U.S. patent number 3,795,233 [Application Number 05/254,852] was granted by the patent office on 1974-03-05 for fuel-air ratio control for supercharged engines.
This patent grant is currently assigned to Caterpillar Tractor Co.. Invention is credited to Donald R. Crews, Larry A. Larson.
United States Patent |
3,795,233 |
Crews , et al. |
March 5, 1974 |
FUEL-AIR RATIO CONTROL FOR SUPERCHARGED ENGINES
Abstract
A fuel-air ratio control device for a super-charged engine
having a governor means connected to a fuel-adjusting member and a
supercharger for supplying air through an intake manifold. The
control device is directly engageable with the fuel-adjusting
member and is responsive to intake manifold air pressure and to
engine oil pressure. The device is inoperative to restrain the
adjusting member during start-up of the engine and remains so until
such time as a predetermined intake manifold pressure is attained
at which time the control device moves to a position which permits
the metering of engine oil therethrough to permit normal governor
operation and proportional increases of fuel with air pressure
increases. The control device is automatically shiftable to a
position which blocks the metering of engine oil therethrough and
which provides a hydraulic lock and positive connection between the
control device and the fuel adjusting member to preclude any
undesired increase of fuel supply.
Inventors: |
Crews; Donald R. (Peoria,
IL), Larson; Larry A. (East Peoria, IL) |
Assignee: |
Caterpillar Tractor Co.
(Peoria, IL)
|
Family
ID: |
22965842 |
Appl.
No.: |
05/254,852 |
Filed: |
May 19, 1972 |
Current U.S.
Class: |
123/383;
123/387 |
Current CPC
Class: |
F02D
1/00 (20130101); F02D 2700/0287 (20130101) |
Current International
Class: |
F02D
1/00 (20060101); F02d 001/06 () |
Field of
Search: |
;123/14MP,14MC |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Goodridge; Laurence M.
Attorney, Agent or Firm: Fryer, Tjensvold, Feix, Phillips
& Lempio
Claims
What is claimed is:
1. In an engine having an intake manifold, a governor-controlled
fuel supply means, said fuel supply means having a control member
means adapted to move in a first direction to increase the supply
of fuel to the engine and in a second direction to decrease the
supply of fuel to the engine, and override means for selectively
overriding said governor to prevent movement of said control member
means in said first direction, said override means comprising; a
piston means slidable within a first chamber means, a portion of
said piston means being capable of directly contacting a portion of
said control member means to prevent movement of said control
member means, diaphragm means movable within a second chamber means
within said override means, first resilient biasing means
physically disposed between said piston means and said diaphragm
means for acting upon and biasing said piston means toward said
first direction and for acting upon and biasing said diaphragm
means toward said second direction, means for supplying fluid
pressure to said first chamber means to move said piston means
toward said second direction against the bias of said first
resilient means, valve passage means in said piston means for
selectively draining off said fluid pressure from said first
chamber to allow said piston means to move in said first direction,
valve spool means connected to said diaphragm means for selectively
opening and closing said valve passage means, means for
communicating said intake manifold to said second chamber means to
supply intake manifold pressure thereto to move said diaphragm
means and said valve spool means toward said first direction in
opposition to said first resilient biasing means, second resilient
means separate from said first resilient means for acting upon said
diaphragm means and biasing said diaphragm means and said valve
spool means toward said first direction, and third resilient means
separate from said first and second resilient means for biasing
said diaphragm means and said valve spool means in said second
direction.
2. The override means of claim 1 wherein the biasing force exerted
upon said diaphragm means by said second resilient means is
substantially balanced by the opposing forces exerted upon said
diaphragm means by said first and third resilient biasing
means.
3. The override means of claim 1 wherein fourth resilient biasing
means are provided for biasing said diaphragm means toward said
second direction.
4. The override means of claim 3 wherein said first, third and
fourth resilient biasing means act in series upon said diaphragm
means in opposition to the biasing forces exerted upon said
diaphragm means by said second resilient biasing means and said
intake manifold pressure extant in said second chamber means.
