TORSION DAMPER
FIELD OF THE INVENTION
This invention relates generally to transmission systems and, more
particularly, relates to a torsion damper for use in a torque transmission system
BACKGROUND OF THE INVENTION
Torsion dampers of the type under consideration are used in torque
transmission systems for tuning output torque fluctuations of an engine Current
torsion dampers are typically constructed to include a drive plate, a retaining plate,
and a driven plate The retaining plate is rigidly connected to the dπve plate
which, in turn, is connected to a flywheel associated with the vehicle engine The
flywheel functions to cause the retaining plate and the drive plate to rotate
together The driven plate, mounted between the retaining plate and the drive
plate, is connected to a vehicle dπvetrain A first drive assembly lies between the
drive plate and the driven plate and a second dπve assembly lies between the
retaining plate and the driven plate for use in fπctionally transmitting the engine
torque from the drive and retaining plates to the driven plate During moments of
engine torque fluctuations, slippage may occur between the drive and retaining
plates and the dπve assemblies, and, therefore, the driven plate, which results in
the compression of springs mounted between the dπve and retaining plates and
the driven plate The spπngs function to tune the noted torque fluctuations
TJ S Patent No 4,626,226 entitled "Torque Fluctuation Damper" to
Kajikawa et al , which issued on December 2, 1986, for example, discloses a
torsion damper having a first dπve assembly comprising two friction plates and a
second drive assembly comprising a friction plate and a disc spring The first
drive assembly makes frictional contact with the drive plate and with an
intermediate plate in positive engagement with the dπven plate while the second
dπve plate makes frictional engagement with both the retaining plate and the
driven plate By way of further example, U S Patent No 5,558,579 entitled
"Torsional Damper Having A Resiliency Coupled Damper Element And A
Fπction Generating Device Mounted Within A Padded Window Of The Damper
Element" to Tsuchiya et al , which issued on September 24, 1996, discloses the
use of frictional blocks which function as the first and second drive elements
Unfortunately, while these examples of torsion dampers work for their
intended purpose, they are relatively costly to manufacture and repair owing to the
numerous different parts required in their construction and their complex
arrangement Furthermore, the use of numerous components which are subjected
to frictional forces also tends to undesirably decrease the relative durability of
these devices Another disadvantage is that the relatively small fπctional surfaces
associated with the frictional blocks, when used in the construction of torsion
dampers, undesirably tends to make the torsion dampers less consistent in their
operation
SUMMARY OF THE INVENTION
From the foregoing, it is evident that a need exists in the art for a torsion
damper which overcomes the deficiencies above-noted Accordingly, the present
invention is directed to an improved torsion damper which generally includes a
dπve plate connected to and rotated by the engine, a retaining plate connected to
and simultaneously rotated with the drive plate, and a driven plate mounted
between the drive plate and the retaining plate and angularly displaceable with
respect to the drive plate and the retaining plate. The dπve plate is connected to
the dπvetrain A first friction plate is provided between the drive plate and the
driven plate and a second friction plate is provided between the retaining plate
and the driven plate The first and second friction plates are identical in
construction and include an enlarged frictional surface and a plurality of laterally
extending flanges. The enlarged frictional surfaces allow the friction plates to be
fπctionally driven by the dπve and retaining plates, respectively, and the flanges,
which engage corresponding windows in the driven plate, allow the fπction plates
to mechanically dπve the dπven plate First and second identical biasing springs
are associated with each of the friction plates for enhancing the frictional
engagement. An energy storage element is operatively disposed between_the
dπve and retaining plates and the driven plate for tuning the output torque
fluctuations when a slip occurs in the frictional engagement
In this manner, as will become apparent from the descπption that follows,
the present invention has, among other advantages, the advantages of providing a
