comprising: aperture means; and a plurality of
roller balls received in said aperture means for unrestricted
movement therein; means interposed between said driveshaft
,
, -5b-
` ~J
:`
~3~37~
and said driver to maintain friction thereon; and a pair of
end caps attached to said barrel race to retain said
driveshaft and said driver in torque transmitting engagement
with said barrel race, wherein said roller balls are
spherical in nature and are arranged in said aperture means
of said driveshaft and said driver so that each of said
roller balls has its spherical portion in direct abutting
enqagement with a spherical portion of at least two adjacent
other of said roller balls on either side of said roller ball
in said driveshaft or driver to provide mutual support
therefor.
In a still further aspect of the present invention there
is provided a double constant ~elocity universal joint for
transmitting driving torque comprising, in combination: a
generally cylindrical outer joint members extending out of
each end of said outer joint member; aperture means in each
said inner joint member; a plurality of roller balls
rollingly received in said aperture means of each said inner
joint member wherein each of said roller balls is spherical
in nature and wherein said roller balls received in said
aperture means of each said inner joint member are arranged
so that each of said roller balls has its spherical portion
in direct abutting contact with a spherical portion of at
least two other roller balls on either side of said roller
ball in said aperture means of said inner joint member to
provide mutual support therefore; groove means in each end of
said outer joint member, said groove means rollingly
receiving said roller balls which are received in said
aperture means said inner joint member which extends out of
said end of said outer joint member; and each of said inner
joint members ~eing capable of articulating with respect to
said outer joint member.
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.
~323~ ~
The present invention will be further described with
reference to the accompanying drawings wherein like reference
characters designate corresponding parts in the several views
in which:
Figure 1 is a diagrammatic view of a novel wrench
embodying the universal ~oint of the present invention as the
wrench drive;
Figure 2 is a diagrammatic view illustrating a
construction embodying the present invention being in
conjunction with a standard ratchet wrench of the square
drive type;
Figure 3 is a diagrammatic view showing a construction
embodying the present invention being utilized where an
offset between adjoining torque transmitting shafts is
present;
Figure 4 is a diagrammatic view showing a construction
embodying the present invention is used where angular
misalignment and/or offset is desired;
-5d-
C
~ 132~768
Figure 5 is a diagrammatic view showing a construction enbodying a
multiplicity of universal joints of the present inven~ion connected 1n
series in a cascaded ~oint;
Figure 6 1s a diagrammatic view illustrating a ~onstruction
embodying the present invention being used in a power take-off syste~;
Figure 7 is a right end view of the outer ~oint mRmher w1th the
inner joint member in ax~al alignment with the outer m~mb~r ~d partially
cutaway; : . `
Figure 8 is a sectional view taken in the d1rection of the arrows
along the section line 8-8 of Figure 7;
Figure 9 1s a sectional v1ew tAken 1n the d1rect~Rn Qf th~ arrows
along the section line 9-9 of Figure 8;
F19ure lO 1s a v1ew similar to that of Flgure 7 but show1ng a ver-
s10n of the present 1nvent10n havlng four roller balls 1nstead of three; :~
Figure 11 is an elevat10nal v1ew of a s1ngle constant velocitY un1-
versal ~oint, partly 1n sect10n, showing the 1nner Joint ~e~ber art1culated;
Figure 12 is a sect10nal view taken 1n the d1rect~on of the arrows
along the section line 12-12 of F19ure 11, and show1ng the un1versal ~olnt at ;;
rest;
Figure 13 is a view identical to F19ure 12, but showln~ the s1ngle
constant velocity un1versal ~oint under operat1ng cond1tlons w1th torque
applied to the inner ~oint member 1n the direct10n of the arr*~
Figure 14 1s an elevational view, partly 1n sect10n, of ~ double
constant velocity un~vers~l Jo1nt;
.,
~32~7 ~8
Figure 15 is an elevational view partly in section of a
single constant velocity universal joint having the quick
disconnect feature of the present invention; and
Figure 16 is a view identical to Figure lS but showing
the plunger of the inner joint member in its activated
position so that the roller balls may drop inwardly toward
the plunger and the inner joint member may be removed from
the outer joint member.
