Note: Descriptions are shown in the official language in which they were submitted.
This is a division of Canadian patent application
Serial No. 309,769 which was filed on 22 August 1978.
Background oE the Invention
Field of the Invention. This invention relates to a
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friction brake and, more particularly, to such a brake
which includes a plurality of discs and is hydraulically
cooled.
Description of the_Prior Art. There have heretofore
been provided a number of friction brakes which utilize a
plurality of discs and provide hydraulic oil for cooling
the brake such as those disclosed in United States Patents
2,823,770; 3,580,369; and 3,~84,708. Although brakes of
this type include a number oE configurations and have been
successfully utilized to provide reliable braking of a
wheel mounted on an axlet there continues to exist a need
for such brakes which are more reliable, easier to install
and more accessible for repair.
Summary oE the Invention
In accordan~e with an aspect of the invention there is
provided an improved friction brake for a wheel which has
a hub and is mounted for rotation about a central axis on
an axle spindle, said brake being of the type which
includes a housing mounted on an inward portion o~ said
spindle to encircle said hub for sealed engagement
therewith to define a sealed annular chamber about said
hub and said spindle, a pair of disc means coaxially
ali~ned with said axis and with each other and mounted
within said chamber for movement along said axis, a first
disc means of said pair being non-rotatable and mounted
relative to said housing and a second disc means of said
pair being rotatable and mounted relative to said hub,
said first disc means including an outer disc and an inner
disc with the remainder of said pair of disc means axial~y
disposed therebetween, annular brake actua-ting means
mounted within said chamber in alignment with said pair of
disc means for selective application of force to said
inner disc as said outer disc makes contact with an
interior wall of said housing to produce frictional
contact between said pair of disc means, said improvement
comprising: at least three cylindrical devices mounted to
said housing to extend in an axial direction into said
chamber at generally equally circumferentially spaced
locations about said inner disc and said outer disc; each
of said devices having biasing means mounted thereon which
make contact with said inner and said outer discs tending
to increase the distance therebetween; a disc retainer
mounted on said device to produce a predetermined
frictional contact therebetween which is greater than a
maximum Eorce generated by said biasing means; means for
en~aging said inner disc with said disc retainer to allow
limi-ted axial movement of said inner disc without causing
said disc retainer to move along said device; and said
actuating means being capable of supplying sufficient
~0 force to said inner disc to overcome said predetermined
frictional contact and said maximum force to position said
disc re~ainer on said device to establish the location of
- said 1imited axial movement of said inner disc within said
chamber.
It is, therefore, an ob~ect o~ this invention to
provide a reliable friction brake which employs a
plurality o~ hydraulically cooled discs and includes
Eeatures which provide means for initial testing of
various components thereof and for ease of assembl~.
It is also an object to provide a friction brake o
- the type described which can be more readily and
inexpensively repaired should it be required.
These and other objects of the invention are provided
in a preferred embodiment thereof which includes a
friction brake for a wheel which has a hub and is mounted
for rotation around a central axis on an axle spindle. A
backing plate is mounted about an inward portion of the
spindle~ An annular hydraulic cylinder is removably
secured to the backing plate and has a generally L-shaped
cross section to provide a first cylindrical surface
thereon adjacent the backing plate whlch has a predeter-
mined diameter. A second cylindrical surface on the
cylinder is remote from the backing plate and concentric
with the Eirst surface and includes a diameter which is
different from the predetermined diameter. An annular
piston has an L-shaped cross section which is oppositely
Griented with respect to the cylinder to be slidably
received therein. A third surface on the piston is
aligned with the first cylindrical surface and a fourth
surface on the piston is aligned with the second
cylindrical surface for respective sealed, sliding
engagement therebetween. The piston and the cylinder
define an operating chamber therebetween. There is
provided means for selectively supplying hydraulic fluid
to and removing it from the operating chamber to
selectively position the piston relative to the cylinder.
