U.S. patent number 3,827,832 [Application Number 05/298,761] was granted by the patent office on 1974-08-06 for means for reducing fuel delivery of fuel injection pumps in the low rpm range.
This patent grant is currently assigned to Robert Bosch GmbH. Invention is credited to Werner Faupel, Karl Zibold.
United States Patent |
3,827,832 |
Faupel , et al. |
August 6, 1974 |
MEANS FOR REDUCING FUEL DELIVERY OF FUEL INJECTION PUMPS IN THE LOW
RPM RANGE
Abstract
In a fuel injection pump in which the fuel quantities delivered
for injection are controlled by bypassing one part of the fuel from
the pump work chamber during the pressure strokes of the pump
piston by a control edge of a slidable member that controls a
bypass channel in an rpm-dependent manner, for reducing the
delivered fuel quantities in the low rpm range at any load
condition, said bypass channel is first opened by a throttle and
subsequently opened by said control edge.
Inventors: |
Faupel; Werner (Gerlingen,
DT), Zibold; Karl (Stuttgart-Vaihingen,
DT) |
Assignee: |
Robert Bosch GmbH (Stuttgart,
DT)
|
Family
ID: |
25761896 |
Appl.
No.: |
05/298,761 |
Filed: |
October 18, 1972 |
Foreign Application Priority Data
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|
|
|
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Oct 19, 1971 [DT] |
|
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2151884 |
Jul 14, 1972 [DT] |
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2234557 |
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Current U.S.
Class: |
417/289; 417/293;
123/503; 417/494 |
Current CPC
Class: |
F02M
41/127 (20130101); F02M 41/126 (20130101) |
Current International
Class: |
F02M
41/08 (20060101); F02M 41/12 (20060101); F02m
059/34 () |
Field of
Search: |
;417/289,494,293
;123/139AD,139AM,139AY,14FG,139AL |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
Primary Examiner: Croyle; Carlton R.
Assistant Examiner: Sher; Richard
Attorney, Agent or Firm: Greigg; Edwin E.
Claims
What is claimed is:
1. In a fuel injection pump of the known type that has (a) a
reciprocating pump piston, (b) a pump work chamber bounded by said
pump piston, (c) pressure conduit means through which fuel is
forced from said pump work chamber by said pump piston during its
pressure strokes, (d) a bypass channel leading from said pump work
chamber, (e) a slidable fuel quantity regulator member having
control edge means for opening said bypass channel at an
rpm-dependent moment during said pressure strokes for interrupting
fuel delivery to said pressure conduit means during a portion of
each pressure stroke by causing fuel to escape from said pump work
chamber through said bypass channel and (f) means for displacing
said fuel quantity regulator member to an rpm-dependent extent, the
improvement comprising a throttle in the surface of said regulator
member between said control edge means and said bypass channel when
viewed in the direction of the relative opening motion of said fuel
quantity regulator member and at least partially contiguous to said
control edge means; during the relative opening motion between said
bypass channel and said fuel quantity regulator member said bypass
channel being opened first through said throttle and subsequently
by said control edge means.
2. An improvement as defined in claim 1, wherein said throttle is
constituted by a recessed ground portion extending parallel to and
being axially bounded by said control edge means.
3. An improvement as defined in claim 1, wherein said throttle is
constituted by a bore through which said bypass channel is opened
prior to being opened by said control edge means during said
relative motion.
4. An improvement as defined in claim 3, wherein said bore
constituting said throttle is provided in said fuel quantity
regulator member, said bore having a first open end disposed at
said control edge means and a second open end situated downstream
of said control edge means when viewed in the direction of the
relative opening motion of said fuel quantity regulator member.