5. A fuel-air ratio control device for an engine having a
governor-controlled, fuel-adjusting member means and a supercharger
to supply air through an intake manifold to the engine comprising;
resilient means responsive to intake manifold air pressure, valve
means for interacting with said resilient means and for movement
responsive to engine lubrication fluid pressure toward and away
from said resilient means during normal governor-controlled engine
operation, said valve means being selectively engageable in
interfering relation with said fuel-adjusting member means for
constraining movement of said fuel-adjusting member means upon a
reduction in manifold air pressure but for disposition in
non-interfering relation with said fuel-adjusting member means
during cranking of the engine so that sufficient fuel is supplied
to said engine upon starting in accordance with requirements set by
the governor, said valve means also being effective subsequent to
start-up for interfering with said fuel-adjusting member means to
assure optimum fuel-air ratio for said engine and to prevent
overfueling during periods of reduced pressure in said intake
manifold, said resilient means comprises a diaphragm means of
resilient flexible material and a plurality of separate spring
means arranged on opposite sides of said diaphragm means in
normally-balanced relationship to said diaphragm means and
selectively acting to hold said valve means in said non-interfering
position with respect to said fuel-adjusting member means.
6. The control device of claim 5 wherein said valve means includes
a piston means, a valve spool means connected to said diaphragm
means, said valve spool means and said piston means being in a
non-interfering relation with said fuel-adjusting member means
until said valve spool means is moved in a first direction, chamber
means for receiving engine lubrication fluid under pressure to urge
said piston in a second direction, means communicating between said
chamber means and said valve spool means wherein initial movement
of said valve spool means in the first direction permits said
piston means to be urged in the second direction and movement of
said valve spool means in the second direction prevents said piston
means from moving in the first direction and causes said piston
means to engage said fuel-adjusting member means in interfering
relation therewith.
7. A fuel-air ratio control device for an engine having a
governor-controlled, fuel-adjusting member means and a supercharger
which supplies air through an intake manifold to the engine, said
control device comprising; pressure-responsive means in
communication with said intake manifold, servo unit means for
engagement with said fuel-adjusting member means and for actuation
by engine lubricant pressure and having an integral piston portion
and valve portion, said valve portion of said servo unit means
having a bore and port means, a valve spool means connected to said
pressure-responsive means and slidably disposed within said bore
and having an annulus for cooperating with said port means in a
sliding relation thereto for controlling the flow of engine
lubricant to actuate said servo unit means, resilient means on one
side of said pressure-responsive means for positioning said annulus
with respect to said port means to permit substantially
unrestricted flow of lubricant through said servo unit means during
engine start-up to render said servo unit means inoperative and to
permit unrestricted operation of said fuel-adjusting member means,
said servo unit means being subsequently actuated upon a
predetermined increase in manifold air pressure at which time said
pressure-responsive means and said valve spool means are shifted
relative to said port means to restrict and meter the flow of
lubricant through said servo unit means so that during any
subsequent reduction in manifold air pressure said servo unit means
is effective to restrain said fuel-adjusting member means against
movement to preclude any disproportionate increase in fuel supply
to the engine as determined with respect to the air available in
the intake manifold.
8. The fuel-air ratio control device of claim 7 wherein the said
servo unit means has an extended member which has a stop means for
selectively constraining said fuel-adjusting member means.
pg,23
9. The fuel-air ratio control device of claim 7 wherein said servo
unit means is disposed in substantially axial alignment with said
fuel-adjusting member means.
10. The fuel-air ratio control device of claim 7 including
resilient means acting in opposition upon opposite sides of said
pressure-responsive means and holding said pressure-responsive
means in a normally-balanced condition.
11. The fuel-air ratio control device of claim 10 wherein said
opposing resilient means are positioned in substantially axial
alignment with said servo unit means and fuel-adjusting member
means.
