FORCE REDUCING PEDAL AND LINKAGE
This invention relates to a control pedal and a control linkage for a vehicle.
GB-A-2322836 describes pedals which are designed to deform so that in an accident,
if a driver's foot comes into contact with the pedal, the driver's foot is not injured.
US 4005617 describes a pedal arm which comprises upper and lower members
hingedly coupled together to permit additional movement of the lower member
relative to the upper member, although the purpose of the additional movement is to
provide reduced braking during the initial phase of the braking.
According to the invention there is provided a control pedal, for a vehicle such as a
brake pedal comprising an upper member and a lower member, which are hingedly
coupled together and in combination form an arm of the pedal, and a foot plate located
at a first end of the arm, the distal end of the arm being arranged for pivotal mounting
on a vehicle and the hinged coupling between the two members permitting additional
movement of the lower member relative to the upper member in the operating
direction of the pedal, the pedal further including biasing means arranged to prevent
additional movement until the force applied to the foot pedal exceeds a predetermined
force threshold, characterised in that the lower member comes into contact with a
fixed part of the vehicle body after the additional movement and the additional
movement requires a force applied to the foot pedal against the biasing means which
is different from that applied to the foot pedal prior to exceeding the predetermined
force threshold.
According to a second aspect of the invention there is provided a control linkage for
coupling a vehicle control pedal such as a brake pedal to a vehicle mechanism such
as a brake servo, comprising pedal fixing means for coupling to a vehicle pedal,
mechanism fixing means for coupling to a vehicle mechanism to be controlled, and
biasing means arranged to bias the pedal fixing means and mechanism fixing means
into a first position, the linkage is arranged to move towards a second position in
which the pedal fixing means and mechanism fixing means are closer together than
in the first position when a force is applied between the pedal fixing means and
mechanism fixing means which exceeds a predetermined threshold, characterised in
that the movement towards the second position requires a different force for
displacement against the bias between the pedal fixing means and the mechanism
fixing means to be applied which is different from that force required before
exceeding the pre-determined threshold.
According to a third aspect of the invention there is provided a control mechanism,
comprising the combination of a foot pedal and a control linkage for coupling to a
vehicle mechanism such as a brake servo and for applying a force to the vehicle
mechanism, characterised in that the combination is arranged to deform in use when
a force is applied in the operating direction which exceeds a predetermined threshold,
o so that the force required to be applied to the foot pedal to operate the vehicle
mechanism prior to deformation is different from the force required to provide further
operation of the vehicle mechanism after deformation whereby the force applied to the
vehicle mechanism is limited to a predetermined maximum applied force.
Embodiments of pedals in accordance with the invention will now be described by
way of example with reference to the drawings in which:
Figure 1 is a perspective view of a known pedal;
Figure 2 is a schematic side elevation of a pedal in accordance with the invention;
Figure 3 is a graph showing force on the foot plate of the pedal illustrated in Figure
2 against pedal deformation;
Figure 4 is a graph showing force on the foot plate of the pedal illustrated in Figure
2 against force on the upper arm of that pedal:
Figure 5 is a schematic side elevation of a buffer in accordance with the invention;
Figure 6 is a schematic side elevation of an alternative pedal in accordance with the
invention;
1/38151
Figure 7 is a schematic cross section through a linkage in accordance with the
invention;
Figure 8 is a schematic cross section through a brake servo mechanism incorporating
the linkage illustrated in Figure 7;
Figure 9 is a schematic cross section through a modified linkage in accordance with
the invention;
Figure 10 is a graph showing force on the foot plate of a pedal connected to the
linkage illustrated in Figure 9;
Figure 11 is a schematic perspective view of a linkage in accordance with the
invention;
Figure 12 is a schematic cross section of the linkage illustrated in Figure 11 ; and
Figure 13 is an exploded view of a pedal, servo mechanism and the linkage illustrated
in Figure 11.