5. An improvement as defined in claim 1, including
A. a regulator shuttle constituting said fuel quantity regulator
member,
B. an auxiliary piston operating synchronously with said pump
piston,
C. first channel means containing hydraulic liquid and leading from
said auxiliary piston to said regulator shuttle for causing the
latter to execute forward strokes in response to the pressure
strokes of said auxiliary piston,
D. means exerting a return force on said regulator shuttle for
causing the latter to execute return strokes during the suction
strokes of said auxiliary piston,
E. second channel means leading from said regulator shuttle, said
second channel means carrying at least part of the hydraulic liquid
displaced by said regulator shuttle during its return strokes,
F. an adjustable restriction disposed in said second channel means
to brake said regulator shuttle during its return strokes; beyond
an engine rpm determined by the setting of said adjustable
restriction the braking effect of said hydraulic liquid in said
second channel means causes the appearance of a fluid abutment
preventing said regulator shuttle to return, during its
reciprocating motion, into its original position of rest,
G. an axially parallel shutoff groove provided in the lateral face
of said regulator shuttle, said shut-off groove, when aligned with
said bypass channel by virtue of rotating said regulator shuttle
into a predetermined angular position maintains communication
between said pump work chamber and said bypass channel in any
position of said regulator shuttle and
H. an annular groove provided on said regulator shuttle downstream
of said control edge means when viewed in the direction of the
pressure strokes of said regulator shuttle, said annular groove
constituting said throttle and continuously communicating with said
bypass channel through said axially parallel shutoff groove.
6. An improvement as defined in claim 1, including
A. a regulator shuttle constituting said fuel quantity regulator
member,
B. an auxiliary piston operating synchronously with said pump
piston,
C. first channel means containing hydraulic liquid and leading from
said auxiliary piston to said regulator shuttle for causing the
latter to execute forward strokes in response to the pressure
strokes of said auxiliary piston,
D. means exerting a return force on said regulator shuttle for
causing the latter to execute return strokes during the suction
strokes of said auxiliary piston,
E. second channel means leading from said regulator shuttle, said
second channel means carrying at least part of the hydraulic liquid
displaced by said regulator shuttle during its return strokes,
F. an adjustable restriction disposed in said second channel means
to brake said regulator shuttle during its return strokes; beyond
an engine rpm determined by the setting of said adjustable
restriction the braking effect of said hydraulic liquid in said
second channel means causes the appearance of a fluid abutment
preventing said regulator shuttle to return, during its
reciprocating motion, into its original position of rest,
G. a recessed portion provided on said regulator shuttle downstream
of said control edge means when viewed in the direction of the
pressure strokes of said regulator shuttle, said recessed portion
constituting said throttle,
H. an additional bypass channel extending from said first channel
means and being normally closed by said regulator shuttle,
I. an axially parallel groove provided in the lateral face of said
regulator shuttle, said groove, when aligned with said additional
bypass channel by virtue of rotating said regulator shuttle into a
predetermined angular position, maintains communication between
said first channel means and said additional bypass channel to
cause a discharge of the hydraulic liquid pressurized by said
auxiliary piston for effecting the injection of excess fuel
quantities for starting a cold engine; said control edge means and
said recessed portion on said regulator shuttle being out of
alignment with said bypass channel at any position of said
regulator shuttle when said groove is in alignment with said
additional bypass channel.
7. In a fuel injection pump of the known type that has (a) a
reciprocating pump piston, (b) a pump work chamber bounded by said
pump piston, (c) pressure conduit means through which fuel is
forced from said pump work chamber by said pump piston during its
pressure strokes, (d) a bypass channel leading from said pump work
chamber, (e) a slidable fuel quantity regulator member having
control edge means for opening said bypass channel at an
rpm-dependent moment during said pressure strokes for interrupting
fuel delivery to said pressure conduit means during a portion of
each pressure stroke by causing fuel to escape from said pump work
chamber through said bypass channel and (f) means for displacing
said fuel quantity regulator member to an rpm-dependent extent, the
improvement comprising a throttle formed contiguous with an opening
end of said bypass channel; during the relative opening motion
between said bypass channel and said fuel quantity regulator member
said bypass channel being opened first through said throttle and
subsequently by said control edge means.
8. An improvement as defined in claim 7 including a component that
contains at least part of said bypass channel, said throttle being
situated on said component upstream of said bypass channel when
viewed in the direction of the relative opening motion of said fuel
quantity regulator member.
