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Патент USA US3020912

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Feb. 13, 1962
A. G. SJCBLOM
FUEL INJECTION PU
co
Filed Dec. 29, 1958
3,020,902
FOR MULTI~CYLINDER INTERNAL
STION ENGINES
2 Sheets-Sheet 1
Feb. 13, 1962
A. G. SJGBLOM
3,020,902
FUEL INJECTION PUMP FOR MULTI-CYLINDER INTERNAL
COMBUSTION ENGINES
Filed Dec. 29, 1958
2 Sheets-Sheet 2
FIG.3
ATTORNEVS.
United States Patent'O?Fice
1
3,020,902
FUEL INJECTION PUMP FOR 'MULTI-CYLINDER
INTERNAL COMBUSTION ENGINES
Anders Georg Sjtiblom, Sommarogatan 45B,
Eskilstuna, Sweden
Filed Dec. 29, 1958, Ser. No. 783,290
4 Claims. (Cl. 123-139)
This invention relates to a fuel injection pump for
multicylinder internal combustion engines, said pump
containing a plunger performing reciprocating axial move
ment and at the same time continuous rotary movement
which is reversed with the reversing of the engine, one
part of said pump plunger being designed as a distribut
ing circular slide valve by means of which, during the
3,020,902
Patented Feb. 13, 1962
2
In the embodiment according to FIG. 1 the reference
numeral 1 designates the casing of the fuel injection
pump with a detachable intermediate part 2, a lower
part 3, and an upper part 4. The lower part 3 is
traversed by a shaft 6 which is rotatably mounted in a
bushing 5, said shaft being driven from the crank shaft
of the multi-cylinder internal combustion engine in any
suitable manner. The shaft 6 and the bushing 5 extend
through a disk 7 provided with rollers 8 acting against
10 cam faces 9 of a cam disk 10 which is driven in con
tinuous rotary motion from the shaft 6 through its part
14 which is formed as a clutch half so that the rotary
motion of the plunger is reversed when the direction of
rotation of the engine is reversed. During its rotation
pressure stroke of the pump, the fuel injectors of the 15 the cam disk 10 will also receive an axial reciprocating
engine are successively connected with the working
motion through the action of the cam faces 9 and the
chamber of the pump, and a second part of said pump
rollers 8 since a spring 11 holds the cam disk 10 with its
plunger being designed as a second circular slide valve
cam faces 9 in contact with the rollers 8. The clutch
by means of which the inlet of the pump is, during the
is very simple. The shaft 6 forms a fork between the
suction stroke of the pump, connected with the working 20
prongs of which a cross-piece 10a is disposed belonging
chamber, The invention is characterized in that said
to the disk 10. Said cross-piece moves up and down
second circular slide valve is provided with a passage
such as a groove or the like and is surrounded bytan
simultaneously with the cams 9 and transmits its move—
a number of openings corresponding to the number of
or in combination with an operating mechanism for
adapted to be connected with an inlet chamber surround
ing the sleeve valve via a communication consisting of
said groove or passage and one of said openings during
disk 10, and is, at its free end, journaled by means of a
ball bearing 12 on the intermediate part 2 of the pump.
The lower portion of the pump plunger 13 is secured
the whole of the pressure as well as the suction stroke
to the cam disk 10 and the plunger 13 will thus receive
ment to plunger 13 which is ?xed to the cross-piece by
adjustable sleeve valve, the inner cylindrical surface of
which constitutes the sliding surface for the circular slide 25 means of a pin 9a. The clutch details appear more
clearly in FIG. 6a. The disk 7 may, either separately
valve and the peripheral wall of which is perforated with
rotating a pin 22 for the sleeve valve 17, be connected
injectors, the shape and the position of said openings
with the speed regulation device of the engine. In the
being such that during operation of the pump, the work
ing chamber is, in one position of the sleeve valve, 30 embodiment shown the spring 11 rotates with the cam
of the pump plunger, while in another of the positions 35 the same motion as the cam disk, i.e. a reciprocating
axial motion and a simultaneous rotary motion around
of the sleeve valve the working chamber is connected,
its axis, The upper part of the pump plunger 13 is pro
through the said communication, with the inlet chamber
vided with an axially extending groove 16 constituting
of the pump during only part of the pressure stroke of
a part of the working chamber 24 of the pump from
the plunger and during the whole suction stroke of the
which fuel is conducted through passages 15 to the fuel
plunger, the fuel quantity and the time for the beginning
injectors of the respective engine cylinders. Fuel is
of the injection being variable by means of the sleeve
valve and an unintentional reverse motion of the engine
being prevented by the fuel being then pressed back into
conducted to the groove 16 through a passage 18 which
is shown in FIG. 1 in the form of a groove and in FIG.
the inlet chamber.