12. The combination of claim 11 wherein said resilient means
include spring means having a selectively-variable spring rate.
13. The combination of claim 12 including a plurality of spring
means, said spring means being activated cumulatively and in a
series by said pressure-responsive means.
Description
BACKGROUND OF THE INVENTION
This invention relates to a fuel-air ratio control device for
overriding an engine governor means to preclude an increase of fuel
to the engine during a reduction of air pressure in the engine
intake manifold. Supercharged engines, and, in particular, engines
with exhaust-driven supercharges will produce heavy and
objectionable exhaust smoke emissions when rapidly accelerated.
This is because the engine's fuel-adjusting member can be advanced
faster than the speed of the engine, and the supercharger can build
up to provide sufficient air for the combustion of all the fuel
being injected. This results in the expulsion of large quantities
of unburned fuel as exhaust smoke.
Additionally, engines equipped with superchargers of the above type
smoke badly under lug. Lug is encountered when resistance or load
on the engine is increased to the extent that engine speed is
reduced below that which is indicated by the governor setting.
Under these conditions, the engine governor attempts to regain the
engine speed indicated by the governor setting by automatically
advancing the engine fuel rack to supply more fuel, but, due to the
reduction in supercharger speed caused by the reduced engine speed,
insufficient air is supplied to the engine to support complete
combustion of the additional fuel being injected.
The patent to Parks, U.S. Pat. No. 2,767,700, of common assignment
herewith, teaches a system intended to overcome the above problems
by utilizing a pressure-responsive mechanism which is opposed by a
spring member and which interacts with and restrains a
fuel-adjusting member through a movable stop. As disclosed in the
Parks patent, a lack of inlet manifold pressure allows the spring
member to move the movable stop and, therefore, the fuel control
member toward a decreased fuel position. As inlet manifold air
pressure increases, the pressure-responsive mechanism compresses
the spring member and the main governor spring is permitted to move
the movable stop and fuel adjusting member toward an increased fuel
position.
While theoretically operable, it has been found that this type of
fuel-air ratio control imposes certain restrictions on overall
engine performance. First, it is difficult to provide sufficient
fuel for starting because the spring member holds the movable stop
and fuel-adjusting member toward the decreased fuel position.
Second, the governor spring must be allowed to perform its primary
purpose of moving the fuel-adjusting member toward the increased
fuel position to maintain engine speed with an increasing load or
to increase engine speed. At the same time, the spring member which
interacts with the pressure-responsive mechanism must provide
sufficient force to restrain the governor spring until the
pressure-responsive mechanism is actuated by inlet manifold air
pressure. If the preload force on the spring member is greater than
that on the governor spring, acceleration of the engine will be
impeded to an extent which is detrimental to engine performance. If
the spring member preload force is less than that on the governor
spring, the fuel control member will not be positively restrained
by the movable stop and acceleration will be increased, but
overfueling and, therefore, objectionable smoke will occur. Thus,
the initial preload force on the spring member must be made greater
than that of the governor spring and a stop means must be utilized
to establish the predetermined preload. The fuel-adjusting member
is permitted to move toward an increased fuel position prior to
engaging the movable stop. While allowing the governor spring to
move the fuel control member to an increased fuel position, the
spring member provides sufficient restraint until its force against
the fuel control member is counteracted by increasing inlet
manifold air pressure. Thus, a compromise between engine
acceleration and engine smoke is produced.
Also, in certain conditions such as when accelerating from a low
speed, light load, it is characteristic for the supercharger to lag
in supplying air to the intake manifold. This results in the
production of a negative pressure in the intake manifold. The
fuel-air ratio control device of the above-designated patent could
not respond to such negative manifold pressure because the
pressure-responsive mechanism therein is normally disposed against
an adjustable stop which is initially used to establish the preload
force of the spring member.