A housing is mounted to the backing plate for sealed
encirclement of the hub to define a cvoling fluid
chamber. Non-rotating disc means are mounted relative to
the housing for movement along the axis and rotating disc
means are mounted relative to the hub for movement along
the axis. The di~c means are located within the cooling
fluid chamber and are aligned with each other and between
the housing and the piston for ~rictional contact
~; therebetween for braking the wheel when the piston is
positioned toward the housing.
Brief Description of the Drawin~s
The present invention taken in conjunction with the
invention described in Canadian patent application Serial
No. 309,769 filed 22 August 1978 will be described in
detail hereinbelow with the aid of the accompanying
drawings, in which~
Figure l is a sectional side view o~ the preferred em-
bodiment of the invention as generally seen along the line
1-1 in Figure 2~
Figure 2 is an elevated side view of the embodiment shown
in Figure 1.
DescriPtion of the Preferred Embodiment
As seen in Figures 1 and 2, a friction brake 10 is adapted
to be installed on a spindle 12 of an axle to provide braking
for a wheel 14 which is mounted for rotation about the spindle
12 and an axis 13 thereof. The wheel 14 includes a hub 16 and,
in the preferred embodiment, is of the type which is driven by
a drive axle 18 extending through the spindle 12. ~owever, it
should be clear that the present invention can be employed
just as effectively in a configuration wherein the wheel is
mounted for free rotation about an axle.
The brake 10 is generally of the type which includes a
hydraulic actuating means which is clesigned to apply pressure
to a plurality of disc brakes which are continuously cooled by
a hydraulic cooling system. A first set of the discs is non-
rotatably supported relative to`the axle and a second set of
discs, each of which is disposed between adjacent discs of the
first set, is mounted for rotation with the wheel. When the
operator desires to stop rotation of the wheel, hydraulic oil
is provided to the hydraulic actuating means which, in turn,
applies a force to the plurality of discs creating sufficient
friction therebetween to stop rotation of the wheel about the
axle.
The preferred brake 10 includes a backing plate 20 which
extends generally perpendicular to the axis 13 and is mounted
about an axially inward portion of the spindle 12.
Specifically, in the preferred embodiment, the backing plate
20 is mounted by a plurality of bolts 22 to a flanged portion
24 of the spindle 12. However, it should be clear that a
similar backing plate could be welded to the spindle or
mounted thereon by any other suitable means.
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The backing plate 20 generally provides support for the
remainder of the brake 10 and includes openings therethrough
for hydraulic ac~uating oil and hydraulic oil which is
directed through the brake for cooling of the discs. The
actuating means 26 of the preferred brake 10 includes an
annular cylinder 28 and an annular piston 30 which piston 30
is mounted for movement in an axial direction when the brakes
are applied.
The annular cylinder 28 has a generally L~shaped cross
section and is mounted with its base 32 against the backing
plate 20. The cylinder 2~ is preferably mounted with four
bolts 34 each of which extend through an opening 36 of the
backing plate 20 and include a spring washer 38 which abuts
the surface 40 of the backing plate 20. The significance of
this configuration will be discussed further hereinbelow.
The annular cylinder 28 includes a pair of generally
cylindrical surfaces 42, 44 which are respectively on a foot
portion 43 and a leg portion 45 of the L-shaped cylinder 28 and
are coa~ially aligned with the axis 13. The diameter of the
cylindrical surface 42 is less than the diameter of the
cylindrical surface 40 and, accordingly, the annular cylinder
28 includes a radially extending surface 46 there~etween.
The piston 3Q similarly is annular 2nd includes an L-
shaped cross section having a foot portion 48 and a leg
portion 50. However, the piston 30 is oppositely disposed
from the cylinder 28 so that the foot portion 48 is generally
aligned with and overlies the leg portion 45 of the cylinder
and the leg portion 50 overlies and is generally aligned with
the foot portion 43 of the cylinder. A generally cylindrical
surface 52 of the leg portion 50 has an effective diameter
atching the diameter of the surface 42 and a generally
cylindrical surface 54 of the foot portion 48 has an effective
diameter matching the diameter of the surface 44 o~ the
cylinder. Piston sealing rings 56 are provided between each
of the matching surfaces 52 and 42 and 54 and 46 to insure that
the hydraulic chamber 58 between the cylinder 28 and piston 30
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is effectively sealed. The introduction of hydraulic oil to
the chamber 58 will thus cause the piston 30 to move in a
direction as shown by the arrow A for the introduction of
force to the discs.