9. An improvement as defined in claim 8 wherein said throttle is
constituted by a recessed ground portion bounding said bypass
channel.
Description
BACKGROUND OF THE INVENTION
This invention relates to a fuel injection pump for internal
combustion engines and is of the type in which the delivered fuel
quantities are altered as a function of the rpm. The delivered fuel
quantities are determined by interrupting the fuel delivery at a
certain, rpm-dependent moment during each pressure stroke of the
pump piston by means of opening a bypass channel of the pump work
chamber. The opening of the bypass channel is effected by a control
edge of a fuel quantity regulating member, such as a regulator
shuttle or a control sleeve.
In internal combustion engines the smoke generated in the low rpm
range under full load conditions is caused by an imperfect
combustion of the delivered fuel quantities. Accordingly, a number
of attempts have already been made to adapt the fuel quantities to
the actual requirements of the engine. In particular, a reduction
of the injected fuel quantities in the low rpm range is sought
after.
In a known fuel injection pump of the aforenoted type, such as
disclosed, for example, in U.S. Pat. No. 3,620,648 (German
Published Patent Application DOS 1,947,528), in addition to a first
bypass channel, there is provided a second bypass channel which is
opened by the regulator shuttle prior to opening the first bypass
channel. As long as no fluid abutment is present, however, this
second bypass channel is closed by a means provided on the pump
piston before it could be opened by the regulator shuttle. As the
fluid abutment increases, the second bypass channel is opened to an
increasing degree (the "fluid abutment" will be defined and
explained later). The control edge for controlling the second
bypass channel is preceded by a further control point which is
formed as a throttle. In the beginning stage of the fluid abutment
a discharge may occur only through this last-named throttle and
only upon a further displacement of the control plunger will the
second bypass channel be fully opened. By means of such an
arrangement the injected fuel quantities are reduced in the partial
load range and in idling and there is further achieved a smooth
transition from the unaffected full load range to the partial load
range.
For an optimal operation of an internal combustion engine, it is,
however, a requirement to inject at any load condition only that
amount of fuel which is, in fact, required by the engine. Stated
differently and as noted earlier, the injected fuel quantity has to
be adapted to the actual requirements of the engine. This applies
in particular to the low rpm range in which the vehicle engine
operates for a substantial proportion of its entire operating
period.
In a further known fuel injection pump of the above-described type,
such as disclosed, for example, in U.S. Pat. No. 3,405,700 (German
Published Patent Application DAS 1,526,500), the adaptation is
achieved by angularly adjusting, by means of a sliding setting
member which has a helically extending control edge for opening the
bypass channel. The aforenoted setting member, in turn, is shifted
by the rpm-dependent pressure in the suction chamber of the fuel
injection pump. This displacement of the setting member is effected
against the force of one or several springs of different rigidity.
In this manner an rpm-dependent adaptation of the injected fuel
quantities is achieved, whereby the accuracy of the adaptation
depends upon the number of the springs and the possibilities of
gradation regarding the stiffness of the springs. This type of
adaptation, however, results in substantial additional costs.
OBJECT, SUMMARY AND ADVANTAGES OF THE INVENTION
It is an object of the invention to provide an improved fuel
injection pump of the aforeoutlined type in which under any load
condition an rpm-dependent adaptation of the injected fuel
quantities is achieved in the low rpm range with simple means.
Briefly stated, according to the invention the bypass channel is
first opened by a control means formed by a throttle and then
opened by the conventional control edge of a sliding member. The
throttle is provided either adjacent the mouth of the bypass
channel on the component containing the latter or on the slidable
regulator member adjacent the control edge.
The aforeoutlined arrangement has the substantial advantage that by
means of an only slight structural change, the fuel quantities to
be injected are decreased in the lowest rpm range to an extent
dependent upon the design of the throttle. In case of a high rpm,
the throttle exerts, by virtue of the more pronounced throttle
effect, no substantial influence on the injected fuel quantities.
