U.S. patent number 3,758,241 [Application Number 05/277,116] was granted by the patent office on 1973-09-11 for fuel injection pump for multi-cylinder internal combustion engines.
This patent grant is currently assigned to Robert Bosch GmbH. Invention is credited to Franz Eheim.
United States Patent |
3,758,241 |
Eheim |
September 11, 1973 |
FUEL INJECTION PUMP FOR MULTI-CYLINDER INTERNAL COMBUSTION
ENGINES
Abstract
In a fuel injection pump a pump-and-distributor member is
axially movably and rotatably disposed between two axially parallel
compression springs which are spaced apart 180.degree. with respect
to the pump axis and which, through a common yoke, oppose the
pressure strokes of said member. A control sleeve is slidably and
rotatably arranged on said pump-and-distributor member for altering
the starting moment and the period of injection. The angular and
axial displacement of the control sleeve is effected by actuating
elements connected to said control sleeve and arranged radially
outwardly thereof.
Inventors: |
Eheim; Franz (Stuttgart,
DT) |
Assignee: |
Robert Bosch GmbH (Stuttgart,
DT)
|
Family
ID: |
5817809 |
Appl.
No.: |
05/277,116 |
Filed: |
August 1, 1972 |
Foreign Application Priority Data
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Aug 26, 1971 [DT] |
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P 21 42 704.3 |
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Current U.S.
Class: |
417/494; 123/449;
417/499; 417/500; 123/503 |
Current CPC
Class: |
F02M
41/126 (20130101); F02M 41/121 (20130101) |
Current International
Class: |
F02M
41/08 (20060101); F02M 41/12 (20060101); F04b
007/04 (); F04b 007/06 (); F04b 039/10 () |
Field of
Search: |
;417/494,499,500,492
;123/139AL,139AP,139R |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
Primary Examiner: Croyle; Carlton R.
Assistant Examiner: Gluck; Richard E.
Claims
That which is claimed is:
1. In a fuel injection pump serving a multi-cylinder internal
combustion engine and being of the known type that has (a) a
pump-and-distributor member, (b) means for continuously rotating
said pump-and-distributor member, (c) means causing said
pump-and-distributor member to periodically execute pressure
strokes, (d) means continuously exerting an axially directed force
on said pump-and-distributor member, said force opposing the
displacement thereof in executing said delivery strokes, (e) at
least one control sleeve slidably mounted on said
pump-and-distributor member, (f) groove means provided on said
pump-and-distributor member and cooperating with said control
sleeve to control, dependent upon the position of the latter, the
fuel injection during each said pressure stroke, the improvement
comprising,
A. a plurality of spaced compression springs disposed axially
parallel and adjacent said pump-and-distributor member,
B. means connecting said springs to said pump-and-distributor
member, said springs constituting said means continuously exerting
an axially directed force on said pump-and-distributor member
and
C. setting means passing through the space between two adjacent
springs and connected to said control sleeve to displace the
same.
2. An improvement as defined in claim 1, said springs being two in
number and being spaced apart 180.degree. with respect to the axis
of said pump-and-distributor member.
3. An improvement as defined in claim 1, said means connecting said
springs to said pump-and-distributor member being formed of a sole
yoke supporting one end of said springs and including means
engaging said pump-and-distributor member.
4. An improvement as defined in claim 3, including a disc means
affixed to said pump-and-distributor member and having an annular
surface of spherical configuration, said means engaging said
pump-and-distributor member and forming part of said yoke including
a complemental spherical surface in engagement with said disc
means.
5. An improvement as defined in claim 3, including means securing
said yoke against rotation.
6. An improvement as defined in claim 5, said lastnamed means being
formed of axially parallel fixed guiding pins passing through said
yoke.
Description
This invention relates to a fuel injection pump particularly for a
multi-cylinder internal combustion engine and is of the type that
has an axially reciprocating and simultaneously rotating
pump-and-distributor member, a cam mechanism causing the axial
displacements of the pump-and-distributor member against a return
force and at least one control sleeve surrounding the
pump-and-distributor member and slidable on the lateral face
thereof. For the purpose of altering the beginning and/or the
terminal moment of fuel delivery of the fuel injection pump, the
control sleeve cooperates with a channel having its terminal
opening on the lateral face of the pump-and-distributor member.