U.S. Pat. No. 3,077,873 to Parks et al., of common assignment
herewith, overcomes some of the above-noted disadvantages by
providing a servo mechanism which has a movable member acting upon
a valve member while a pressure-responsive mechanism acts upon a
valve spool. Hydraulic fluid pressure is utilized to provide a
balance of forces between the governor spring, spring member and
the intake air pressure responsive mechanism. The use of the servo
unit permits the spring member to be balanced for improved response
when interacting with the pressure-responsive mechanism. However,
the main disadvantage of this device lies in the necessary
maintenance of a servo piston as a separate unit and in the use of
an intermediate movable member to provide control of the valve. The
resultant configuration is complex and relatively costly.
SUMMARY AND OBJECTS OF THE INVENTION
A fuel-air ratio control device for supercharged engines having a
governor connected to a fuel control member and a supercharger
supplying air through an intake manifold to the engine having an
integral servo piston and valve unit placed in a restraining
relationship with respect to the fuel control member. The servo
piston is activated by a fluid force controlled by movement of a
valve spool which slides in an opening and closing manner relative
to ports in a portion of the servo piston. The valve spool is
secured to a pressure-responsive mechanism which communicates with
the engine intake manifold. Resilient means oppose the reaction of
the pressure-responsive mechanism to intake manifold pressure.
During engine start-up, the valve spool and ports of the servo
piston are in an open condition to render the servo unit
inoperative and to permit unrestricted operation of the fuel
control member. The servo unit is subsequently activated when a
predetermined increase in manifold air pressure shifts the valve
spool relative to the servo piston ports and blocks and meters the
flow of hydraulic fluid to the servo piston. During subsequent
reductions in manifold air pressure, the servo unit is effective to
restrain the fuel control member against movement toward an
increased fuel position. The servo unit's restraint of the fuel
control member precludes any disproportionate increases in fuel to
the engine when the air available in the intake manifold is
insufficient to support proper fuel combustion.
It is an object of this invention to provide an improved fuel-air
ratio control device for overriding the governor and controlling
the injection of fuel to a supercharged engine in strict proportion
to the air pressure available in the engine's intake manifold to
insure complete combustion of fuel by the engine.
Another object of this invention is to provide an improved governor
overriding fuel-air ratio control device which is responsive to
both intake manifold air pressure and to engine oil pressure with
the control device automatically permitting unrestricted movement
of the fuel adjusting member on the engine during cranking to
insure sufficient fuel for dependable starting, but thereafter
automatically restricting the injection of fuel into the engine to
precisely that amount required for operating the engine at maximum
efficiency.
Other objects and advantages of the present invention will become
more readily apparent upon reference to the accompanying drawings
and following description.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a longitudinal vertical section through the fuel-air
ratio control device of the present invention which also
schematically illustrates a supercharged engine intake manifold, a
governor, and a fuel pump mechanism with the control device being
shown in engine start condition.
FIG. 2 is a longitudinal vertical section through the fuel-air
ratio control device of the present invention similar to FIG. 1 but
omitting the governor and showing the fuel-air ratio control device
in engine operating position.
FIG. 3 is a partial longitudinal vertical section through a
modified embodiment of the fuel-air ratio control device of the
instant invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring particularly to FIGS. 1 and 2 in the drawings, a fuel
pump 10 has a plunger 12 vertically reciprocal during engine
operation to supply fuel through a fuel injection line 11 to one of
the cylinders of the engine, there being one pump for each engine
cylinder. Longitudinal movement of a fuel adjusting member 17
having rack teeth 15 moves a gear 14 secured to plunger 12. The
pump is of the metering type in which angular adjustment of the
plunger 12 results in a variation of the quantity of fuel injected
upon each stroke.
The fuel adjusting member 17 is secured to a riser 18 having an
extending link 19 with a stop member 20 attached to its distal end.
