U.S. patent number 3,667,437 [Application Number 05/065,202] was granted by the patent office on 1972-06-06 for multiple plunger fuel injection pump.
This patent grant is currently assigned to Allis-Chalmers Manufacturing Company. Invention is credited to Alexander Dreisin.
United States Patent |
3,667,437 |
Dreisin |
June 6, 1972 |
MULTIPLE PLUNGER FUEL INJECTION PUMP
Abstract
Multiple plunger fuel injection pump having built in fuel
injection timing and quantity control.
Inventors: |
Dreisin; Alexander (Olympia
Fields, IL) |
Assignee: |
Allis-Chalmers Manufacturing
Company (Milwaukee, WI)
|
Family
ID: |
22061026 |
Appl.
No.: |
05/065,202 |
Filed: |
August 19, 1970 |
Current U.S.
Class: |
123/449; 123/495;
123/501 |
Current CPC
Class: |
F02M
59/44 (20130101); F02D 1/10 (20130101); F02M
59/361 (20130101) |
Current International
Class: |
F02D
1/08 (20060101); F02M 59/20 (20060101); F02M
59/44 (20060101); F02M 59/00 (20060101); F02M
59/36 (20060101); F02D 1/10 (20060101); F02m
059/00 () |
Field of
Search: |
;123/139R,139AB,139AD,139AE,139AG,139AP,14R |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Goodridge; Laurence M.
Claims
The embodiments of the invention in which an exclusive property or
privilege is claimed are defined as follows:
1. A multiple plunger fuel injection pump for an internal
combustion engine comprising, a pump housing means defining a
plurality of bores, a plunger received in each of the bores and
defining a fuel injection pumping chamber and a fuel supply chamber
in each of said bores, a delivery valve in communication with each
of said fuel injection pumping chambers, each of said plungers
defining passage means selectively communicating between said
injection pumping chamber and said supply chamber for supplying
fuel to said injection pumping chamber, means sequentially
reciprocating each of said plungers for discharge of fuel from said
fuel injection pumping chamber through said delivery valve, a
control sleeve mounted for reciprocal and rotational movement about
each of said plungers and defining port means with said plunger for
controlling the closing and opening of said passage means in said
plunger between the supply chamber and the fuel injection pumping
chamber, lever means connected to said plunger for rotating said
plunger in said housing means to calibrate one of said plungers
relative to remaining plungers, a speed responsive device adapted
for connection to an engine including a control member moving in
response to engine speed and load, means connecting said control
member to each of said control sleeves for transmitting rotational
and axial movement of said sleeves thereby controlling the quantity
and timing of fuel injection delivered from said injection pumping
chambers through said delivery valves.
2. A multiple plunger fuel injection pump for an internal
combustion engine as set forth in claim 1 wherein said means
sequentially reciprocating said plungers comprises a cam, a cam
follower connected to each of said plungers to operate said
plungers in response to operation of said cam, said lever means
defines a shim removably positioned between said plunger and said
follower, a window for selectively positioning said shim of
predetermined thickness between said plunger and said follower when
said window is open.
3. A multiple plunger fuel injection pump for an internal
combustion engine as set forth in claim 1 wherein said means
sequentially reciprocating each of said plungers includes, a cam, a
cam follower operated by said cam, said lever means defining
calibration shim removably positioned between said plunger and said
cam follower to thereby provide a means of selectively controlling
the high and low position of each of said plungers in response to
rise and fall of said cam follower.
4. A multiple plunger fuel injection pump for an internal
combustion engine as set forth in claim 1 wherein said plunger and
control sleeve define a spill slot means having a diagonal edge,
said lever means connected to said plunger for rotating said
plunger on its axis relative to said sleeve for selectively and
alternatively increasing and decreasing quantity of fuel injection,
an adjusting screw means mounted in said housing connected to said
lever means to thereby adjustably rotate said plunger relative to
said control sleeve to vary fuel quantity injection.
5. A multiple plunger fuel injection pump for an internal
combustion engine as set forth in claim 1 wherein said speed
responsive device includes said member rotatably and axially
movable relative to said housing means, a timing mechanism
including a control rod in said means connecting said control
member with each of said control sleeves providing axial movement
of said control sleeves for timing control, means for transmitting
axial movement from said control member to said control rod to
rotatably move said control sleeves for fuel quantity control, said
lever means connected to said plunger providing timing calibration
by its selective thickness and quantity calibration through plunger
rotation by said lever means.