In fuel injection pumps of the aforenoted type, such as disclosed,
for example, in U. S. Pat. No. 2,813,523, the return force for the
pump-and-distributor member is generally supplied by a coil-type
compression spring which is arranged beneath the
pump-and-distributor member coaxially therewith. In this manner the
control sleeve is radially accessible for actuating members. Such a
structure, however, results in a relatively large axial dimension
of the fuel injection pump.
It is an object of the invention to provide an improved fuel
injection pump of the aforenoted type which has a reduced axial
dimension permitting nevertheless an easy radial access of the
actuating members to the control sleeve.
Briefly stated, according to the invention, the resilient return
force is supplied by at least two compression springs which are
arranged axially parallel with respect to, and uniformly spaced
apart from the pump-and-distributor member, so that the control
sleeve is adapted to reciprocate between the two compression
springs.
The invention will be better understood, as well as further objects
and advantages become more apparent, from the ensuing detailed
specification of a preferred, although exemplary, embodiment of the
invention taken in conjunction with the drawing wherein:
FIG. 1 is an axial sectional view of the fuel injection pump
according to the preferred embodiment;
FIG. 2 is a partial axial sectional view along line II--II of FIG.
1; and
FIG. 3 is a partial sectional view along line III--III of FIG.
2.
Turning now to FIG. 1, in a housing 1 of a fuel injection pump for
a multi-cylinder internal combustion engine there journals a drive
shaft 2 to which there is keyed a radial cam disc 3. The latter
carries as many cams 4 as there are cylinders in the internal
combustion engine. The cam track of the cam disc 3 is engaged by
rollers 5 which journal on pins 6. The latter, in turn, are
supported in a bearing ring 7 which is inserted in the pump housing
1. A pump-and-distributor member 8 carries at its driven end a
collar 9 which is coupled with the cam disc 3 by means of a pin 10.
On the collar 9 there are disposed, in a stacked relationship, two
sliding discs 11 and an upwardly spherical disc 12.
Also referring now to FIG. 2, there is provided a bar-like yoke 13
having a central concave face which is complemental to the convex
spherical face of the disc 12 and is in a face-to-face engagement
therewith. The yoke 13 is engaged by one end of two coil-type
compression springs 14 which, at their other end, are supported,
through spring seat discs 16, by a radial face of a pump body 15
which fits into the opening of the pump housing 1. As best seen in
FIG. 3, the two springs 14 are spaced apart 180.degree. with
respect to the axis of the pump-and-distributor member 8. By means
of the aforedescribed structure, the springs 14 exert an axial
force on the pump-and-distributor member 8. It is noted that by
providing a common yoke 13 for both compression springs 14,
manufacturing tolerances in the latter are compensated. In the pump
body 15 there are press-fitted two axially parallel guiding pins 17
which project through openings 18 provided in the yoke 13 and thus
secure the latter against rotation. It is thus seen that the cam
disc 3 is pressed against the rollers 5 under the effect of the
springs 14.
The pump-and-distributor member 8 reciprocates and rotates in a
cylindrical sleeve 19 which is firmly inserted into the pump body
15. The latter is closed at its external end by a threaded closure
21 which presses a valve seat body 22 against a axial end face of
the cylindrical sleeve 19. In the valve seat body 22 there is
slidably arranged a valve member 23 which in its closed position is
pressed against the valve seat body 22 by means of a spring 24.
The inner chamber 26 defined by the pump housing 1 is filled with
low-pressure fuel from a source, not shown. From the chamber 26
there extends a channel 27 which leads to an inlet port 28 passing
through the cylindrical sleeve 19. The port 28 cooperates with
axially parallel grooves 29 provided in a terminal portion of the
pump-and-distributor member 8. The grooves 29 communicate with the
pump work chamber 30 which is closed by the pressure valve 22, 23.