A pair of flyweights 22 carried upon a yoke 23 are driven by a gear
24 which is rotated by the engine's timing gear (not shown) at a
speed proportional to engine speed. Radially outward movement of
the flyweights due to centifugal force causes portions of the
flyweights to act leftwardly upon the riser 18. A spring 26,
disposed between the riser and a collar 27, opposes the biasing
action of the flyweights. A movable lever 28 is positioned to
provide a predetermined selectable preload force for the spring 26
to act against the force of the flyweights 22.
An engine air intake manifold 30 is supplied with air under
pressure by an engine-driven supercharger 31. A conduit 32
communicates between the intake manifold and a chamber 35 formed by
an adapter 33 having a cover 36 secured by bolts 37.
A control housing 39 has an inlet 40 connected to a fluid pressure
source such as engine lubrication oil. An orifice 43 communicates
inlet 40 with a bore 44 formed in the housing 39. A servo unit 46
has a piston portion 47 slidable within bore 44 and a valve means
48 integral with a piston portion and slidable within a bore 50
formed in the housing. The valve means has an extending portion 49
with a shoulder 49a thereon which is positioned to engage the stop
member 20 under conditions to be explained hereinafter. An
expansible chamber 53 is formed by a face 51 of the piston 47, a
surface 52 of housing 39, and bore 44. Fluid from inlet 40 is
permitted to enter chamber 53 by way of a groove 54 in the surface
52 which is intersected by the orifice 43.
A first set of passages 56 in valve means 48 communicate the
chamber 53 with a bore 62 in the servo unit. A second set of
passages 57 of valve means 48 communicate the bore 62 with an
annular groove 58 formed in the bore 50. The annular groove, in
turn, is intersected by a drain passage 60 in housing 39. Another
passage 91 is provided to communicate any fluid which might leak
through the servo unit to the drain.
A valve spool 63, slidable in the bore 62, has an annulus 66 formed
between a pair of lands 64 and 65. When the land 64 is disposed as
shown in FIG. 1, the passage 56 is open and land 65 is disposed so
that passage 57 is open and chamber 53 is in communication with the
drain passage 60.
A threaded portion 67 of valve spool 63 is secured to a cup member
68. An end 69 extends from the threaded portion 67 and has a pin 70
which engages a slot 36a in the cover 36.
A first spring member 72, having a first spring rate, is disposed
between the piston 47 and cup member 68. A second spring member 73,
having a second spring rate, is disposed between the cup member and
a seat member 74. A diaphragm 76 is secured between the adapter 33
and the housing 39 and is supported by the cup member 68. A washer
77 disposed adjacent to and rearwardly of the diaphragm 76 acts as
a seat for a third spring member 78 which resides between the cover
36 and the washer. The rates of the three spring members are such
that forces on the diaphragm are balanced when no pressure is
extant in the chamber 35 to provide sensitivity in the servo
unit.
OPERATION
Prior to engine start-up, the fuel-air ratio control of the present
invention assumes an inoperative position in the following manner.
Spring member 72 urges the servo unit 46 toward the right, as shown
in FIG. 1, and removes the shoulder 49a from engagement with stop
20. Any movement of the lever 28 in a counterclockwise direction
compresses spring 26 and moves the fuel adjusting member 17
rightwardly toward an overfueling position. During engine cranking
or upon initial start-up of the engine, the valve spool 63 is
maintained in this position which provides communication between
passages 56 and 57 through annulus 66 by means of the balanced
condition of the spring members 73 and 78 which act upon the
diaphragm 76. Fluid under pressure which enters the chamber 53 from
the inlet 40 is drained off through passages 56, 57, and 60 thus
preventing the exertion of a fluid force upon the piston 47 and
consequent leftward movement.
After the engine has started and speed is increased a predetermined
amount, air pressure in intake manifold 30 builds up and the
pressure in chamber 35 increases. At such time, diaphragm 76 is
acted upon by the increasing air pressure in chamber 35. This tends
to compress the spring members 72 and 73 and to move valve spool 63
toward the right. Such movement eventually causes the land 64 to
cover passages 56. Fluid is thus prevented from draining from the
chamber 53 and fluid pressure begins to build therein to force the
piston 47 toward the left into a control operative position. During
this leftward movement, the shoulder 49a engages stop member 20 and
moves the fuel-adjusting member 17 to a decreased fuel position
such as is shown in FIG. 2. The mechanism is cocked and operative
when it is disposed as shown in FIG. 2.