torsion damper which, minimizes the number of parts which must be specifically
manufactured for use in its construction resulting in a device which is relatively
less costly to manufacture, includes components which are especially adapted for
ease in construction and/or removal resulting in a device which is relatively easier
and less costly to manufacture and/or repair; reduces the number of components
which are subjected to frictional wear resulting in a device which is relatively
more durable, includes components which are configured to enhance frictional
engagement resulting in a device which is relatively more reliable in its operation,
and minimizes the losses in the rotational power transmitted between the vehicle
engine and the dπvetrain by providing a torsion damper which is more accurately
designed to respond to a predetermined amount of torque fluctuations
A better understanding of the objects, advantages, features, properties and
relationships of the invention will be obtained from the following detailed
descπption and the accompanying drawings which set forth illustrative
embodiments and which are indicative of the various ways in which the principles
of the invention may be employed
BRIEF DESCRIPTION OF THE DRAWINGS
For a better understanding of the invention, reference may be made to
preferred embodiments shown in the following drawings in which
Figure 1 is a front elevational view of a first embodiment of a torsion
damper constructed in accordance with the present invention,
Figure 2 is a cross-sectional, side elevational view of the torsion damper
taken along line 2-2 of Fig 1,
Figure 3 is an exploded, isometric v ew of the torsion damper of Fig 1,
Figure 4 is a close up, partially cut away view of an area of the torsion
damper of Fig 1,
Figure 5 is a front elevational view of a second embodiment of a torsion
damper constructed in accordance with the present invention, and
Figure 6 is a cross sectional view of the torsion damper of taken along line
6-6 of Figure 5.
DETAILED DESCRIPTION
Referring now to the figures, wherein like reference numerals refer to like
elements, there is illustrated in Figs. 1-4 a first embodiment of a torsion damper
10 constructed in accordance with the present invention. As discussed, the
torsion damper 10 is adapted to be disposed between an engine and a drivetrain of
a vehicle (not shown) for the purpose of allowing the torque generated by the
engine to be transmitted to the drivetrain while tuning output torque fluctuations.
Generally, the torsion damper 10 includes a substantially planar drive plate 12
which is adapted to be connected to and rotated by the engine, a substantially
planar retaining plate 14 which is rigidly and coaxially connected to the drive
plate 12 for simultaneous rotation with the drive plate 12, and a substantially
planar driven plate 16 which is coaxially mounted between the drive plate 12 and
the retaining plate 14 and which is adapted to be connected to the vehicle
drivetrain. Additionally, the torsion damper 10 includes first and second
substantially planar friction plates 18a, 18b which are coaxially disposed between
the drive plate 12 and the driven plate 16 and the retaining plate 14 and the driven
plate 16, respectively. During the operation of the torsion damper 10, which will
be described in greater detail hereinafter, the friction plates 18a, 18b are used to
transmit the rotation imposed upon the drive plate 12, and, therefore, the retaining
plate 14, to the driven plate 16.
The dπve plate 12 may be rotated by a flywheel associated with the
engine. More specifically, in the illustrated embodiments of the invention, the
drive plate 12 is attached to the flywheel utilizing fasteners (not shown) which are
sized to engage a first plurality of apertures 22 disposed around the periphery of
the drive plate 12. The drive plate 12 further includes a second plurality of
apertures 24, disposed within the circumference created by the first plurality of
apertures 22, which are arranged to align with a plurality of apertures 26 disposed
around the periphery of the retaining plate 14. A like number of fasteners 28,
such as bolts or the like, are passed through the apertures 24, 26 for coupling the
drive plate 12 and the retaining plate 14 Additionally, a plurality of spacers 30,
through which the fasteners 28 pass, are disposed between the drive plate 12 and
the retaining plate 14. In this manner, the spaced attachment of the drive plate 12
and the retaining plate 14 serves as a housing to enclose various other
components of the torsion damper 10.