6. A multiple plunger fuel injection pump for an internal
combustion engine as set forth in claim 1 wherein each of said
plungers and control sleeves define a diagonal spill slot and port
means whereby rotational movement of said control sleeve varies
fuel injection quantity, said means reciprocating said plungers
including a cam and a cam follower, said lever means defining a
shim removably positioned between said plunger and said cam
follower to control the extreme reciprocal positions of said
plungers in response to rise and fall of said cam follower, said
lever means operating to selectively rotate said plunger relative
to said control sleeve to thereby increase or decrease quantity of
fuel injection of the adjusted plunger with relation to remaining
multiplungers at said pump.
7. A multiple plunger fuel injection pump for an internal
combustion engine as set forth in claim 1 wherein each of said
plungers define a spill port in said passage means, each of said
control sleeves define a diagonal slot on their internal periphery
for spilling high pressure fluid from said fuel injection pumping
chamber through said spill port for termination of fuel injection,
said means reciprocating said plunger including means selectively
receiving said lever means of desired thickness for calibration of
timing.
8. A multiple fuel injection pump for an internal combustion engine
as set forth in claim 1 wherein the end of said plunger includes
slot means for receiving said lever means to thereby selectively
control the plunger position axially and angularly relative to its
mating control sleeve for calibration of said plunger.
9. A multiple plunger fuel injection pump for an internal
combustion engine as set forth in claim 7 including means defining
a window for removably positioning said lever means for rotating
said plunger in said housing means, an adjusting screw pivoting
said lever means to calibrate said plungers relative to the
remaining plungers, a cover removably positioned over said
adjusting screw and said window.
10. A multiple plunger fuel injection pump for an internal
combustion engine as set forth in claim 1 including an adjusting
screw for pivoting said lever means and rotating said plunger, a
cover removably positioned over said adjusting screw.
Description
This invention relates to a fuel injection pump for an internal
combustion engine and more particularly to a multiple plunger fuel
injection pump with fuel injection timing and quantity control
within the fuel injection pump responsive to engine speed and load
conditions.
Multiple plunger fuel injection pumps which are used today on high
speed Diesel engines generally have a fixed timing in relationship
to the engine. Initiation of injection occurs after the closing of
an intake port. In order to change timing of the pump it is
required to dephase the pump camshaft in relation to the engine.
The camshaft sequentially drives the plungers in the multiple
plunger fuel injection pump. The dephasing of the pump is done
usually by interposing a mechanical timing advance between the pump
drive shaft of the engine and the injection pump camshaft. The
mechanical timing advance mechanism consists of centrifugal weights
balanced by springs which change their position as a function of
engine speed and transform this change into a dephasing between the
pump camshaft and the pump drive shaft. This mechanism is bulky and
rather complicated because the entire pump driving torque has to be
transmitted through the timing advance mechanism. In addition to
its bulkiness and complexity which results in low reliability the
timing advance mechanism requires an additional installation length
between the pump drive shaft and the pump itself. This space is
very costly on the engine and sometimes, especially in the smaller
models is not available. With Diesel engines, of increasing engine
speed which is the modern trend of Diesel engines, it becomes more
and more necessary to dephase the fuel injection pump and to
control the beginning of injection with relation to the engine in
order to obtain the best combustion efficiency and starting
properties throughout the engine speed range.
Accordingly, this invention provides a timing advance mechanism in
the injection pump per se. By incorporating the timing advance
mechanism, within the pump itself, the mechanism can be
substantially simplified over the conventional dephasing mechanism
in the drive assembly. The control rod connected to a plurality of
control sleeves provides a means whereby the timing and quantity
control for fuel injection can be conveniently and simply
controlled in response to movement of a control member on the
governor of the engine.
Accordingly, it is an object of this invention to provide a
multiple plunger fuel injection pump with built-in timing and
metering control.
It is another object of this invention to provide a multiple
plunger fuel injection pump incorporating a timing and metering
control responsive to speed and load conditions of the engine.
It is a further object of this invention to provide a cam operated
multiple plunger fuel injection pump having a speed responsive
control element operating a control sleeve on each of the plurality
of plungers to thereby control fuel injection timing and
quantity.
It is a further object of this invention to provide a cam operated
multiple plunger fuel injection pump having a control sleeve on
each of the plungers controlled in response to a governor operated
control mechanism to thereby control timing and quantity of fuel
injection for each of the plurality of plungers.