Referring to Figures 1 through 6, several uses of the
present invention are shown. In Figure 1 there i8 shown a
novel ratchet wrench 23 having a constant velocity universal
joint, generally designated by the numeral 20, included as an
integral part thereof. The constant velocity universal joint
20 may be considered to be of the quick disconnect type, as
hereinafter described, with the disconnect feature being
actuated by a spring-loaded push button 23a. The ~oint 20
itself i8 made up of an outer ~oint member 22 and an inner
~oint or pintle member 21. The wrench 23 with the integral
inner ~oint member 21 may be part of a set which includes a
multiplicity of di~ferent sizes of sockets, each of which can
interchangeably be assembled to the inner joint member 21 to
serve as an outer joint member.
It is, of course, also contemplated that other tools,
such as screwdrivertype tools, pneumatic wrenches and other
-tools, and electric wrenches and other tools can be
constructed with an integral constant velocity universal
joint.
In Figure 2 there is shown a conventional ratchet wrench
27 of the square drive type, the drive beinq provided through
an extension 28 which is square in cross-section, as is known
in the art.
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V
; A
1~237 ~8
The extension 28 fits into a socket 29 provided in an outer
joint member 26 of a constant velocity universal joint 24.
The universal joint 24 is of the non-quick disconnect type,
as hereinafter described, and is made up of an inner joint or
pîntle member 25. It is also contemplated that the univer~al
joint 24 can be applied to other types of driven tools, such
as screwdrivers, pneumatic wrenches and screwdrivers, and
electric wrenches and screwdrivers.
In Figure 3 there is shown an application where offset
and possible variation in axial spacing exists between the
shaft of a motor 30 and the driveshaft of a gear box 31. The
motor and gear box are shown joined by a double constant
velocity universal joint 32 embodying the construction used
in the present invention.
Figure 4 shows the same motor and gear box as shown in
Figure 3 but under a condition where angular misalignment
and/or offset is desired. Again, the shaft of the motor 30
and the driveshaft of the gear box 31 are joined by a double
constant velocity universal joint, generally designated by
the numeral 32.
Figure 5 shows an application where a substantial offset
exists between the shaft of the motor 30 and the drive shaft
of the gear box 31. The motor and the gear box are joined by
a cascaded series of universal joints 32 embodying the
construction used in the present invention.
There is shown in Figure 6 a situation where the
construction of the present invention is used as a power
take-off. A source of power such as a farm implement is
illustrated by the numeral 33 and, thus, is towingly
connected to
.
~ - 8 -
. .
13237~8
a power actuated attachment 34. The implement 33 provides a
driving force for the operation of the power attachment 34.
In this case, a quick disconnect, single universal U-joint 37
is utilized in providing this driving force.
Referring now to Figures 7 and 8, the outer joint member
26 has the socket 29 provided in one end thereof to receive
the ratchet wrench 27 shown in Figure 2, or any other device
to be driven. Immediately adjacent the socket 29 is an
enlarged portion 38 having three rectilinear
circumferentially æpaced groove~ 39. The grooves 39 may
spaced egually around the circumference, and have a right
circular cylindrical shape in a plane extending transversely
through the outer joint member 26 to receive the three
Gpherical roller balls 40. In the single constant velocity
universal joint the enlarged portion 38 of the outer joint
member 26 receives the inner joint member, generally
designated by the numeral 25. Before insertion, the three
spherical roller balls 40 are inserted in circular apertures
41 provided in the head portion 42 of the inner joint member
25. The inner joint member 25 having the spherical roller
balls 40 inserted therein is then, in turn, inserted into the
enlarged portion 38 of the outer joint member 26 until the
head portion 42 of the inner joint member 25 contact~ a
position washer 44. Slight additional ~orce is then applied
and the deformations 45 of the outer joint member are
deformed, by staking or otherwise, a distance sufficient to
prevent removal of the inner joint member 25.
Several considerations are important when the dimensions
of the single constant velocity universal joint are
considered. The circular apertures 41 in the head portion
42 of the inner joint member 25 must be such as to
3 2 3 7 6?~ beZ ~e~ ~ ~e seg ~ ent ~Oi~;~n~ a5
- allow free rotation of the roller balls 40~and ball-to-ball contact among
the roller balls. The dimension across the grooves 39 of the outer joint
member 26 must be such that when the inner joint member 25 is axially
aligned with the outer joint member 26 there is a rolllng plunge fit between
the roller balls 40 and the rectilinear grooves 39.