2 in the form of a hole which, except in the axial groove
According to a feature of the invention, the pump is 45 16, opens partly into the peripheral surface of the
plunger, and partly into the upper (pressure) surface of
provided with an adjustable drive device which upon
the plunger.
movement thereof will simultaneously vary the moment
The upper part of the pump plunger 13 is surrounded
for the beginning of the injection and the fuel quantity
injected in order to enable the reversing of the engine.
by a sleeve valve 17 which is adjustable about the c0m~
The invention is illustrated in the accompanying draw 50 mon axis of the sleeve valve and of the pump plunger
by means of the pin 22 and an operating member 21
ings. Two different pump types embodying the invention
which may be connected to the speed regulating device
will now be described by way of example with reference
to accompanying drawings, in which:
(not shown in the drawing) of the engine, either sepa
FIG. 1 is a longitudinal section of a pump which is of
rately or in combination with an operating mechanism
55 for rotating the disk 7 and which is shown in FIGS.
the differential plunger type;
'
FIG. 2 is a longitudinal section of a pump provided
6a and 6b. The sleeve valve 17 is prevented from axial
with a cylindrical plunger;
displacement by means of a screw 20 which is axially
FIG. 3 is a diagrammatic illustration of the plunger
bored to constitute a bearing for the pin 22. The pe
movement relatively to the sleeve valve, and a section
ripheral wall of_ the sleeve valve 17 is perforated with
on line IV-IV in this ?gure refers to FIG. 4;
' 60 openings 19 the number of which is equal to the num
FIG. 4 is a partial cross section on line IV-IV of
FIG. 1 drawn to an enlarged scale, and
FIG. 5 is a partial cross section on line V—~V of FIG.
ber of the engine cylinders. Through theopenings 19
the fuel from the inlet passage 29 and the inlet cham
ber 23 concentrically surrounding the sleeve valve 17
2 also drawn to an enlarged scale.
?ows via the passage 18 into the working chamber. The
FIG. 5a is also a partial cross section similar to FIG. 65 sleeve valve 17 is the member which varies the fuel
5 but showing a modi?ed construction for the sleeve valve.
FIG. 6a is a side elevation with certain parts shown
in section which is similar to FIG. 1 but taken at a
quantity and the moment for the beginning of the fuel
injection and prevents unintentional reversing of the
engine. Its function is clear from FIGS. 3 and 4.
In FIG. 2 the working chamber of the pump is desig
for an operating component of the pump and also the 70 nated by 24. It is in this case located above the plunger
details of a clutch mechanism, and
13 and communicates through passages 25 and 26 with
FIG. 6b shows a modi?ed detail of FIG. 6a.
the axial groove 16, and through the passages 18a with
right angle thereto. This view shows a regulating device
3,020,902
3
fuel inlet chamber 23 via the openings 19 of the sleeve
valve 17.
FIG. 3 which is a developed view of a part of the
peripheral surface of the pump plunger 13 and one of
the openings 19, shows the movement of the leading
edge of the groove 18 or passage 18a relatively to the
opening 19, said edge in the following being indicated
as point 38. Since the function of the pump plunger
will be quite the same at both openings 19 only one of
them is shown in FIG. 3. The engine is supposed to
work normally when the point 38 of the groove 18 or
passage 18a is moving from the left to the right (rep
resenting its rotary movement in the direction of the
arrow in FIG. 4). When the plunger 13 is in its lower
position, the point 38 of the groove 18 is located on
the line a-a, and when the plunger is moving upwards,
4
openings 19, the number of which openings corresponds
to the number of fuel injectors, the shape and position
of said openings being such that, during the operation,
the working chamber is connected with the inlet cham
ber 23 surrounding the sleeve valve 17 via one of said
openings 19 during an inoperative part of the pressure
stroke of the plunger which is in dependence upon the
position of the sleeve valve 17, and during the suction
stroke of the plunger. By this the fuel quantity and
the moment for the beginning of the injection are con
sequently variable by means of the sleeve valve 17, and
an unintentional reverse motion of the engine is pre
vented by the fuel being then pressed back into the inlet
chamber 23.