The known pedal illustrated in Figure 1 has a pivot tube 1 located at one end of a main
arm 2. At the other end of the main arm 2 is a foot plate 3. The pedal is mounted to
a vehicle by the pivot tube 1 and is caused to move about the pivot tube 1 by force
applied to the foot plate 3. A control linkage 5 is pivotally mounted at point 4 partwa}
along the main arm 2. Force applied to the foot plate 3 is multiplied
the lever
arrangement formed by the main arm 2 and the relative locations of the pi\ ot point 4
and pivot tube 1. and is transmitted to a mechanism to be controlled such as a brake
servo or clutch mechanism via the control linkage 5.
In an emergency . a driver may apply a force of the order of 250 deca-newtons to the
foot plate 3. This after multiplication by the lever arrangement, may cause a force of
the order of a 1000 deca-newtons to be applied to the vehicle brake servo. However,
the effort which is required for full operation of the brakes is typically of the order of
18 deca-newtons at the foot plate. Pressure applied at higher levels than this usually
results in the operation of an ABS system or in skidding of one or more wheels of the
vehicle.
Although the high forces generated by the lever system under emergency have no use.
it is necessary to design the braking system and the pedal system to withstand such
high forces. This has implications for the construction of the pedal and braking
system. Plastic materials are not generally used as brake pedals as softer plastic
materials will deform over time from repeated use. Harder plastics may be too brittle
over the full temperature range of the vehicle and so suffer catastrophic fracture with
a resultant loss of brakins function.
The invention described below allows a pedal to be used which is made of a material
other than metal (plastics for example) and thus allows the pedal to be lighter and
cheaper to manufacture. A suitable pedal may be based on the pedal described in our
co-pending application GB-A-232551 1.
With reference to Figure 2, a pedal is shown which limits the maximum force
transmitted to a vehicle control system such as the brake or clutch system. This allows
the size and therefore cost, of the braking or clutch system to be reduced.
Furthermore, foot pedals made from plastic materials may also be used. The
maximum force is limited to ensure failure of the pedal does not occur due to the
vehicle operating too far below the glass transition temperature of the plastic material
and so fracturing in use.
The general principle is to direct two different levels of force to different parts of the
vehicle. Part of the force is directed to the mechanism to be controlled and the surplus
force is directed to the body of the vehicle.
With reference to Figure 2, an upper pedal arm 6 is rotatably connected to the vehicle
body about point 7. The upper arm 6 also includes a hinge point 8 for the connection
of a control linkage to transmit force to a mechanism such as a brake servo.
A lower arm 9 has a foot plate 10 which is formed at the lower part of the lower arm
9. The lower arm 9 is hingedly connected to the upper arm 6 by an axle 1 1. A further
connection between the upper and lower arms 6 and 9 is made by co-operating hooks
13 and 12 on the upper and lower arms respectively.
The hooks 12 and 13 permit rotation of the lower arm 9 about the axle 1 1 generally
in the direction A. They prevent such rotation in the opposite direction.
A compression spring 14 is located on lugs 15 and 16 formed respectively on the
upper and lower arms 6 and 9. The compression spring acts against the hooks 12 and
13 and acts to rotate the lower arm 9 in the opposite direction to arrow A.
The compression spring 14 is precompressed so that the upper and lower arms 6 and
9 are held generally in the position shown in Figure 2 until a force is applied to the
foot plate 10 which overcomes the precompression of the spring 14. Thus until the
precompression of the spring 14 is overcome, the pedal acts in a generally
conventional way and transmits effort applied to the foot plate 10 to a control linkage
connected to the pivot point 8.
When excess force is applied to the foot plate 10, the lower arm 9 is allowed to pivot
about axle 1 1 and eventually comes into contact with a part of the vehicle body 17.
The effect of this is shown in the graph of Figure 3. At point A, no effort is applied
to the foot plate 10. Along the line A to B, increasing force is applied to the foot plate
but no deformation of the pedal occurs. This situation is shown in Figure 2 where all
force applied to the foot plate 10 is applied to the mechanism of the vehicle which is
being controlled.
At point B, the force applied to the foot plate 10 is just enough to overcome the
precompression of the spring 14. This is preferably adjusted to occur at a point where
all the force necessary to operate the vehicle mechanism has already been applied via
the pivot point 8. Thus the pedal is allowed to deform by compression of the spring
14. At point C, the lower arm 9 comes into contact with the part of the vehicle 17 and
the deformation of the pedal ceases. All further force applied to the foot plate 10 is
transmitted to the vehicle body at 17.