The objects of this invention are accomplished by incorporating in
a multiple plunger fuel injection pump a control sleeve operating
with each plunger. A control rod is connected to each of the
control sleeves and is adapted for reciprocal and rotational
movement to in turn provide reciprocal and rotating movement o the
control sleeves. The control member on a governor operates in
response to the speed and a manual setting on the throttle shaft
which in turn transmits a rotational and reciprocal movement to the
control rod. The control rod being connected to each control sleeve
on the plurality of plungers operates to control the initiation and
termination of fuel injection and also the duration of fuel
injection to thereby control timing and quantity of fuel injection
of the engine in response to the speed and load conditions.
The preferred embodiments of this invention are illustrated in the
attached drawings.
FIG. 1 is a side elevation view with portions of a fuel pump
cutaway to show related parts of the pump.
FIG. 2 is an end view of FIG. 1.
FIG. 3 is a cross section view taken on line III--III of FIG.
1.
FIG. 4 is a cross section view taken on line IV--IV of the FIG.
3.
FIG. 5 is a view of the plunger and control sleeve.
FIG. 6 is a plan view of FIG. 5 showing the plunger and control
sleeve.
FIG. 7 is a modification of the plunger and control sleeve.
FIG. 8 is a plan view of the modification shown in FIG. 7.
FIG. 9 is a fragmentary view of the control rod and one of the
control sleeves illustrating their operation in the fuel pump.
FIG. 10 is a cross section view of the governor connected to the
control rod.
FIG. 11 is a cross section view of the governor as viewed from the
end of the control rod.
Referring to the drawings, FIG. 1 illustrates a multiple plunger
fuel injection pump 50 having a plurality of cam operated pump
assemblies 51, 52, 53, 54, 55 and 56. The camshaft 57 includes a
plurality of cams, of which cams 1 and 58 are shown, which operate
the pump assemblies 56 and 55 respectively. The camshaft 57 is
engine driven and directly connected to the engine 110. FIG. 3
illustrates the cam follower 2 which is driven by the cam 1 on the
camshaft 57. The cam follower 2 includes a roller 59 supported in
the follower sleeve 60. The follower sleeve 60 receives the
follower plate 4 which carries the plunger 3. The follower sleeve
60 also carries the pin 61 which rides up and down in the slot 23
of the housing 63. Pin 61 maintains the alignment of the roller 59
on the cam 1.
The shoulder 64 on follower sleeve 60 supports the follower plate
4. The follower plate 4 is formed with openings 65 and 66 to permit
the flow of fuel through the plate when the follower
reciprocates.
As shown on the left side of FIG. 1, the plunger 3 is spaced from
the cam follower plate 4 by a rectangular strip or timing shim 5
visible also in FIG. 3 and the partial section view FIG. 4. Timing
pin 6 locates the timing shim angularly in relation to the pump
body as will be explained more fully later in the description.
The plunger 3 has a milled slot 108 in the bottom which straddles
the timing shim 5 and it is therefore retained in an angularly
controlled position in relation to pump housing.
The plunger 3 has an axial drilled passage 7 communicating with a
radial port 8. The intermediate portion of the plunger is fitted
within the control sleeve 9 which has a helical slot 10 on its
inner periphery on the same side of the plunger as the radial port
8. The control sleeve 9 has the cylindrical wall 11 extending
upwardly. A control finger 12 is rigidly connected with this
cylindrical wall and is equippedwith a spherical end 68 which has a
sliding fit in the cross drilled passage 13 located in the control
rod 14.
The upper portion of the plunger 3 is fitted into the barrel 15.
The barrel 15 is threaded on the outer periphery and is held in
delivery union 16 which also carries a delivery valve 17 and an
outlet fitting 18.
The plunger spring 19 transmits a downward force through the lower
spring seat 20 to the plunger retaining plate 21 which engages a
peripheral recess 70 on the plunger 3. The retaining plate 21 is
formed with an opening 71 to facilitate assembly and to permit fuel
to flow into the fuel supply chamber 72 surrounding the control
sleeve 9.
Fuel from a supply pump 125 passes through the opening 67 through
slot 23 vertically upward into the supply chamber 72. The camshaft
compartment is also filled through the opening 67 which flows
upwardly through the cam follower plate 4 and retainer plate 21.
Excess fuel continues to flow upwardly through the chamber 72 and
outlet opening 35 and returns through a pressure relief valve to
the fuel tank.
Barrel 15 and plunger 3 form the fuel injection chamber 24 which
discharges pressurized fuel through the delivery valve 17. The
delivery valve 17 is in communication with the fitting 18 which is
adapted for connection to a combustion chamber of an internal
combustion engine.
