DESCRIPTION
TITLE OF THE INVENTION
FRICTION PLATE TYPE LIMITED SLIP DIFFERENTIAL FOR VEHICLE
FIELD OF THE INVENTION
The invention is termed the "Friction Plate Type Limited Slip
Differential for transmissions of vehicles" as it allows appropriate
distribution of traction force in both driving wheels through limiting
the differential action. Such limitation of the differential action is
required in several conditions, particularly for motor-sports vehicles
and when enhanced traction force is required in driving. For
example, in motor sports vehicles improvements in the stability of
straight-forward driving or in the stability of cornering are often
required as quick start, accelerating, and quick turning often occur
frequently and repeatedly. The enhanced traction force is required
when driving off-roads or getting out of rugged roads.
The invention is called friction plate type Limited Slip
Differential (LSD) where limitation of differential action in vehicles is
created through using the friction resistance which occur between
the friction plates. The device is following structures: front and
rear differential case which support gears and friction plates; 2-side
gears and 4-pinion gears for vehicles with the same size of torque
distribution; case plates which are fixed along the splines of the
differential case; clutch plates constrained to the splines of the side
gear and thus able to rotate exactly same with the side gear; cross-
shaped pinion shaft which supports four pinion gears; cam which
transmits the limited differential torque to clutch plate; and plurality
of coil springs which provides regulated pre-load to generate
friction torque on the friction plates.
DESCRIPTION OF RELEATED ART
In general the differential in transmission for vehicles allows the
smooth driving such as cornering or even driving forward with one
wheel on a flat road while the wheel on the other side on a rugged
road or when the difference occur in the radius of dynamic load
between the tires or friction coefficient on the roads.
However, such differential possesses a number of weaknesses
as~ the following illustrates. If one wheel falls into mud and skids,
then the transmittal of the driving force may not occur, and thus
resulting incapacity to drive. Also, when making quick turns, the
occurrence of load movement in inner wheels can block the
transmitting of driving force thus may result in the decrease of
accelerating tendency of the vehicle. Even on normal road condition,
the stability aspect in straight-forward driving can be decreased
under quick start.
Therefore, the purpose of the invention is to maintain the
stability and acceleration of the forward driving of vehicles when
facing repeated quick start or quick turn and to increase the traction
force of vehicles when driving under rugged roads where skidding
occur frequently due to the falling of wheels on one side by adding
the friction plate type clutch structure onto the differential of
generally-used transmissions allowing appropriate limited in
differential action of vehicles.
The existing friction plate type limited differential used the dish
spring as a mechanism to apply pre-load to the friction plates. The
application of dish-spring is advantageous under a small space
where spatial limitation is accompanied. However, as seen in Fig.
10 regarding an example of unique characteristics of dish spring
curve, the dish spring posses a number of problems such as the
occurrence of instability in friction characteristic or decrease in
differential limitation effect due to abrasion of friction plates in
accordance to duration of use due to non-linear relationship in the
applying force according to displacement requiring regular
readjustment of friction plate clearance. Another weakness would
be the difficult in achieving the appropriate spring constant
adjustment in accordance to the usage of vehicles.
This invention has solved the above mentioned problems in the
following skills were applied: First, for setting-up differential torque
and to realize delicate adjustment of torque, the structure to apply
plurality of coil springs were installed instead of the dish spring.
Plurality of coil springs are characterized by the displacement
to change linearly in according to the spring force. Second, for
setting-up the initial torque in according to the vehicle usage, the
structure was invented to control the number of springs or to allow
installation of plurality of springs with different spring constant.
Third, for stabilized friction characteristics of friction plates and
optimization of friction coefficent, the shape of lubricant groove of
the friction plate was invented.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is an exploded perspective view for illustrating limited
slip differential;
FIG. 2 is a sectional view for illustrating installed shape of
limited slip differential in transmission;
FIG. 3 is a plan view of the limited slip differential;
FIG. 4 is a sectional view taken along line C-C of FIG. 3;
FIG. 5 is a sectional view taken along line D-D of FIG. 4;
FIG. 4 is a front view for illustrating applying forces to groove
of cam;
FIG. 7 is a plane view of case plate and shape of lubrication
groove;
FIG. 8 is a plane view of clutch plate and shape of
lubrication groove;
FIG. 9 is a perspective view of rear case for illustrating shape
of case spline and holes for installing the coil springs;
• FIG. 10 is a "graph for illustrating dish characteristics, the
prior art;
1 : front case;
1 a : front case spline;
1 b : holes of front case for installing coil springs;
2 : rear case;
2a : rear case spline;
2b : holes of rear case for installing coil springs;
3 : case plate;
3a : protrusion of case plate;
3b : lubricant groove of case plate;
4 : clutch plate;
4a : protrusion of clutch plate;
4b : lubricant groove of clutch plate;
5 : coil spring;
6 : side gear;
6a : external spline of side gear;
6b : internal spline of side gear;
7 : front cam;
8 : rear cam;
8a : protrusion of cam;
9 : pinion gear;
10 : pinion shaft;
1 1 : spacer;
12 : speedometer drive gear;
13 : bearing ;
14 : bolt;
15 : limited slip differential assembly;
16 : differential drive gear;
17 : transmission case;
18 : drive shaft;
19 : cam groove;
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
features of the present invention will become apparent to
those skilled in the art upon consideration of the following detailed
description of the invention. The detailed description particularly
refer to the accompanying figures.