The position washer 44 is preferably made of resilient material9
such as duro nitrile or the like, and the relationship between the position
washer and the deformations 45 must be such that the position washer 44
exerts enough pressure against the head port10n 42 of the inner ~oint member
25 such that the pintle member, when articulated, w~ll be able to hold any
angle at which ~t is placed under its own weight. This feature conforms to
, a Society of Automotive Engineers sfandard. One source for the duro nitrile
material used to make the position washer is 60shen Rubber Company. If
desired, an aperture 46 may be provided in the position washer 44.
In addition, the deformations must be such as to keep all the
roller balls 40 in the rectilinear grooves 39 when the inner ~oint member 25
is at its full angular articulation. The deformed areas are to allow no
free axial movementr and they are not to interfere with the rotatlon of the
shaft when it 1s at an angle of up to thirty degree (30) from the outer
~oint member 26.
It can be seen that with this construction there is ball-to-b~ll
contact between the sphertcal roller balls 40, and that all the torque is
transmitted through the roller balls 40 to the rectilinear spherical grooves
39.
It is contemplated that a version of the present invention uti-
lizing four roller balls may be constructed as shown ~n Figure lO, and used
-10-
1~237~
when large amounts of torque are to be transmitted. As before, there are a
plurality (in this case four) of rectilinear grooves 39 equally spaced
around the circumferen~e of the enlarged portion 38 of the outer joint
member 26. The~apertures 41 in the inner joint member 25 must meet the
same requirements as before, and the four apertures 41 are provided at right
angles to each other. In this case the cross-section of the inner joint
member 25 is reduced, so that some material is lèft to strengthen the inner
joint member at the center thereof, as indicated by the numeral 25a, and
ball-to-ball contact dmong the four spherical roller balls 40 is still main-
tained. It must be understood that torque transmission in any of these
devices takes place mainly because of the interact~on of the roller balls 40
in ~he spherical rectilinear grQove,s 39. It can be easily seen that ver-
sions of the present invention having more than four roller balls may be
provided.
As shown tn Figure 8, to provide for easy attachment of the inner
~oint member or pintle 25 to a socket, not shown, or other device for
receiving torque from the universal ~oint, the inner ~oint member 25 is pro-
; vided with a standard ball detent in the form of a ball bearing 50 held in
place~by the spring 51.
Referring now to Figure 11, there is shown a version of the single
constant velocity universal ~oint having a different outer configuration
from the device above described. The socket 29 thereof is not shown for
ease of illustration. As before, the outer ~oint member 26 has an enlarged
portion 38 having a plurality of spaced rectilinear grooves 39 in which a
plurality of roller balls 40 are received. The yrooves 39 are preferably
cylindrical ~n transverse section as in the case of the universal ~oint
rcl~r
~ illustrated in Figures 7 and 8. The roller balls 40 are received in~aper-
!~ tures in the head portion 42 of the inner ~oint member 25. It can be seen
-11 -
.~
:,
1323768
that as the inner joint member or pintle is articulated, as soon as the
~e~ ber
inner joint~articulates to an axis away from the axis of the outer joint
member, the plane of torque transmission is no longer perpendicular to the
axis of the outer joint member because the roller balls 40 pull away from
the rectilinea~ grooves 39. This is possible because of the unrestricted
rotation and linear translation (movement) of the roller balls 40 of this
invention, a feature not present in the previously discussed prior art devi-
ces.
As Figure 12 shows, when the constant velocity universal ~oint is
at rest one of the roller balls 40 pulls substantially out of the groove
39, wh~1e the remainder of the roller balls 40 are held against the grooves
by gravity. However, as shown in Figure 13, as soon as the ~oint starts to
rotate, because of circumferential forces, the roller balls 40 all assume a
position approximately e~uidistant from the axis of rotat~on of the inner
~oint member 25 and all are slightly out of the rectilinear grooves 39.
As can be seen, the point of torque transmission in this situation becomes a
point-to-point contact at approximately the same position, respectively,
between the roller balls 40 and each of the rect~linear grooves 39. It is
believed that the moment arm from the center of rotation to the point T, for
the present invention, is smaller than any of the previously discussed
prior art devices thereby providing for more efficient and smoother torque
transmission. This feature, coupled with the unrestricted rotat1On of the
balls as the joint is rotated, provides for lower frictional forces also,
mak~ng the present ~oint a substantial advance over the prior art.