A calibration means to accommodate vertical tolerances is provided
as shown in FIGS. 1, 3 and 4. The calibration screw 32 has an
eccentric timing pin 6 received in the fork timing strip 5. Timing
strip 5 is received within a slot 108 in the lower end of the
plunger 3. The timing strip 5 will be manufactured in varying
thicknesses and can be inserted through the window 31 to make the
proper calibration setting for each individual pump assembly. The
O-ring 33 seals the calibration screw. The pump cover 34 covers the
timing window 31 and at the same time will prevent unauthorized
interference with the adjustment screw 32.
FIG. 5 illustrates the control sleeve 9 on the plunger 3. FIG. 6
also illustrates a plan view of the control sleeve 9. The passage 7
extends upwardly through a portion of the plunger 3 and is
connected to the radial port 8 which extends to the outer periphery
of the plunger 3. The sleeve 9 is shown with a helical slot 10 cut
on its inner periphery forming an edge 26 which passes over the
radial port 8 as the plunger is moved upwardly.
FIGS. 7 and 8 show a modified control sleeve 109 on the modified
plunger 103. The axial passage 7 is connected to the radial port 8
as shown. A recess 171 is formed in the plunger 103 having a
triangular configuration as shown in FIG. 7. The edge 28 of the
recess 171 comes in to register with the lower edge 122 of the
control sleeve 109 to initiate fuel injection. The triangular
recess forms a helical edge 29 which subsequently comes in
communication with the radial opening 30 in a control sleeve 109 as
the plunger is moved upwardly to terminate injection.
It is understood that the metering edges 28 and 29 and recess 171
could be inverted from that shown in FIGS. 7 and 8 whereby the
registry of helical edge 29 and passage 8 control initiation of
injection. The beginning of the effective stroke with a constant
port closing is shown.
A control rod 14 controls a plurality of control sleeves such as
control sleeve 9 on mating plungers such as plunger 3. Each control
sleeve is connected to the control rod 14 by a stem 12 received in
an opening 13 and forms a spherical head 68 as shown in FIG. 3. The
control rod reciprocates to rotate the control sleeve and thereby
increase or decrease the fuel quantity of injection per stroke. The
control rod 14 also rotates in response to engine speed causing a
lifting and lowering of the control sleeve which in turn produces a
change in the timing of fuel injection. This movement of the
control rod 14 is accomplished with a conventional speed responsive
mechanism such as an engine governor. For the purpose of
illustration the function of the governor and its control of the
control rod 14 is shown in FIGS. 9, 10 and 11. The control rod 14
is connected to the control sleeve 9 as shown in FIG. 9. The
control rod 14 is connected to the governor plate 74 which carries
the control finger 75 extending axially in parallel with the
control rod 14 to control fuel quantity. The timing finger 76
extends from the governor plate 74 and is adapted for rotating of
the control rod 14 about its axis to control timing of
injection.
Referring to FIGS. 10 and 11 a governor is shown connected to the
governor plate 74 through the control finger 75 and the timing pin
76. The governor plate 74, timing pin 76 and control finger 75 are
rigidly fastened to the control rod 14 to transmit rotary motion
produced by a slotted plate 77 and transmit axial motion produced
by motion of the governor yoke assembly to the control finger 75
and the control rod 14.
The timing of fuel injection is contolled by a rotary motion
generated by the centrifugal governor 78. The screw 79 is rigidly
fixed to the governor housing 80 and engages an angled slot 81 in
the slotted plate 77. A rotary motion is imposed on a slotted plate
77 as it moves axially responsive to speed changes. The timing fork
83 is rigidly fixed to the slotted plate 77. The timing fork 83
transmits a rotating force to the timing pin 76 which inturn is
transmitted through the governor plate 74 to the control rod 14
producing a vertical displacement of the control sleeve 9.
An angular displacement of the slotted plate 77 is a function of
the axial displacement of the slotted plate 77 and the angle of the
slot 81.
Referring to the governor 78, the fly weights 84 are driven by
shaft 85 which is connected to the engine. The shaft 85 carries the
bracket 86 for pivoting the weights 84. As the fly weights 84
rotate, a centrifugal force is generated tending to accelerate them
radially. This force is transmitted through the fly weight fingers
and thrust bearing 87 to the shifter sleeve 88 and the slotted
plate 77. The impending motion of the shifter sleeve 88 and slotted
plate 77 is opposed by the spring force of the springs 89 and 90
which creates an equilibrium position of the shifter sleeve 88
solely a function of governor speed or engine speed. By utilizing
the shifter sleeve 88 as a speed sensing member, the timing fork 83
transmits a signal of the axial position of the shifter 88 to the
slotted plate 77 to the timing pin 76, causing the control rod 14
to rotate and to move the control sleeve 9 vertically.