In case of a low rpm, the decrease of the injected fuel quantities
is stronger for partial load than for full load. In this manner the
generation of smoke in the lower rpm range is avoided and there is
achieved a quiet run of the internal combustion engine,
particularly in the idling and in the partial load range.
The invention will be better understood, as well as further objects
and advantages will become more apparent, from the ensuing
specification of four exemplary embodiments taken in conjunction
with the drawing.
BRIEF DESCRIPTION OF THE DRAWING
FIG. 1 is a sectional schematic view of a first embodiment of the
invention illustrating a distributor-type fuel injection pump in
which the fuel quantity regulation is effected by the principle of
"fuel abutment";
FIG. 2 is a development of the control edges of the fuel quantity
regulator member according to the first embodiment of the
invention;
FIG. 3 is a fragmentary cross-sectional view of one component
illustrated in FIG. 1;
FIG. 4 is a development of the control edge of a regulator member
according to the second embodiment of the invention finding
application in a fuel injection pump according to FIG. 1;
FIG. 5 is a development of the control edge of a regulator member
according to the third embodiment of the invention;
FIG. 6 is a diagram of the course of the injected fuel quantities
per stroke as a function of the pump rpm for different throttle
designs;
FIG. 7 is a simplified sectional view of a fourth embodiment of the
invention finding application in a distributor-type fuel injection
pump in which the fuel quantity regulation is effected by a control
sleeve arranged on the pump piston and
FIG. 8 is a fragmentary elevational view of the pump piston
illustrated in FIG. 7.
DESCRIPTION OF THE EMBODIMENTS
Turning now to FIG. 1, a pump piston 1 of a fuel injection pump
operates in a cylinder 2 and is driven in such a manner by known
means, not illustrated, that it executes a reciprocating axial
motion and a rotary motion about its axis. The reciprocating motion
serves for fuel delivery, while the roarty motion serves for fuel
distribution. During the rotary motion, during the pressure
strokes, fuel is admitted in sequence to the individual pressure
conduits 3 (only one shown) which are arranged uniformly spaced
about the cylinder 2. In each of the pressure conduits 3 there is
situated a check valve 4. On the lateral surface of the piston 1
there is provided an axially parallel distributor groove 5 which,
during each successive pressure stroke of the piston, connects the
pump work chamber 6 with another pressure conduit 3. The pump work
chamber 6 is supplied with fuel through a channel 7, an annular
groove 8, one of longitudinal grooves 9 provided on the lateral
surface of the piston 1, and a supply channel 10 which communicates
with a suction chamber 11. The latter, in turn, is supplied with
fuel by means of a fuel delivery pump 12 which may be a gear pump
driven by the engine that is served by the fuel injection pump.
In order to maintain an rpm-dependent pressure in the suction
chamber 11, the latter is connected with the suction channel 13 at
the intake side of the delivery pump 12 by means of a channel 14
containing a throttle 15, the flow passage section of which is
controlled by a piston plunger 16. The latter is, at one side,
exposed to the fuel pressure which prevails in the suction chamber
11. As the rpm increases, the piston plunger 16 is displaced
against the force of a return spring 17. As a result, the flow
passage section of the throttle 15 is increased.
For the quantity control of the fuel delivered by the piston 1 to
the engine during the pressure strokes, there is provided a
regulator shuttle 18. The latter controls a bypass channel 19a, 19b
by controlling in an annular space 20 communication between the
bypass channel portion 19a and the bypass channel portion 19b. The
bypass channel 19a, 19b leads from the pump work chamber 6 to the
suction chamber 11. The bypass channel portion 19a is in continuous
communication with the annular chamber 20 in every position of the
regulator shuttle 18. The bypass channel portion 19b is connected
with the suction chamber 11 through a channel 21. A regulator
spring 22 seeks to maintain the regulator shuttle 18 in its
position of rest which is determined by the cooperation of a solid
fixed abutment 23 forming part of the pump housing and a collar 24
affixed to the regulator shuttle 18. In this position of rest the
latter maintains the bypass channel portion 19b closed.