When the engine is operating at idle, air pressure in the intake
manifold and in chamber 35 together with the bias of spring member
78 would not be sufficient to overcome the bias of the spring
members 72 and 73 acting upon the diaphragm 76. The valve spool 63
would be restrained in a leftward position by the diaphragm member
76 and the piston 47 would be in the operative position wherein
land 64 would effectively restrict the passages 56 to permit only a
predetermined amount of fluid to be metered from chamber 53 to
maintain the piston 47 in the position shown in FIG. 2. The
passages 57 would be out of alignment with the annular groove 58
and the drain passage 60 to prevent fluid drainage.
As previously described, when the lever 28 is moved
counterclockwise, the spring 26 is compressed to cause loading and
movement of the fuel-adjusting member 17 rightwardly toward an
increased fuel position. However, with the fuel-air ratio control
device operative, the spring members 73 and 78 would tend to
position the valve spool 63 toward the left. Therefore, the servo
unit 46 and the shoulder 49a would permit only a slight movement of
the fuel control member toward the increased fuel position.
If a negative pressure occurred momentarily in the manifold 30 and
chamber 35, such as when the engine was accelerating from a low
speed at light load, the diaphragm 76 would be drawn to the left
causing the servo unit 46 to be moved slightly in the same
direction. The shoulder 49a would engage the stop 20 as the stop
tended to move rightwardly to increase the fuel supply to meet the
demands. As engine speed increased, however, air pressure in
chamber 35 would increase slightly and would move the diaphragm 76
and valve spool 63 to the right. The land 64 would move and
slightly uncover the passages 56 to permit fluid to be metered out
the opening and drain to the outlet 75 through a passage 74a. Fuel
adjusting member 17 would then be permitted to pull the servo unit
to the right as long as the air pressure in chamber 35 was
increasing and the valve spool 63 was moved rightwardly to allow
fluid to drain from the chamber 53.
With the engine operating within a predetermined speed and load
range, as determined by the governor flyweights, sufficient air
will be available within the chamber 35 to maintain the fuel-air
ratio control device in a position which does not restrict the
slight movements encountered by the governor in maintaining that
speed. However, if engine load is increased to the point of
decreasing engine speed, then air pressure in the chamber 35 will
be reduced by a proportionate amount so as to cause land 64 to
restrict the passages 56 and allow fluid forces in chamber 53 to
move the piston 47 slightly leftwardly to cause shoulder 49a to
restrain the stop 20 and prevent a disproportionately-larger amount
of fuel to be injected relative to the available air. If the
operator moves the lever 28 to accelerate the engine, the stop 20
will be restrained by shoulder 49a until such time as sufficient
air becomes available in chamber 35 to permit the servo unit 46 to
be moved to the right by the fuel-adjusting member 17.
DESCRIPTION OF MODIFIED EMBODIMENT
A modification of the instant invention is shown in FIG. 3. A
different plurality of spring members are provided to oppose the
air-pressure-responsive diaphragm 76 in a manner somewhat similar
to the first form of the invention. Elements common to both forms
have identical reference numerals. The modification permits a
variable biasing force to act upon the diaphragm for more precise
tailoring of the fuel-air ratio control device to the needs of a
particular engine, as will be described.
The spring rate of a single spring opposing the pressure-responsive
diaphragm is linear. However, the intake manifold pressure of a
supercharged engine does not always increase at a linear rate. Such
a rate disparity could lead to short periods when the increasing
air pressure is temporarily reduced while the fuel-adjusting member
is moving toward an increased fuel position. This could lead to a
phenomenon referred to as secondary exhaust smoke plumes. The
fuel-air ratio control device, shown in the version of FIGS. 1 and
2, eliminates or limits these secondary plumes to acceptable limits
in most engines. It has been found, however, that in certain
engines the exhaust plumes are slightly above an acceptable limit.