The slotted plate 77 and the shifter 88 are rigidly fastened
together and moves the unit axially and angularly. As the speed
increases the shifter sleeve 88 moves axially toward the spring 89
and 90 until a new position of equilibrium is reached. This axial
movement of the shifter 88 and the slotted plate 77 in cooperation
with the screw 79 and the angled slot will cause further rotation
of the slotted plate 77 and the timing fork 83. This rotation is
transmitted by the timing pin 76 through the governor plate 74 and
control rod 14. The control rod 14 moves the control sleeve 20 thus
lowering the control sleeve. Port closing or beginning of the
injection will occur earlier in the cycle as the speed
increases.
The speed setting of the internal combustion engine is controlled
through a throttle shaft 91 which is manually controlled. Once the
throttle shaft 91 is set the centrifical governor will
substantially maintain the speed setting of the throttle control.
The throttle shaft 91 is mounted on the governor housing 80.
The governor yoke assembly comprises a torque link 93 and a yoke 94
rotatably hinged on a pin 95. A spring 96 is compressibly
positioned etween the sleeve 181 carried on housing 180 and the
governor plate 74. This spring biases the control finger 75 to an
engagement position n the torque plate 97 to maintain the torque
plate in contacting position with the shaft 95 and yoke 94. The
force of the spring will bias the governor yoke 94 to engage the
shaft 95 and cause the torque plate 97 and yoke 94 and torque link
93 to initially rotate as a unit about the pin 98.
The shifter pin 99 engages the lower end of the governor yoke 94
and transmits an axial motion of the shifter sleeve 88 and slotted
plate 77 to the governor assembly. When an equilibrium position
exists between the fly weights 84 and the governor springs 89 and
90, rotation of the throttle shaft 91 will displace the pin 98.
This will force the governor yoke assembly to rotate about the
shifter pin 99. The torque plate 97 on the upper end of the
governor yoke 93 transmits the rotational movement to cause in the
control finger 75 an axial movement which will rotate the control
sleeve 9 so the required amount of fuel may be delivered to the
engine.
With the throttle shaft held in this position, the position of the
pin 98 remains the same. A decrease in engine speed in other words,
a load increase will make shifter sleeve 77 move to a new
equilibrium position away from the governor springs 89 and 90. This
movement will be transmitted by the shifter pin 99 to slots in the
lower end of the governor yoke 94. The control finger 75 is contact
with the torque plate 97 at the end of the governor yoke 93 will be
moved toward an increased fuel position which will tend to
reestablish the original speed.
The torque plate 97 is retained on the governor yoke 94 by the pin
95. The spring 96 biases the torque plate 97 to an engagement
position with the pin 95 and yoke 94. This arrangement provides for
a degree of governor yoke rotation relative to the link 93 which is
limited by the clearance between the torque adjusting screw 101 on
the torque link 93. This rotation occurs when the yoke rotates
about the fuel stop adjusting screw 102 on the fuel stop lever 103
which is pivotally supported on the shaft 104 and mounted in
housing 80. Although the complete description of the governor is
quite extensive, it is understood that a conventional governor
which provides a speed control for timing of fuel injection and a
torque control or load control which is responsive to a manual and
speed control to provide a control of the quantity of fuel injected
would be satisfactory. The multiple plunger fuel injection pump as
described operates in response to such a speed and manual control
such as set forth in this description above. A more detailed
description of the governor assembly can be had by reference to the
U.S. Pat. No. 3,421,486, entitled Fuel Injection Control, if a more
detailed description is desired.
The relative position of the various parts of the governor
mechanism are shown in the high idle position in FIGS. 10 and
11.
The injection pump operates as follows. Fuel under pressure from
supply pump 125 enters the injection pump housing 63 through the
opening 67. As fuel is supplied to the fuel injection pump
assembly, it is permitted to flow upwardly through the cam follower
2 and slot 23 as well as the radial port 8 and the axial passage 7
to the fuel injection pump chamber 24, when the plunger is at the
bottom of the stroke. As the cam 1 rotates the plunger begins to
lift until the port 8 is closed by the lower edge 22 of the control
sleeve 9. As the plunger continues to rise, it compresses the fuel
into the pumping chamber 24. Fuel pressure opens delivery valve 17
and the fuel then passes into the outlet connector 18 and from
there through a high pressure line, and a fuel injection nozzle to
the combustion chamber.