For the purpose of moving the regulator shuttle 18 away from its
above-described position of rest, there is provided an auxiliary
piston 25 which operates synchronously with the piston 1 and which
is preferably formed as a stepped piston portion of the piston 1.
The auxiliary piston 25 displaces fuel from its cylinder through
longitudinal grooves 26 arranged on the lateral face of the piston
25 and a channel 27 which contains a check valve 28 and which opens
into a cylinder 29 accommodating the regulator shuttle 18. Thus, by
virtue of the fuel pressure generated immediately to the left of
the regulator shuttle 18 by the auxiliary piston 25, the regulator
shuttle 18 is displaced towards the right against the force of the
spring 22, whereby hydraulic communication is established between
the bypass portions 19a and 19b.
During the period between two pressure strokes of the piston 25,
the regulator shuttle 18 returns to its position of rest, driven
thereinto by the spring 22. During this return motion the regulator
shuttle 18 displaces one portion of the fuel present in the
cylinder 29 through a channel 31 in which there is disposed a
regulator throttle 30 braking the return motion of the control
shuttle 18. The free flow passage section of the regulator throttle
30 is adjustable by a throttle needle 32 or the like. At a given
flow passage section above a determined pump speed (that is, engine
rpm), a fluid abutment appears which means that the regulator
shuttle 18 does no longer return to its fixed position of rest at
the end of its return motion. Stated differently, the starting and
terminal point of the reciprocating motion of the regulator shuttle
18 will be spaced from its fixed position of rest and will shift to
the right (towards the spring 22) as the rpm further increases. In
this manner the fuel quantity which is delivered during each
pressure stroke of the pump piston to the fuel injection nozzles
through the pressure conduits is decreased.
If the throttle 30 is widened, for example, during full load or
partial load, then the initial and terminal point of the
reciprocating motion of the control shuttle 18 shifts in an
opposite direction (that is, towards the left) until the control
shuttle 18 again engages the abutment 23. If, on the contrary, the
flow passage section of the throttle 30 is decreased corresponding
to a lower partial load or zero load, then the starting and
terminal point of the reciprocating motion of the control shuttle
18 travels correspondingly faster in the direction of the regulator
spring 22. The maximum excursion of the control shuttle 18 is
obtained when the latter opens with its trailing edge a bypass
channel 34 which directs the residual fuel quantity displaced by
the piston 25 into the suction chamber 11.
The annular chamber 20 is bounded by a control edge 35 adjacent
which there is disposed a control means 37 constituted by a
throttle 36 by means of which, in the working position of the
control shuttle 18, the channel 19b is opened earlier than it is by
the control edge 35. Thus, when viewed in the direction of shuttle
travel caused by the fuel pressure in the cylinder 29, the throttle
36 is disposed immediately downstream of the control edge 35. In
this manner, even before the control edge 35 reaches the channel
19b, fuel is already drained from the pump work chamber, whereby
the entire injected fuel quantity is decreased. The faster the
opening step occurs as the rpm increases, the stronger will be the
throttle effect, so that in case of a high rpm, it is substantially
only the control edge 35 which determines the moment of opening the
channel 19b.
In order to obtain an excess fuel quantity for starting the engine,
the control shuttle 18 has at its land portion which is remote from
the regulator spring 22, a longitudinal groove (starting groove) 38
which, when the control shuttle 18 is rotated by means not shown,
establishes hydraulic communication between the cylinder 29 and the
bypass channel 34. In this manner, during the phase of engine
start, the fuel delivered by the auxiliary pump 25 flows through
the channels 34, 21 into the suction chamber 11 without displacing
the regulator 18. Thus, in this operational condition the throttle
36 is inoperative. In this embodiment, the throttle 36 is, with
regard to the starting groove 38, so positioned adjacent the
control edge 35 that in the rpm range which immediately follows the
starting phase, the bypass channel portion 19b is not opened
prematurely.