Figure 4 shows the force transmitted by the pedal against the force applied to the foot
plate 10. The reference letters used are the same as those used in Figure 3. Thus it will
be seen that beyond point C (at which point the lower arm 9 is in contact with the
vehicle body at 17) no additional force is transmitted to the vehicle mechanism.
In order to adjust the maximum force transmitted to the vehicle mechanism, the point
at which the lower arm 9 comes into contact with the vehicle body at 17 may be
adjusted, for example, by providing an adjustable buffer of the form shown in Figure
5. By adjusting the height of the buffer, the point at which the pedal comes into
contact with the buffer may be adjusted which has the effect of adjusting the position
of point C in graph 4. The buffer may include side wings 17 and 18 which serve to
centralise the pedal laterally.
It will be appreciated that the compression spring 14 may be replaced by any generally
resilient compressible material or biasing means. Typical examples are a leaf spring,
a gas spring, a torsion spring, a tension spring, a torsion bar or elastomeric washers.
Figure 6 shows an alternative arrangement for the pedal in which a tension spring 20
is used. In this case, it is not necessary to have inter-engaging hooks 12 and 13 since
the spring does not need to be held in compression. Instead, the spring is pretensioned
and is held in this state by abutting surfaces 22 and 24 on the upper and lower arms
6 and 9 respectively.
With reference to Figure 7, a force reducing effect may instead be achieved using a
generally conventional pedal 50 having a foot plate 52 which pivots on the vehicle
body at pivot point 54. The leverage provided by the pedal 50 is applied to a brake
servo 56 via a control linkage 58.
The control linkage 58 is operable to transmit force from the pedal 50 to the servo 56
until a predetermined maximum force is reached at which point the distance between
the pedal fixing point 60 and the servo fixing point 62 at the distal end of the linkage
58 begins to reduce. This allows the pedal 50 to come into contact with a part of the
vehicle 17 as described above.
In order to achieve this effect, the control linkag 58 has an outer member 64 which
carries the servo fixing means 62 and an inner member 66 slidably mounted within the
outer member 64. The inner member 66 carries the pedal fixing means 60. A wall 68
formed across the inside of the outer member 64 provides an end stop and locating
lugs 70 for a compression coil spring 72. The other end of the coil spring 72 acts on
the inner member 66 to bias the inner member 66 away from the servo fixing point 62.
The inner member 66 is held within the outer member 64 by formations 74. Thus the
coil spring 72 is held under precompression.
When a force is applied to the foot plate 52 of the pedal 50 which (after taking
account of the lever ratios of the pedal ) is sufficient to overcome the precompression
of the coil spring 72. the inner member 66 begins to telescope into the outer member
64. This corresponds to point B on the graph of Figure 3. Thereafter, force continues
to be transmitted to the servo 56 and at the same time, the pedal moves towards the
part of the vehicle 17. At point C. the pedal 50 comes into contact with the part of the
vehicle 17 and no additional force is transmitted to the brake servo 56.
Figure 8 shows a modification in which the servo fixing means 62 is dispensed with
and instead the linkage 58 forms an integral part of the servo mechanism 56.
With reference again to Figure 4, it is noted that at point B, the maximum force
necessary to operate the brake servo is applied. However, additional force is applied
to the brake servo until the pedal reaches the part of the vehicle 17. In order to reduce
this additional, unnecessary force, a modified linkage 58 may be used as shown in
Figure 9. This includes a damper arrangement 80 coupled effectively in series with
the compression spring 72. The effect of this damper 80 is shown in the graph of
Figure 10. It will be seen that the additional force transmitted between the point B at
which the spring 72 begins to compress and the point C at which the pedal 50 reaches
the part of the vehicle 17, is much reduced. This provides dual-rate resistance to pedal
movement and allows further cost savings to be made in the manufacture of the brake
servo and braking system. The damper arrangement 80 could be replaced by another
spring or other biassing means.
Figure 1 1 shows one form of the linkage 58. A typical cross-section is shown in
Figure 12.
Figures 13 shows the linkage 58 of Figure 13 in an exploded view ready for assembly
to a pedal 50 and a brake servo 56.