As thus described, the generai configuration o~ the
backing plate 20, cylinder 28 and piston 30 are similar to the
configuration shown in United States Patent 3,832,770.
However, significantly, the configuration shown therein
discloses that the cylinder should be integrally orrned as a
portion of the backing plate rather than their being provided
as separate elements~ The configuration of the present
invention has the advantage of providing a separate cylinder-
piston configuration which can be readily tested prior to
installation remote from the spindle to insure its proper
operation. This feat-lre is o~ particular advantage if after
extensive use of the brake it is found that wear of the
cylinder and/or piston requires one or both elements to be
remachined or replaced. Accordingly, repair or replacement of
the actuating means 26 can be accomplished without removal of
the backing plate 20 or any need for its replace~ent due to
failure of another element.
Furthert mounting the cylinder 28 to the backing plate 20
by bolts 34 which include a spring washer 38 allows the
actuating means 26 to operate efficiently even if the backing
plate 20 is subjected to slight distortions or warping during
the operation of the axle. Distortion in the backing plate 20
will not be directly transmitted to the cylinder 28 which
might impair braking efficiency.
The preferred actuating means 26 is also provided another
feature not found in United States Patent 2,832,770 which is
intended to improve its reliability. It is possible because
of the large diameter of the piston-cylinder configuration for
shock, vibration or other outside forces to act on the piston
30 to cause it to become cocked within the cylinder 28 so that
it is no longer axially aligned with the axis 130 If the
generally`mating cylindrical surfaces of the piston and the
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cylinder are provided with minimum clearance therebetween, it
would be possible for the piston to become jammed within the
cylinder, possibly impairing actuation. Therefore, the
surfaces 52 and 54 of the annular piston 30, while having been
previously described as generally cylindrical to match the
adjacent surfaces of the cylinder 2~3, are in fact provided
with a cross section which is slightly curved away from the
adjacent surfaces of the cylinder 28 at opposite sides of each
of the piston sealing rings 56. The surfaces S2 and 54 thus
provide sufficient clearance between the piston 30 and the
cylinder 28 to insure proper movement of the oiston 30 by the
introduction of hydraulic fluid through the fitting 60 to the
chamber 58 since there would be no binding between the piston
30 and the cylinder 28. In other words, the primary "contact"
between the piston 30 and Ihe cylinder 28 will remain at the
sealing rings 56 throughout operation of the brake 10 even if
some cocking of the piston were to exist prior to actuation of
the bra~e. It should be noted that this feature might also be
employed on piston-cylinder configurations such as those shown
in United States Patents 3,580,369 and 3,584,708.
During initial installation of the brake 10, the backing
plate 20, cylinder 28 and piston 30 are initially assembled
and installed on the spindle 12 as described hereinaboveO To
complete the formation of the bra~e 10, an outer 'nousing 62
and two sets of discs 64 and 66 are initially assembled on the
hub 16. The outer housing 62 is adapted to be bolted by a
plurality of bolts 68 to .the backing ~late 20 for sealed
engagement therewith to gene.rally define a pair of chambers 70
and 72 therebetween which receive hydraulic fluid for cooling
o:E the brake during operation. In the ~referred embodiment,
cooling hydraulics are provided through an opening 73 in the
backing plate 20 to provide the oil to the chamber 72 and cause
il to flow around and through the discs o4 and 66 into the
cl-amber 70. An outlet opening 71 is also provided through the
backing plate 20 to allow the hydraulic oil ot exit from the
chamber 70 to be returned to the hydraulic cooling system ~not
shown) for eventual return to the chamber 72. ~It should be
understood that the brake 10 might include an entirely self-
-~3-
contained hydraulic cooling system which would have no
external components. Movement of the discs would cause
sufficient flow between the chambers 70 and 72 to adequately
cool them to improve their efficiency during braking. To
insure that the brake 10 is effectively sealed and that the
cooling fluid is retained therein in either type of cooling
system, seals 74 and 76 are respectively installed ~etween the
outer housing 62 and the hu~ 16 and between the hub 1& and the
spindle 12.