Fig. 2 shows the installed condition of limited slip differential
in the transmission of vehicle.
• This invention, as seen on Fig. 1 and Fig 3, is comprised of
case, clutch packs, differential and springs.
Gears, plates and coil springs can be built inside the cases (1 )
(2), and for the ease of assembly, the cases are made as a front-&-
rear separation types. This means the cases are comprised of the
Front Cased ) and the Rear Case(2), and the Front Cased ) and the
Rear Case(2) are connected through the Bolts. Both ends of the
above mentioned cases (1 ),(2) are being supported by transmission
case (17) through bearing (13), and as in the case of prior art, they
are also connected to the differential drive gear(16) which is driven
by the engine and transmit driving force to the vehicle wheels
through drive shaft(18).
Clutch packs are comprised of the Case Plates(3) and the
Clutch Plates(4). The Case Plates(3), a number of protrusions(3) are
formed in external circumference of plate and is constrained at the
cases (1 ), (2) along the internal spline (1 a), (2a) of the case. The
Clutch Plate(4) is located in-between the Case Plate(3). The Clutch
Plate(4), a number of protrusions(4a) are formed in internal
circumference of plate, and are constrained along the external
spline(δa) of the side gear; they transmit the torque which acts on
the side gear. Clutch packs, Multiple Case PlatesO) and the Clutch
Plates(4), are symmetrically placed at both ends in between CAM
(7), (8) and cased ) (2) datum for the center line of the pinion
shaft(10). As the friction between the Case Plate(3) and the Clutch
Plate(4) characteristically directly effect the differential limiting
capability, in order to provide sufficient lubrication to stabilize the
friction characteristics and friction coefficent change lubricant
groove (3b), (4b) have been set-up on both sides of the Case
Plate(3) and the Clutch Plate(4) as shown on Fig. 8. The lubricant
groove(3a), which is placed through optional degree for even
distribution of the circumference from the center of the plate at both
sides of the Case Plate(3), is constrained onto cases (1 ),(2) and is
designed to maximize the lubrication under the rotating condition.
On the Clutch Plate(4), there is the spiral Lubricant groove(4b),
which is centered eccentrically in an optional distance from the
center of the plate, is constrained on the Side Gear(6) and is
designed to maximize the inflow and outflow of lubricant under the
rotating condition. The structure considered to maintain the stable
lubricating layer to prevent plate seizing and to stabilize friction
characteristics.
The differential of the limited slip differential is -comprised of a
couple of Side Gears(6), four Pinion Gears(9), cross-shaped Pinion
Shaft(10), which supports four Pinion Gears(9), and Front CAM(7)
and Rear CAM(8), which support the Pinion Shaft(10). The internal
spline(6b) of the Side Gear is connected with the Drive Shaft(18) to
transmit the driving force to the wheels of vehicle. There are
Spacers(1 1 ) at the both ends of Side Gear(6) supporting cases
(1 ),(2). The Pinion Gears(9), which are installed at each level of
cross-shaped Pinion Shaft(I O), rotate datum for the Pinion Shaft(I O)
and are geared with the Side Gear(6) to rotate around the Side
Gear(6). Also, the Pinion Gear(9) was optionally designed in a
four pinion structure for minimizing the size and maximizing torque
capacity which allows ease of application without any changes
within the open differential of the vehicle. As shown on Fig. 6, the
Front CAM(7) and the Rear CAM(8) are structured in a symmetrical
formation and are constrained to Case spline(1 a),(2a) to support the
rotation of the Pinion Gear(6) and the Pinion Shaft(10) by forming a
similar shape of protrusions (8a) as the Case Plate in external
circumference. Four grooves (19) are formed to support the Pinion
Shaftd O) on the cylinder of CAM(7),(8). The formation of CAM
grooved 9) is structured in such a way that when ttie vehicle
speeds-up, the Pinion Shaft(10) moves along the incline of CAM
grooved 0) and differential action is restricted as the clearance
between the Front CAM(7) and the Rear CAM(8) gets bigger while
the Case Plate(3) and the Clutch Plate(4) are pressed to each other.