When the fuel supply of the engine increases, the
number of revolutions of the engine is increased at con
stantly counteracting torques, and consequently an earlier
injection of the fuel into the cylinder is required. By
At the moment when, during the upward, i.e. the pres
sure stroke of the plunger, the groove 18 or the passage " rotating the disk 7 the fuel injection can be caused to
18a is covered by the wall of the sleeve 17, and the 20 begin at the desired moment. It is seen from FIG. 3
the point 38 follows the full line, i.e. a part of a helix.
plunger presses fuel through one of the passages 15 to
an injector, but when the groove reaches the line b—b
in FIG. 3 i.e. one of the openings 19, as shown in FIG.
that if the disk 7 is rotated in such a manner that an
earlier injection is obtained, i.e. the point 27 is displaced
to a position further to the left along the line a—a, the
distance between the points 28 and 29 and thus the fuel
quantity injected will increase. An arrangement for con
trolling rotation of disk 7 in accordance with the change
in engine speed is illustrated in FIGS. 6a and 6b. In
these two views it will be seen that the operating mem
tion, and the pump sucks in new fuel from the chamber
ber 21 previously described is connected to a pulling
23 through the opening 19, until the groove 18 or the
passage 18a reaches One of the edges 19a of the open 30 rod 48 which is moved in accordance with the change
in engine speed. As the pivoted operating member 21
ings 19. The point 38 has now passed the points 27—
swings back and forth with a change in engine speed,
28—35—P in FIG. 3. Then it follows the line a-a
it actuates a crank 43 over crank pin 43a which slides
to the point 27 in front of the next opening 19 (not
in a groove 49 in the member 21. Crank 43 is con
shown in FIG. 3) where the pressure stroke and feed
nected to a vertical spindle 44 for turning the latter
injection begins again. The distance from point P‘ to
4, fuel ?ows through said opening and back into the
inlet chamber 23, and the fuel injection in the engine
cylinder ceases. The point 38 then travels downwards
along the dashed line towards the lower plunger posi
point 27 varies, of course, with the number of openings
19. However, the width B of each opening 19 may be
so adapted that the pump can perform a whole pres
sure and suction stroke while the groove 18 or the pas
about its axis, and spindle 44 is mounted in upper and
lower bearings 47 ?xed to casing 1 of the pump. The
turning movement of spindle 44 is transmitted to disk
7 and rollers 8 by means of a crank 45 secured to the
sage 18a communicates with one of the openings 19, 40 lower end of spindle 44, an arm 46 secured to sleeve
5 which in turn is secured to disk 7, and which has a
when the sleeve 17 is rotated to a position in which
pivotal motion about the sleeve axis, and a connection
the contour of the opening 19 embraces the curve C
between arm 46 and crank 45 which is constituted by
shown in FIGURE 3. This position means that no fuel
is injected into the cylinders of the engine. If the engine
a crank pin 45a which slides in a groove 50 in arm 46.
should unintentionally move in reverse, it is seen from
the dashed curve that after the reversal the groove 18
or passage 18a is connected to the opening 19 during
Thus by turning disk 7 in accordance with a change in
engine speed, the exact time of fuel injection is con
trolled. It may be observed that according to FIG. 6a,
the disk 7 is turned opposite to the direction of plunger
13. In the modi?cation shown in FIG. 6b, disk 7 will
the pressure stroke. No fuel then enters the engine
cylinder. If it is desired to reverse the engine (for ex
be turned in the same direction as plunger 13 owing to
ample, in certain marine engines) so that it moves back
wards, the position of the disc 7 must be adjusted in 50 the fact that the crank 46 in FIG. 6b has an initial posi
tion which is opposite to the position shown in FIG. 6a.
such a manner that the point 38 of the groove 18 will
Since also the sleeve valve 17 is rotatable, the moment
follow the dot and dash curve in FIG. 3 from the point
for the ending of the fuel injection and thus also the
36 on line a—a up to point 37 and then down again to
fuel quantity may be varied by means of the sleeve
line a—-a (the last part of the curve not shown). Thus,
the points 32 and 33 correspond to the points 30 and 55 valve 17. If there is exact agreement between the fuel
quantity and the moment for the beginning of the in
31 and the points 36 and 37 correspond to the points
jection, the pump can be controlled solely by rotating
27 and 35, when the engine moves in reverse. The
the disk 7. If there is no exact agreement the sleeve
angle on Which extends from the line a-a to one edge
valve 17 must also be rotated. These rotary motions
of the opening 19, and the angle 6 which denotes the
inclination of the cam disc, must be adjusted partly to 60 are preferably received from the speed regulation device
the compression character of the engine, and partly to
of the engine. The fact that by not making the edge
of the opening 19 purely axial but such that the angle
the desired design of the cams.