For these engines, it becomes necessary to provide a plurality of
springs in series or a variable-rate spring to oppose the
pressure-responsive diaphragm. With this provision, it is possible
to tailor the fuel-air ratio control device functions to particular
engine characteristics.
As shown in FIG. 3, a first spring member 80 is disposed between a
seat member 81 and the piston 47. Seat member 81 is slidable within
a bore 82 in the housing 39. A second spring member 84 is disposed
between the seat member 81 and an intermediate cup-shaped member
85. A third spring member 86 is disposed between a flange 88 of the
cup-shaped member and a cup member 68. A fourth spring member 78 is
disposed between the cover 36 and the washer 77, as in the primary
embodiment. Each spring member has a particular predetermined
spring rate.
For instance, the rate required of the third spring member 86 is
calculated by determining the amount of rack movement (deflection)
relative to the force (load) acting on the diaphragm 76 during a
given period of engine operation. A spring equation, Deflection
(third spring member) = (Load/K4 + K3) is used where K4 (fourth
spring member 78), deflection and load are known establishes the
rate of K3 (third spring member 86). The rate required of the
second spring member 84 is calculated by the amount of rack
movement (deflection) relative to the force (load) acting on a
diaphragm 76 during a given period of engine operation just prior
to that period of engine operation controlled by the third spring
member 86. A spring equation, deflection (of second spring
member)=[Load/K4 + (1/1/K2 + 1/K3)]
where K4, deflection, load and K3 (third spring member) are know
establishes the rate of the second spring member K2. The rate
required of the first spring member is calculated by the amount of
deflection relative to the load acting on diaphragm 76 just prior
to that period controlled by the second spring member. Spring
equation, Deflection (of first spring member)= [load/K4 + (1/1/K1 +
1/K2 + 1/K3)]
where K4, deflection, and load are known, and K3 and K2 have
previously been determined establishes the rate of the first spring
member K1.
OPERATION OF MODIFIED EMBODIMENT
In operation, the first spring member 80, with a relatively low
rate, is utilized initially to move the seat 81 slidably toward the
left within the bore 82. Thus, initial air pressure in the chamber
35, which would be slight, would be working against a relatively
weak spring. As air pressure increased further, the spring members
85 and 86, having relatively higher forces than spring member 80,
would act against the spring 80 through the seat member 81 until
the seat member would move against a stop 83, at which time the
second spring member 84, having a slightly greater spring rate than
the spring member 80, would oppose the air pressure in chamber 35.
A still further increase in air pressure in the chamber 35 would
compress the spring member 84 through the spring member 86, which
member has a still higher spring rate than spring member 84. At a
predetermined air pressure in chamber 35, cup-shaped member 85 will
bottom against seat member 81 and air pressure in chamber 35 will
begin to act upon the spring member 86. Thus, a selectively,
progressively-increasing spring rate will be available to oppose
the variably-increasing air pressure in chamber 35.
In the primary embodiment the use of a single spring produces a
linear force to oppose the variably-increasing air pressure force.
In the modified embodiment the use of different rate springs
provides a linear force in combination with a geometric change of
force to more evenly match the change of force of the air
pressure.
Valve spool 63 will act in the manner previously described in the
primary embodiment. Compression of the springs by the
pressure-responsive diaphragm will act to permit fluid to be
metered out of chamber 53. This will permit the fuel-adjusting
member 17 to move rightwardly toward an increased fuel position.
The plurality of springs permits the pressure-responsive diaphragm
to be more responsive to the air pressure characteristics of the
supercharger.
While the invention has been described and shown with particular
reference to the preferred embodiment, it will be apparent that
variations and modifications would fall within the spirit of the
present invention and the scope of the appended claims.
* * * * *