On its further upward movement radial passage 8 registers with the
lower edge 26 of the helical slot 10 in the control sleeve 9. As
shown in FIG. 3 this slot communicates with the fuel filled cavity
72 in the pump housing through the intersection of the helical slot
10 with the lower edge 22 and the upper edge 27 of the control
sleeve 9. When the upper edge of the radial port 8 registers with
the edge 26, communication is reestablished between the pumping
chamber 24 and the fuel supply chamber 72. The injection pressure
is spilled and the delivery valve 18 closes and injection is
terminated in a conventional manner.
Two control motions are available to the control sleeve 9. The
first motion is up and down. This motion can be induced by rotation
of the control rod in a clockwise or counterclockwise direction.
This motion will move the outside edge of the passage 13 up and
down and this movement is transmitted to the control sleeve 9 by
the finger 12. When the control sleeve 9 is lifted closing of port
8 will occur later. Injection will be retarded without affecting
the output quantity. Lowering of the control sleeve will effect
closing of the radial port 8 and will advance injection.
The second mode of control occurs when the rod is moved axially
back and forth. This does not affect the port closing or the
injection timing, however, it changes the effective stroke by
moving the helical slot 10 away or toward the port 8. Moving it
toward port 8 will decrease the effective stroke because the upper
edge of the port 8 will meet edge 26 sooner decreasing the delivery
quantity of the pump.
An alternative arrangement is shown in FIGS. 7 and 8. In these
figures the helical recess of essentially a triangular shape is
produced on the circumference of the plunger 103. As shown in FIG.
8 the recess has a predetermined depth. The recess communicates
with the axial passage 7 through the radial port 8 but the metering
and timing are now controlled by the edges of the triangular cutout
on the plunger as follows. When the plunger starts its rise, edge
28 of the recess on the plunger registers with the lower edge 122
of the control sleeve 109 effecting the port closing. In its
further upward stroke the helical edge 29 of the plunger recess
will register with the radial passage 30 on the inside diameter of
the control sleeve 109 and this will effect the spill of pressure
from the pumping chamber 24. Both metering arrangements shown in
FIGS. 5, 6 and FIGS. 7 and 8 are functionally alike and differ only
in manufacturing details.
The metering edge can also be reversed and positioned upside down
in both arrangements so that instead of having a constant port
closing for begining of injection with the variable port opening
for ending of the injection the metering element could be so
arranged as to result in a variable beginning of fuel injection and
a constant time of ending or termination of fuel injection.
When a multiple plunger fuel injection pump is assembled in the
process of manufacturing certain service adjustments have to be
made to obtain equal timing and equal delivery quantity of fuel
form all outlets. This process is known as calibration and is
accomplished as described below. Due to the accumulation of
vertical tolerances the port 8 will reach the edge 22 at camlifts
which will vary from one element to the next. In order to make sure
that the port closing occurs always at the same camlift timing,
strips 5 will be manufactured in varied thicknesses and will be
introduced into the individual pumping element assemblies through
the windows 31.
Subsequently the quantity delivered by each element will be
adjusted by means of the calibration screw 32 which is equipped on
its lower end with the timing pin 6 arranged eccentrically to its
threaded portion. An O-ring 33 located below the thread of the
adjusting screw seals the interior of the pump against fuel leakage
past the adjusting screw 32.
The lower end of the timing pin 6 registers with the forked end of
the timing strip 5. Rotating of the adjusting screw in the
clockwise or counterclockwise direction will rotate the plunger
slightly in relation to the pump housing and in relation to the
control sleeve which will alter the delivery of this particular
element. This adjustment is used to equalize the delivery of all
pump elements.
Accordingly it can be seen that the metering and timing arrangement
built into the control sleeve allows fuel injection to advance and
retard with a very small force by rotating of the control lever.
Both the timing and metering movements of the control rod can be
introduced by a single centrifugal governor in a manner similar to
the one which has been described in the above description. In
addition the manner in which the fuel quantity can be equalized and
the timing can be made uniform is also incorporated in this
invention. Accordingly the automatic timing advance is built into
the pump assembly which provides a compact fuel pump mechanism
which can be contained with the normal in line pump and governor
assembly package of a Diesel engine.
* * * * *