on becomes greater than 90°, the cam angle 5 must be
In both embodiments one part of the pump plunger
increased to get the same fuel quantity injected, is also
is thus designed as a distributing circular slide valve by
means of which, during the pressure stroke of the plunger, 65 of interest. On the other hand, the cam angle 5 can
be reduced if the angle a is made smaller than 90°, but
the fuel injectors of the engine are successively con
in this case the groove 18 must be replaced by aper
nected with the working chamber 24 of the pump, and
tures, for example, and an axial passage as in the con~
a second part of the pump plunger is designed as a sec
struction according to FIG. 2. However, in this case
ond circular slide valve by means of which the inlet
of the pump is, during the suction stroke of the pump, 70 the opening of the passage in the upper surface of the
connected with the working chamber, said second cir
cular slide valve being surrounded by the adjustable
sleeve valve 17, the inner cylindrical surface of which
constitutes the sliding surface for the circular slide valve
and the peripheral wall of which is perforated with the 75
plunger must be plugged.
FIG. 5a shows a cross section of the sleeve valve in
a modi?ed embodiment. The sleeve valve 17 has here
a (possibly several) groove or opening 40 with a com
munication passage 41 to the inlet chamber 23 to obtain
3,020,902
5
divided injection in which the supply to the fuel dis
tributor is interrupted a short time after its beginning
during part of the plunger stroke through a communi
cation of short duration between the working chamber
and the inlet chamber 23 of the plunger. Furthermore,
one or more holes 18b are bored radially through the
pump plunger so that a mouth 42 is provided for each
engine cylinder, and thus only a single opening 19, and
6
another position of said sleeve valve, said working cham
ber is placed in communication with said fuel inlet cham
ber via said passage in said second circular slide valve
and said opening in the peripheral wall of said sleeve
valve during only part of the pressure stroke of said
pump plunger and during the whole suction stroke of
said pump plunger, the fuel quantity and the time for
the beginning of the fuel injection being variable by ad
40 and 41 respectively, is required in the sleeve valve 17
justing the position of said sleeve valve, said sleeve Valve
to serve all the cylinders of the engine.
10 also serving to prevent any unintentional reverse mo
What I claim is:
tion of the engine when said sleeve valve is positioned
1. A fuel injection pump for multicylinder internal
to let said pump plunger press back the fuel into said
combustion engines, said pump containing a fuel inlet
fuel inlet chamber.
chamber, a Working chamber and a plunger performing
2. A fuel injection pump according to claim 1, charac
reciprocating axial movement relative to said working
terized by a drive device for the pump plunger, said
chamber and at the same time performing a continuous
device being adjustable in such a manner that the plunger,
rotary movement which is reversed with reversing of the
when movement occurs, at the same time varies the
engine, one part of said‘ pump plunger being constructed
moment for the beginning of the fuel injection and the
as a distributing circular slide valve by means of which,
fuel quantity in order to enable the reversing of the
during the pressure stroke of the pump, the fuel injectors 20 engine.
of the engine are successively placed in communication
3. A fuel injection pump according to claim 1, char
with said working chamber, and a second part of said
acterized in that the sleeve valve has at least another
pump plunger being constructed as a second circular
opening with a communication passage to the inlet cham
slide valve by means of which, during the suction stroke
ber to obtain divided injection, in which the supply to
of the pump, said Working chamber is placed in com 25 the fuel distributor is interruped a short time after its
munication with said fuel inlet chamber of said pump,
beginning during part of the plunger stroke through a
characterized in that second circular slide valve is pro
communication of short duration between the working
vided with a passage and is surrounded by a cylindrical
sleeve valve adjustable about the axis of said second cir
cular slide valve in a rotational but non-axial manner,
the inner cylindrical surface of said sleeve valve con
chamber and the inlet chamber of the pump.
4. A fuel injection pump according to claim 1, char
acterized in that at least one hole is bored radially
through the pump plunger so that a mouth is obtained
stituting the sliding surface for said second circular slide
for each engine cylinder and thus only a single open
valve and the peripheral wall of said sleeve valve being
ing is provided in the sleeve valve to serve all the cyl~
provided with at least one opening therethrough lead
inders of the engine.
ing to said fuel inlet chamber, the con?guration and po 35
References Cited in the file of this patent
sition of said opening being such that during operation
of the pump said working chamber is, in one position
UNITED STATES PATENTS
of said sleeve valve, placed in communication with said
fuel inlet chamber via said passage in said second circular
slide valve and said opening in the peripheral wall of 40
said sleeve valve during the whole of the pressure as well
as the suction stroke of said pump plunger, while in
2,784,670
High et a1. __________ __ Mar. 12, 1957
359,603
Great Britain __________ __ Oct. 29, 1931
FOREIGN PATENTS
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