The plurality of friction discs 64 are disposed about the
hub 16 in general alignment with the actuating means 26 and
include a plurality of grooves 78 therein which mate with the
bolts 68 to allow axial movement thereof but to prevent their
rotation relative to the spindle 1~. The plurality of discs
66 are mounted directly to the hub 16 by having an interior
diameter which is splined to match a splined region 80 of the
hub 16 so that the discs 66 will rotate therewith about the
a~is 13. Adjacent discs from the set of discs 64 and 66 are
separated by a single disc from the other set to provide an
array of alternating discs from each set. While the preferred
embodiment therefore includes a plurality of discs as
described hereinabove, it should be kept in mind that an
e~fective brake can be provided which includes only one
stationary disc and one rotating ~isc which are mounted for
axial movement to produce friction therebetween upon movement
o the actuating means 26.
Accordingly, as mentioned above, during initial
installation the outer housing 62 is generally mounted about
the hub 16 and the individual discs ~4 and 66 are
a]ternatively positioned about the hub 16 prior to
installation of the bolts 68. I~ has been found that this form
of installation is preferred over a form of installation which
might include full assembly of the brake 10 on the spindle 12
prior to mounting of the wheel 14 on the spindle 12 as appears
would be required by the installations shown in United States
Patents 3,580,369 and 3,584,70~ if a backing plate were to be
permanently secured to the spindle. Mounting the wheel 14 on
- 9 -
the spindle 12 with the brake 10 installed would be very
difficult because of trouble which would be encountered when
trying to align the discs 66 with the splined region 80. While
this alignment problem is eliminated by generally mounting the
above mentioned portions of the brake 10 on the hub 16, there
still exists the problem of insuring that the discs ~6, which
will generally hold the other elements in position, will
remain on the splined region 80 as the outer housing 62 is
being brought into contact with the backing plate 20 for final
assembly. Accordingly, a circumferential groove 82 is formed
in the splined region 80 and is adapted to receive a locking
wire 8~ therein after the discs 66 are properly positioned on
the hub 16. The locking wire 84 is simply wrapped about the
hub 16 with its terminal ends twisted together to insure that
it will not be dislodged from the groove 82. The wire 8Ll and
groove 82 have no function other than during inst~llation and
do not affect brake operation after the brake 10 is fully
installed.
To further facilitate installation of the brake 10, one
feature thereof includes the addition of ribs 85 to the
interior of the housing 62. The ribs 85 generally extend
axially toward the backing plate 20 and are located between
the bolts 68. Although the installation instructions would
specify the a~ount of torquing force to be applied to the
bolts 68, it has been found that exceeding these limits could
provide sufficient stress to the housing 62 to warp or deform
it from its desired position relative the backing plate 20.
Therefore, the ribs 85 provide additional resistance to this
type of deflection, even if the recommended limits are
exceeded during instal.lation, to insure that the desired
diMensions are maintained for proper operation of the bra~e
10 .
As thus explained, one forM of the brake 10 could be
provided by simply including the elements described
hereinabove. It would be possible to effectively prevent
rotation of the wheel 1~ about the spindle 12 by the
introducti`on of hydraulic fluid to the actuating means 26.
~3~
-~ --10--
The resulting movement of the piston 30 in the ~irection A
would generate a force between the discs 6a and 66 as they are
enkrapped between the piston 30 and the outer housing 620 The
friction therebetween would be sufficient to stop rotation of
the wheel 14 and would be generally uniform at all portions of
the discs 64 and 66 even if the contact area on the outer
housing 62 were not exactly perpendicular to the axis 13.