However, when the vehicle slows-down, the CAM grooved 9) is
structured to restrict the movement of the Pinion Shaft to allow
differential action.
The spring, which is comprised of plurality of Coil Springs(5),
are set-up on the holes (1 b), (2b) of case and are able to generate
differential limiting torque through applying pre-load on the Case
Plates(30) and the Clutch Plates(4). The springs are structured to
easily adjust the differential limiting torque by decrease the number
of the Coil Spring(5) or to optionally select springs with different
spring constant in accordance to the purpose of vehicle usage.
The operating principles of this invention, limited slip
differential, is as follows:
If different sizes of reaction force act onto the right and the
left driving wheels due to the road condition or the spinning action
and the differences in torque are generated at both of the Side
Gears(6), the torque is transmitted to the Pinion Gears(9) which is
geared with both of the Side Gears(6), the Pinion Gears(9) and the
Pinion Shaft(10) are rotated around the Side Gear(6) datum for the
rotatiing axis of the Side gears(6). As Shown on Fig. 6, reaction
force(Fn) is generated on the inclined plane of the Front CAM(7) and
the Rear CAM(8) in an vertical direction with the inclined plane,
which is connected to the Pinion Shaft through the inclined plane at
the CAM grooved 9). The reaction force (Fn) at the inclined plane
is divided into circumferential direction force (Fr) and axial direction
force (Fx). Circumferential direction force(Fr) tries to rotate the CAM
(7), (8), but the it is constrained to the Rear Case spline(2a), and
thus not allowed for rotation. Axial direction force (Fx) operates
CAM(7),(8) in the direction to pressing the Case Plate(3) and the
Clutch Plate(4) along the Case spline.
When the Front CAM(7) and the Rear CAM(8) overcomes the
pre-load from the Coil Spring(5) and move along the Case
spline(1 a),(2a), the clearance between the two CAMs (7), (8) gets
bigger and press the Case Plate(3) and the Clutch Plate(4). When
the Case Plates(3) and the Clutch Plates(4) are pressed by the
CAMs (7), (8), the torsional friction is generated due to the relative
movement between the Case Plates(3), which is constrained to the
Case spline(1 a),(2a), and the Clutch Plates, which tends to rotate by
the torque of the Side Gear(6). At this moment, if the size of torque,
which is generated by the torsional friction between the Case
Plates(3) and the Clutch Plates(4), is bigger than the torque acting
upon the Side Gear(6), the differential action is restricted; whereas if
the size of torque acting upon the Side Gear(6) gradually increases
and becomes bigger than the torsional friction, then the differential
action begins to be generated finally.
Therefore, if the size of differential torque, i.e. the torque
difference generated on the both driving wheels, is smaller than the
differential limiting torque, then there will be no relative movement
between the Case Plates(3) and the Clutch Plates(4), the internal
parts rotate together with the cases (1 ),(2) and the same size of
driving force is transmitted to the both of the wheels. If torque
difference of both of the wheels gradually increase and become
bigger than the torsional friction, the relative movement is generated
between the Case Plates(3) and the Clutch Plates(4), and finally the
differential action is allowed. Hence, the differential limiting torque
is determined by the size of pre-load of the Coil Springs(5> and the
torsional friction of the Case Plates(3) and the Clutch Plates(4)
through the pressing by two CAMs (7), (8).
Vehicles should be able to fully utilize the driving force through
the appropriate differential limitation to get out of driving conditions
such as rugged roads. At the same time, under conditions such as
cornering and general driving, the differential action should be
allowed for smooth driving. This means that the size of differential
limiting torque needs to be changed according to the purpose of
vehicle usage or the driving condition. Therefore, determining the
size of differential limiting torque of the limited slip differential
becomes significant.
This invention, friction plate type limited slip differential, is
able to fully utilize the driving force of vehicles while at the same
time allowing smooth differential action. It has limited change in
differential limiting torque in accordance to duration of the use and it
allow easiness in adjusting differential limiting torque fitting with the
usage purpose of the vehicle without any internal structural change
since it is able to either control the number of Springs(5) or adapt to
the different spring constant optionally. As shown on Fig. 7 and Fig.
8, it also has other unique characteristics such as preventing seizing
due to smooth lubricating action and has lubricant groove
formation(3b),(4b) on surface of the Case Plate(3) and the Clutch
Plate(4) to secure friction characteristics and to maintain friction
coefficent.
REPRESENTATIVE DRAWING
FIG. 1
INDEX
friction plate, limited slip differential, LSD, differential, side
gear, pinion gear, pinion shaft, cam, case plate, clutch plate, coil
spring