From the inner cavity defined by the threaded closure 21 and
disposed downstream of the pressure valve 22, 23, there extends a
channel 31 which is formed in the valve body 22 and in the wall of
the cylindrical sleeve 19. The channel 31 merges into a radial
channel 32 passing through the cylindrical sleeve 19. The channel
32 cooperates with an annular groove 33 in the pump-and-distributor
member 8. From the annular groove 33 there extends in the
pump-and-distributor member 8 a distributor groove 34 which
cooperates with outlet channels 35 (only one shown). Each output
channel 35 is arranged radially in the cylinder sleeve 19 and in an
inclined manner in the pump body 15 and merges into an associated
outlet opening 36 to which there is coupled an injection conduit
(not shown) leading to an injection nozzle (also not shown) of the
internal combustion engine. Similarly to the cams 4 of the cam disc
3, the axial grooves 29 and the outlet channels 35 together with
the outlet openings 36 are equal in number to the cylinders of the
internal combustion engine.
From the pump work chamber 30 there extends, within the
pump-and-distributor member 8, an axial channel 38 to two radial
channels 39 and 40 which merge into control grooves 41 and 42,
respectively. The control grooves 41 and 42 are provided in the
lateral face of the pump-and-distributor member 8 and cooperate
with radial control bores 37 which, in turn, are formed in a
control sleeve 43 which surrounds the pump-and-distributor member 8
and is axially and rotatably slidable thereon. The number of the
control bores 37 is equal to the number of the cylinders in the
internal combustion engine. The control groove 41 extends helically
with respect to the axis of the pump-and-distributor member 8 while
the control groove 42 extends parallel thereto.
For the axial displacement of the control sleeve 43 there serves an
eccentrically supported radial pin 44 which projects into a
transversal groove 45 provided on the control sleeve 43. For the
rotary motion of the latter there serves an eccentrically supported
radial pin 46 which projects into an axially parallel longitudinal
groove 47 provided in the control sleeve 43. The eccentric pins 44
and 46 may be arbitrarily operated by setting shafts 49 and 48,
respectively, or by adjusting means (not shown) as a function, for
example, of the rpm of the internal combustion engine.
The aforedescribed fuel injection operates in the following
manner:
When the internal combustion engine is running, the rotating drive
shaft 2 of the fuel injection pump and the rotating cam disc 3
generate an axial reciprocating motion and a simultaneous rotary
motion of the pump-and-distributor member 8 which is shown in the
figures in its lower dead center position. During this operation
the cam disc 3 is maintained in continuous contact with the rollers
5 by the force of the return springs 14. The pump work chamber 30
is charged with fuel entering through the inlet port 28. As the cam
disc 3 rotates, first the inlet port 28 is closed. During the
subsequent effective pressure stroke of the pump-and-distributor
member 8, the fuel is delivered from the pump work chamber 30
through the open pressure valve 22, 23 and the channels 31, 32 into
the annular groove 33 and therefrom through the distributor groove
34 into one of the outlet channels 35 and the associated coupling
opening 36. Therefrom the fuel is admitted to a fuel injection
nozzle of the internal combustion engine.
The beginning and the end of the fuel delivery is determined by the
control grooves 42 and 41, respectively. Assuming that the
pump-and-distributor member 8 rotates in the direction of the arrow
A, the effective pressure stroke begins when the groove 42 leaves
the associated control bore 37 and terminates when the groove 41
arrives into alignment therewith.
The duration of injection and thus the quantity of the injected
fuel may be varied by an axial displacement of the control sleeve
43, because in this manner the arcuate distance between the grooves
41 and 42 measured at the height of the radial control bores 37 is
altered while the moment of injection start remains the same. The
control sleeve 43 is axially displaced by rotating the adjusting
shaft 49. The beginning moment of the injection may be varied by an
angular displacement of the control sleeve 43, because in this
manner the relative position between the control bores 37 and the
control groove 42 is altered, while the aforenoted arcuate distance
between the control grooves 41 and 42 remains the same. The control
sleeve 43 is angularly displaced by turning the setting shaft
48.
Turning now to FIG. 3, it is seen that the control sleeve 43 which
is movable between the compression springs 14 is easily accessible
by the components 44 and 46 arranged radially and necessary for its
actuation. By virtue of arranging the control sleeve 43 between the
compression springs 14, there is achieved a reduction in the axial
dimension of the fuel injection pump.
Instead of a sole control sleeve which serves for independently
controlling both the fuel quantities and the starting moment of the
fuel injection, there may be provided two control sleeves, one
controlling the beginning of the fuel injection while the other
controlling the terminal moment thereof.
* * * * *