ant drive for accessories. There is a pis-ton-effect on most pinion designs in
which one end (usually the bottom) must
be large enough for the pinion to be
inserted into the case and the other end is
customarily smaller (illustrated in Figure
3). Pressure in the actuator, acting
against different upper and lower areas,
causes an axial load on the pinion. In this
case, an inverted actuator would have a
greater chance of pinion blowout; if the
actuator is installed conventionally, the
pinion would be secondarily retained by
the valve stem.
This cutaway differs from the Norris
Brothers’ design, which uses rods for
guiding the piston. Almost all rack and
pinion actuators produced since the original design use thrust pads to absorb the
side load on the skirts. Since the faces of
the rack and pinion teeth have slope, a
small component of the force exerted by
the pistons acts to lift the racks off the
pinion. The thrust pad keeps the racks
properly meshed with the pinion. These
thrust pads are commonly molded of an
engineering resin with a large portion of
dry lubricant such as 25% MoS2, which
helps reduce friction. Another notable
difference between the designs is that the
actuator pictured in Figure 2 uses concentric springs while the Norris Brothers
design uses multiple parallel springs.
Releasing the pressure at P2 enables
the springs to push the pistons together,
rotating the pinion clockwise and closing
the valve. Springs are optional—used to
ensure fail-safe operation on loss of air
pressure—and they are selected so the
torque generated during opening, using
supply air pressure at P2, matches the
torque when the springs close the valve.
Without springs, the actuator may be
operated as double-acting by applying
pressure at P1 to close the valve.
The actuator shown in Figure 2 has an
outward travel stop, also called a stop-
bolt, in the right endcap and an inner
travel stop in the left endcap. Other actu-
ator designs may apply the travel stops
against the pinion. There are advantages
and disadvantages to each of the loca-
tions for the stops. The full-travel stops
shown in the endcaps in Figure 2 may be
adjusted to stop the valve at any point in
its travel, in either the opening or closing
direction. These place a load on the cen-
terline of the piston that is transmitted
back through the rack to the pinion,
causing an asymmetric load on the actua-
tor bearings when the assembly rotates
far enough to hit the stop. Stop-bolts can
also be arranged to engage the pinion
directly, by placing them in the side of the
actuator housing where they engage a
shoulder on the pinion gear itself. These
arrangements generally offer adjustabili-
ty over a much shorter range; typically,
on the order of plus or minus 6 degrees
and place significant bending loads on
the stop bolts at the extremes of adjust-
ment. In this arrangement, asymmetrical
loading on the pinion bearings still occurs
when the stop-bolts are engaged, but the
force is not transmitted to the rack(s).
Figure 3: Cutaway of a typical actuator
illustrating the travel stops and pinion design
to be subtracted: a preload multiplied by
a constant and the stroke of the actuator.
The torque curve will be a straight line,
sloping downward.
A typical ball valve requires the highest torque to open from its closed position
due to the process differential pressure
exerted against a closed valve and a “
set-torque” that occurs as the resilient seat
material conforms to small irregularities
in the surface of the ball. As the ball is
opened, the run torque drops to about
60% of the break torque, out to full-open
position. About 80% of the break torque
is required to re-seat the valve. For a fail-
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