For the purpose of completely interrupting fuel delivery during the
operation of the fuel injection pump, the regulator shuttle 18 has
at its land portion oriented towards the regulator spring 22, a
longitudinal groove 39 (cutoff groove) which, upon proper angular
displacement of the regulator shuttle 18, establishes
communication, in a manner known by itself and therefore not shown
here, between the annular chamber 20 and the bypass channel portion
19b. As a result, the entire delivered fuel is directed through the
channel 21 into the suction chamber 11, thus bypassing the pressure
conduits 3.
Turning now to FIG. 2, there is shown a development of the
regulator shuttle 18 with the cutoff groove 39, the starting groove
38, as well as the throttle 36 constituting the control means 37.
The throttle 36 is constituted by a ground portion 36a extending
parallel to the control edge 35 and axially bounded thereby. The
ground portion 36a has a width b and a depth t, as illustrated in
FIG. 3. Instead of the ground planar portion 36a shown in section
in FIG. 3, the throttle 36 may be of any other shape; for example,
it may be of annular configuration. It is apparent from FIG. 2 that
in the absence of the throttle 36a the regulator shuttle 18 would
start to open the bypass channel portion 19b only after a shuttle
stroke s, while in the presence of the throttle 36 such opening
already starts after a shorter shuttle stroke s'.
As the fluid abutment increases (that is, it travels to the right
as viewed in FIG. 1), the stroke s' decreases and thus there is
also a decrease in the width of the sealing piston land between the
bypass channel portion 19b and the annular chamber 20. The thus
appearing leakage losses in the lower rpm range reduce the injected
fuel quantities, so that under partial load conditions there will
be a stronger adaptation of the fuel quantities than in case of
full load and, in particular, there is attained a "silent" idling
of the engine.
FIG. 6 illustrates schematically how the throttle 36 affects the
injection quantity Q at different rpm's. The curve formed of curve
portions Q.sub.st and Q.sub.n corresponds to a regulator shuttle
without a throttle; the curve portion Q.sub.st illustrates the
excess fuel quantity for starting. Dependent upon the size and
shape of the throttle 36, there are obtained different curve
portions such as Q.sub.s1, Q.sub.s2, Q.sub.s3 adjoining the curve
portion Q.sub.st. The curve portion Q.sub.s3 is obtained from the
curve Q.sub.s1 if, for example, in the throttle 36a the depth t of
the ground portion is increased. Q.sub.s2 is obtained from the
curve Q.sub.s1 if, for example, in the throttle 36a the width b of
the ground portion is enlarged.
The throttle 36 may be formed as an annular groove 36b which is in
communication in a tangential direction through the cutoff groove
39 with the annular chamber 20 as shown in the developed
illustration of FIG. 4.
FIG. 5 shows a development of a regulator shuttle wherein adjacent
the control edge 35 there is provided a throttle in the form of a
radial bore 36c which effects communication with the annular
chamber 20 through an axial bore 40.
In FIG. 7 there is schematically illustrated a fuel injection pump
in which the injected fuel quantity is determined by means of a
control sleeve. In a cylinder 102 provided in the housing of a fuel
injection pump there operates a pump piston 101 which is driven by
known and therefore not illustrated means in such a manner that it
executes an axial reciprocating motion and a rotary motion about
its axis. The reciprocating motion serves for fuel delivery, while
the rotary motion serves for fuel distribution. As a result of the
rotary motion, during the pressure strokes, fuel is admitted
sequentially to the individual pressure conduits 103 which are
arranged uniformly spaced about the cylinder 102. Each pressure
conduit 103 leads to a non-illustrated fuel injection valve of the
internal combustion engine. The number of the pressure conduits 103
is equal to that of the cylinders of the internal combustion engine
which is served by the fuel injection pump. In the cylinder 102 the
pump piston 101 bounds a pump work chamber 106 which during the
suction stroke of the pump piston is supplied with fuel from the
suction chamber 111 through longitudinal grooves 109 provided in
the lateral face of pump piston 101 and a supply channel 110. The
longitudinal grooves 109 are equal in number to that of the
pressure conduits 103 and merge into the pump work chamber 106.