The driven plate 16, which is disposed between the drive plate 12 and the
retaining plate 14, includes a centrally formed, splined hub portion 32 for splined
connection to the vehicle drivetrain. As illustrated in Figs. 2 and 3, the hub
portion 32 is sized and arranged to pass through centrally disposed apertures 34,
36 in the drive plate 12 and the retaining plate 14, respectively. A pair of
retaining rings 38, which are adapted to engage the hub portion 32 to the outer
surfaces of the drive plate 12 and the retaining plate 14, may be used to maintain
the desired arrangement of the components. Additionally, in order to
accommodate the spacers 30, the driven plate 16 has a series of peripheral
recesses 40 which are dimensioned in the direction of rotation of the driven plate
16 to be slightly greater than the diameter of the spacers 30 In this manner, the
dπven plate 16 is angularly displaceable relative to the drive plate 12 and
retaining plate 14 within the limits determined by the opposed edges of the
recesses 40
The drive plate 12 and retaining plate 14 are further formed with a
plurality of generally rectangular shaped windows 42a, 42b which are arranged to
register with a plurality of similarly shaped windows 44 formed in the driven plate
16 Within each of the registered windows 42a, 42b and 44 is disposed an energy
storage element 46, for example, in the form of coil spπngs 48, 50 Positioned
adjacent to each of the windows 42a, 42b is a pair of oppositely disposed,
outwardly extending, generally arcuate shaped flanges 52 The flanges 52
cooperate to form a housing around each of the windows 42a, 42b for retaining
the energy storage element 46 Each energy storage element 46, which is sized
and arranged to abut the opposed edges of the registered windows 42a, 42b and
44, functions to oppose the angular displacement between the drive plate
12/retaιnιng plate 14 and the dπven plate 16 In the illustrated embodiment, by
way of example, at least one of the coil springs 48, 50 is sized and arranged to
abut the opposed edges of the registered windows 42a, 42b and 44
The pair of identical fπction plates 18a, 18b, which are disposed between
the drive and retaining plates 12, 14 and dπven plate 16, are adapted to
fπctionally engage the drive and retaining plates 12, 14 and mechanically engage
the dπven plate 16 More specifically, each of the friction plates 18 has a
frictional surface 54 which functions to provide the frictional engagement with
the inteπor wall of the plate 12, 14 As illustrated in Figs 1 and 2, it is preferred
that at least one of the drive plate 12 and the retaining plate 14 be provided with
slight recesses for accommodating the fπction plate(s) 18 for ease in assembly In
a preferred embodiment of the invention, the frictional surface 54 of each of the
friction plates 18a,18b is provided with an enlarged surface area of at least eleven
square inches which results from the frictional surface 54 having an outer
diameter dl of approximately four and one-half inches (which diameter is
approximately one-third of the approximately fourteen inch outer diameter
provided to the retaining plate 14) and an inner diameter d2 of approximately two
and one-half inches This enlarged, frictional surface area has the advantage of
enhancing the frictional engagement between the friction plates 18a, 18b and the
dπve and retaining plates 12, 14, respectively In other embodiments, the
frictional surface 54 may be dimensioned to provide at least 10 square inches of
frictional surface area
The frictional engagement between the components is further enhanced by
biasing the friction plates 18 into engagement with the appropπate plate 12, 14 by
means of a pair of identical disc springs 56 which are also coaxially aligned with
the drive plate 12 about the hub 32 Each of the spπngs 56 is preferably sized and
arranged between its associated friction plate 18a, 18b and the driven plate 16
such that the outer portion 56a of the springs 56 engages the associated fπction
plate 18 while the inner portion 56b of the spπngs 56 engages the driven plate 16
proximate to the hub 32 during assembly In this manner, a substantially even
pressure is applied to the fπction plates 18a, 18b resulting m a relative increase of
the effective frictional contact between the friction plates 18a, 18b and its
corresponding driving member while minimizing the potential for uneven
fπctional wear during operation
To provide the mechanical engagement between the friction plates 18a,