Since the preferred piston 30 includes curved surfaces 52 and
54, it would be able to apply proper braking force to the discs
even if slightly tilted to conform to the angle of the contact
area. Relieving the pressure within the actuating means 26
would allow the piston 30 to be repositioned away from the
discs to again allow wheel rotation.
However, in the preferred installation, a s~lf-adjusting
feature is provided in the form of a slack adjuster 86 which
determines the relative spacing of the discs 64 during normal
operation of the wheel 14 prior to ac:tuation of the brake. The
slack adjuster 86 includes, in the preferred embodiment, three
equally circumferentially spaced bolt elements 87 whlch are
mounted to the outer housing 62 and adapted to extend
therethrough into the chamber 72~ Each bolt ~7, only one of
which will be described since they all function in an
identical manner, has an inward portion 88 thereof which has a
uniform and continuous cylindrical surface and receives
thereon a wa5her 90, a spring 92, a spring retainer 94 and a
di,c retainer 96. The washer, spring and spring retainer are
free to move axially along the inward portion 88. However,
the disc retainer 96 is a spring loaded collar device wnich is
adapted for frictional enegagement with the portion 88,
requiring in the preferred embodiment about 100 pounds force
to overcome friction to allow it to slide along the partion
88. The outermost disc 64 includes a peripheral groove 98
therein adapted to partially encircle the portion 88 for
abutting contact with the washer 90. The innermost disc 64 is
35 provided with a groove 100 at its outer periphery which is
adapted to be received within a slot 102 in the disc retainer
96. The combined slot and sroove confisuration insures that
there is s`ufficient engagement between the inner disc 64 and
the disc retainer 96 throughout brake operation; in other
words, to insure that slight radial movement of the disc
relative the disc retainer 96 will not interfere with their
engagement during bra.ke operation. Additionally, the inner
disc 64 is provided sufficient surface area about the disc
retainer 96 to provide adequate contact for the spring
retainer 94 to prevent it from being ansularly displaced
relative to the bolt 87..
Therefore, during operation of the slack adjuster 86
relative position is maintained between the inner and outer
discs 64 by the combined action of the washer 90, spring 92 and
the spring retainer 94 to cause them to be separated until the
inner disc 6'1 makes abutting contact with the inner wall of
the slot 102 of the disc retainer 96. The maxi~u~ Lorce
exerted by the spring 92 is about 50-60 pounds so that there is
insufficient force produced to cause the disc retainer 96 ~o
slide along the portion 88. During brake operation, the
piston 30 will be caused to move toward the discs 64 to make
initial contact with the inward disc 64. The hydraulic
actuating force is quite sufficient to easily overcome the
force cxeated by the spring 92 so that the inner disc 64 is
moved axially within the slot 102 as the spring retainer 94
compresses the spring 92. If no adjustment is required, axial
force will be applied to the brake to generate frictional
force and to prevent rotation of the hub 16. Release of the
brakes will allow the spring 92 to reposition the inner disc
64 within the slot 102 as shown in Figure 1.
However, should there exist sufficient wear to the discs
66 or the discs 64, actuation would begin as described above,
but full contact between the discs would not be possible prior
to the inner disc 64 making contact with the outer wall of the
slot 102. Continued movement of the piston 30 would easily
overcome frictional engagement between the disc retainer 96
and the portion 88 so that the disc retainer 96 would be
axially repositioned at that location which would allow
contact between the discs. Release of the brake would again
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allow the spring to reposition the inner disc 6~ against the
inner wall of the slot 102 preventing it from returning to its
initial position. As a result, the movement of the disc
retainer 96 along the portion 88 will establish the limiting
positions for the inner disc 64 to prevent excessive movement
of the disc during brake operation. Therefore, during normal
operation the maximum movement of the inner disc 64 would be
that distance required to move from one side of the slot 102 to
the other side thereof.
While there has been shown and described hereinabove the
preferred embodiment of the invention, it will now be obvious
to those skilled in the art that changes and modifications may
be made therein without departing from the claimed invention.