From the pump work chamber 106 there extends a bore 141 which
merges into a compartment 142. The mouth of the bore 141 is formed
as a valve seat and is closable by a valve body 143 which is loaded
by a spring 144 accommodated in the compartment 142. From the
latter there extends a conduit 145 which merges into the cylinder
102 in a plane situated between the entry of the supply channel 110
and the entry of the pressure conduits 103 into the cylinder
102.
The pump piston 101 has an annular groove 108 which communicates
with a longitudinal distributor groove 105 provided on the lateral
face of the pump piston 101. For each pressure stroke of the pump
piston 101 a different pressure conduit 103 is connected with the
conduit 145 through the distributor groove 105. The latter can be
connected with one of the pressure conduits 103 only if the
longitudinal grooves 109 are not in communication with the supply
conduit 110.
The pump piston 101 has an axial blind bore 107 which at one end
communicates with the pump work chamber 106 and at the other end is
intersected by a radially extending throughgoing bore 146. In the
zone of the latter there is disposed a control sleeve 118 which is
slidably mounted in a fluid-tight manner on the piston 101.
Dependent upon the position of the control sleeve 118, during the
pressure strokes of the pump piston the bore 146 is opened by the
upper edge 118a of the control sleeve 118 at an earlier or later
moment so that a certain variable residual quantity of the
delivered fuel may flow into the suction chamber 111 from the pump
work chamber 106 through the bores 107, 146. In case the control
sleeve 118 is set in such a manner that the bore 146 is not
uncovered at all during the pressure strokes of the pump piston
101, then the entire fuel quantity delivered by the pump piston
(excessive fuel quantity for engine start) will be directed into
the pressure conduits 103. The displacement of the control sleeve
118 is effected by a lever 148 which is pivotable about a
stationary point 149 and has a nose 150 which projects into a
depression 151 provided in the control sleeve 118. The lever 148 is
displaceable as a function of load and rpm by means not shown.
In order to obtain in the suction chamber 111 an rpm-dependent
pressure, the fuel supply is effected -- in the same manner as
described in connection with the first embodiment in FIG. 1 --
through a pump 112 while the pressure of the suction chamber is
regulated by means of a piston 116 which is loaded by a spring 117
and which controls a throttle 115 situated in a return channel
114.
According to the invention, in the fuel injection pump illustrated
in FIG. 7, there is provided on the piston 101, immediately
adjacent the opening of the bore 146, a ground portion which
constitutes a throttle 136. In this manner, during each pressure
stroke of the piston 110 the pump work chamber is first discharged
through the throttle 136 and then, after an additional axial
displacement of the pump piston 101, it is discharged through the
bore 146. Thus, there is obtained, in a manner similar to that
already discussed in connection with the type of pump shown in FIG.
1, an adaptation of the fuel injection quantities as a function of
the rpm, particularly in the low rpm range.
Turning now to FIG. 8 there is shown an elevational view of that
side of the pump piston 101 which contains the throttle 136 and the
outlet plane of the bore 146. In this embodiment the plane of the
ground portion 136 is at an angle with respect to the longitudinal
axis of the pump piston 101; it is to be understood that the
throttle may be formed as a ground portion which is parallel to the
longitudinal axis of the pump piston. Further, the throttle may
also be provided on the inner lateral face of the control sleeve
118 in the vicinity of the upper control edge. This solution,
however, involves more complex machining. The arrangement and
formation of the throttle described in connection with FIGS. 4 and
5 may also be adapted in case of the piston illustrated in FIG.
8.
It is thus seen that in fuel injection pumps in which the injected
quantities are controlled by sliding elements which regulate a
bypass, there is achieved in the low rpm range for any load a
reduction of the injected fuel quantities by providing a throttle
at a particular location by simple means. The course of the
injected fuel quantity as a function of the rpm is determined by
the particular shape of the throttle. At higher rpm's there may be
obtained, however, the original level of injection since, as the
rpm increases, the fuel quantities which pass through the throttle
are decreased.
* * * * *