18b, and the driven plate 16, the friction plates 18a, 18b are further provided with
a plurality of flanges 58 which extend laterally inward from the peπphery of the
fπction plates 18a, 18b The flanges 58 are adapted to engage the windows 44
formed within the dπven plate 16 More specifically, as illustrated in Figs 2 and
4, each of the windows 44 is provided with a radially, inward extending, generally
rectangular extension 44a within which the corresponding flanges 58 of both
friction plates 18a, 18b are accommodated Specifically, the flanges 58 cooperate
with opposed edges of the extensions 44a for providing a means for the friction
plates 18a, 18b to dπve the dπven plate 16 during operation The mechanical
engagement between the friction plates 18a, 18b and the dπven plate 16 also
encloses the spπngs 56 so that the spπngs 56 move with the fπction plates 18a,
18b and the driven plate 16 In this manner, wear which may result from the
relative movement between the fπction plates 18a, 18b, and the spπngs 56 and/or
between the driven plate 16 and the springs 56 during the operation of the device
is minimized
During the operation of the torsion damper 10, the drive plate 12 and
retaining plate 14 fπctionally transmit the output torque of the engine to the
friction plates 18a, 18b which, in turn, mechanically transmit the engine torque to
the driven plate 16 In response to fluctuations in the engine output torque, the
frictional surfaces 54 of the friction plates 18a, 18b will slip over the associated
surfaces of the dπve plate 12 and the retainer plate 14 resulting in the relative
angular displacement between the dπve plate 12 and the retainer plate 14 with
respect to the dπven plate 16 In response to slippage, the energy storage element
46 will undergo compression to tune the engine output torque fluctuations It is to
be noted that the mechanical linkage of the friction plates 18a, 18b to the dπven
plate 16 functions to reduce the number of surfaces which may slip relative to one
another which, in turn, allows the torsion damper 10 to be more accurately
designed to respond to a predetermined amount of torque fluctuation In this
manner, losses in the rotational power transmitted between the vehicle engine and
the drivetrain, which often result when engine torque fluctuation are over-tuned or
under-tuned, may be minimized Additionally, it will be appreciated that the
enlarged surface areas of the friction plates 18a, 18b also function to more
efficiently dissipate the heat generated as a result of this slippage which further
functions to prolong the life of the components of the torsion damper 10
In a further embodiment of the invention, illustrated in Figs 5 and 6, the
components of the torsion damper remain the same except that the hub portion 32'
of the driven ring 16 is adapted for splined engagement with a yoke 70 which is,
m turn, adapted to be connected to a universal joint associated with a remotely
mounted transmission As such, it will be appreciated that the torsion damper 10
may be easily modified for different applications without requiring an extensive
amount of retooling In particular, the hub portion 32' is sized such that an
interior surface 72 of the yoke 70 engages with the exterior surface of the
retaining ring 14. Additionally, a further retaining ring 74 is provided which
engages the yoke 70 and the outer surface of the hub portion 32'. In this manner,
engagement between the retaining ring 74 and the hub portion 32' in cooperation
with the engagement between the yoke 70 and exterior surface of the retaining
plate 14 provides a means to maintain the desired arrangement of the components.
The universal joint is attachable to the yoke 70 by using fasteners which are
adapted to mate with apertures 74 formed in the yoke 70. As the components of
this embodiment of the torsion damper remain relatively unchanged with respect
to the embodiment illustrated in Figs. 1-4, it will be understood that both
illustrated embodiments function the same and, accordingly, the operation of this
embodiment will not be described in greater detail herein.
While specific embodiments of the invention have been described- in
detail, it will be appreciated by those of skill in the art that various modifications
and alternatives to those details could be developed in light of the overall
teachings of the disclosure. Accordingly, the particular arrangements disclosed
are meant to be illustrative only and not limiting as to the scope of the invention
which is to be given the full breadth of the appended claims and any equivalent
thereof.