A version of the present invention as embodied 1n a double
constant velocity universal ~o1nt can be seen in Figure 14. The double
constant velocity universal ~oint shown in Figure 14~fconsists of a dri-
1323768
veshaft, generally designated by the numeral 55; a barrel
race, generally designated by the numeral 56; and a driver,
generally designated by the numeral 57.
The driveshaft 55 has a squared off extension portion 54
for ease of attachment to other devices, and is provided with
the standard detent ball 58 which is spring-loaded as
described hereinbefore. Of course, the extension portion 54
could also be round, and this would be the preferred
configuration in the case of a universal joint intended to be
connected to the driveshaft of a motor, for example. In any
case, a head portion 63 of the driveshaft is similar to the
single constant velocity universal joint ~ust described in
that it has a plurality of circular apertures 67 spaced
equidistantly around the head portion to receive a plurality
of roller balls 65. As before, there is ball-to-ball contact
between the roller balls 65 as in the single constant
velocity universal joint. The driveshaft 55 is inserted into
the barrel race 56 and one of the identical end caps 61,
which was placed over the head portion 63 of the driveshaft
55 before the roller balls 65 were inserted, is
press-~it onto a barrel 53. A position pad 62 is then
inserted, and a second identical end cap is placed over the
head portion 6~ of the driver 57, the identical roller balls
65 are placed in identical circular apertures 67, and then
the end cap 61 is press-fit onto the barrel 53. In the
illustrated embodiment there are three roller balls 65 in the
driveshaft and the driver and, therefore, there will be three
equally spaced rectilinear grooves 66 in the barrel 53. As
before, the dimensions across the grooves are of importance.
When the axis of the driveshaft and/or driver are in
alignment with the axis of the barrel the dimensions across
the roller balls 65 and the rectilinear grooves 66 must be
such as to provide a rolling plunge fit.
- 13 -
~ X
7 ~ 8
Likewise, the dimension of the position pad 62 is important. As
before, this position pad is preferably made of resilient material, such as
duro nitrile, and must be of a sufficient dimenslon such that when the end
caps 61 are in place it exerts sufficient force against the head portion 63
of the driveshaft and the head portion 64 of the driver 57 so that the
driver and the driveshaft will hold any angle they are placed at under their
own weight. If desired, a hole 70 may be placed in the position pad 62. To
complete the construction, a socket 59 having a standard detent 60 is pro-
vided in the driver 57.
In embodiments where a quick disconnect version of a constant
velocity universal joint is required, the version of the invention shown in
. Figures i~} and ~ may be used. For, ease of lllustration, there is shown a
version of the universal joint of the present invention having two roller
balls, but it should be understood that versions having three and four
roller balls, such as those just described, or any practical number, may
also be constructed in this manner.
In the quick disconnect universal drive shown in Figures 15 and
16, as before, there is an outer drive member 75 having a plurality of r19ht
circular cylindr1cal rectilinear grooves 79 into which roller balls 83 are
received. Deformations 76 are provided for the purposes previously
described, but in this instance the inner drive member 77, because of its
construction, can permit the roller balls 83 to move inwardly toward the
center of the ~oint a distance suffic~ent to clear the deformations 76.
This is accomplished by having the inner drive member being hollow in
construction and being provided with a plunger 81 having an ~nclined surface
81A against which the roller balls 83 rest. The plunger 81 is rece~ved in
the hollow ~nterior of the inner drive member 77 and is retained in its
retracted position b~ a spring 82 which is shown in its normally extended
position in Figure ~r. Since the spring ls retained between a bearlng por~
-14-
1~237 ~8
tion 85 on the interior of the inner drive member and a land
87 provided on the plunger 81, when the plunger is pushed in
a direction toward the outer drive member 75, the spring 82
will compress allowing the plunger to move in an axial
direction toward the outer drive member, and the roller balls
83 to collapse toward the axis of the plunger. Because of
the dimensions of the plunger, the roller balls 83 move
inwardly sufficiently to clear the deformations 76, thus
allowing the disassembly of the inner drive member 77 from
the outer drive member 75, as illustrated in Figure 16.
- 15 -
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