[0001] This invention relates to a fuel injection nozzle for supplying fuel to an internal
combustion engine, the nozzle comprising a valve member defining a surface against
which fuel under pressure supplied to an inlet can act to lift the valve member away
from a seating against the action of resilient means, the valve member when lifted
from the seating allowing a flow of fuel from the inlet to an outlet, a piston member
defining a surface against which fuel under pressure from the inlet can act, the piston
member acting to assist the initial movement of the valve member against the action
of the resilient means and stop means for limiting the movement of the piston member.
[0002] Fuel injection nozzles of the aforesaid kind provide for two stage lifting of the
valve member away from the seating, the first stage of lift being such as to allow
a fuel flow to the combustion chamber of the associated engine at a restricted rate
and the second stage of lift allowing fuel flow at a substantially unrestricted rate.
The fuel pressure required to lift the valve member from its seating is known in the
art as the nozzle opening pressure and is lower than the fuel pressure required to
lift the valve member through the second stage of lift.
[0003] The nozzle opening pressure depends upon the force exerted by the resilient means
and the areas of said surfaces of the valve member and piston member exposed to the
fuel pressure at the inlet. The pressure required to move the valve member alone depends
upon the force exerted by the resilient means and the area of said surface although,
when the valve member has been lifted from the seating the area of the valve member
exposed to fuel pressure is slightly increased since a portion of the valve member
is shielded from the fuel pressure when the valve member is in contact with the seating.
[0004] Fuel injection nozzles of the aforesaid type are known from British Patent Specification
1531580. In two of the examples described in the aforesaid specification the piston
member is constituted by one or more pistons slidable in a bore or respective bores.
In each example one end surface of the piston or pistons is exposed to the fuel pressure
at the fuel inlet of the nozzle and the other end or ends of the piston engage the
valve member or an abutment for the aforesaid resilient means. In the other two examples
described in the specification the piston member is in the form of a slidable sleeve
which surrounds the valve member and again one end surface of the sleeve is exposed
to the pressure of fuel at the fuel inlet of the nozzle and the other end of the sleeve
engages either the valve member or the aforesaid abutment.
[0005] A similar type of injection nozzle is shown in GB2145468B in which the piston member
is in the form of a sleeve which engages with the valve member. In some applications
for nozzles of the aforesaid kind, it is required that the increase in fuel pressure
which is required to move the valve member through the second stage of movement should
not be appreciably higher than the nozzle opening pressure in order to reduce the
risk of the valve member being lifted from its seating by the action of reflected
pressure waves in the pipelines connecting the fuel inlet of the nozzle to the associated
fuel injection pump and also to reduce the risk of gas blow by which is the lifting
of the valve member from its seating by the pressure of gases in the associated combustion
chamber of the engine. These risks can be minimised by raising the nozzle opening
pressure and the pressure required to lift the valve member through the second stage
of movement, however, the latter pressure could then be undesireably high.
[0006] In order to reduce the difference between the two pressures, the areas of the piston
member which are exposed to the fuel pressure can be reduced. However, in the case
of the sleeve the reduced section can cause problems firstly in the production of
the sleeve and secondly in that the thinner the section of the sleeve the more likely
it is to be distorted either due to hydraulic forces or mechanical forces. Moreover,
the area of the sleeve for engagement with the valve member or the abutment, is reduced
unless the sleeve is provided with a flange. In the case of the piston the diameter
can be reduced but again there is a risk of distortion occuring.
[0007] The object of the present invention is provide a fuel injection nozzle of the aforesaid
kind in a simple and convenient form.
[0008] According to the invention in a nozzle of the kind specified the piston member has
a stepped peripheral surface and is slidable in a stepped cylinder the stepped portion
of the cylinder being relieved to define an annular chamber which is connected to
the fuel inlet and the end surface of the piston member being exposed to the same
pressure.
[0009] A example of a fuel injection nozzle in accordance with the invention will now be
described with reference to the accompanying drawings in which:-
Figure 1 is a sectional side elevation showing a substantial part of the nozzle, and
Figure 2 is a view to an enlarged scale of a portion of the nozzle seen in Figure
1.
[0010] Referring to the drawings the injection nozzle comprises a stepped nozzle body 10
which is secured to a tubular elongated nozzle holder 11. Intermediate the holder
and the nozzle body is a distance piece 12 and the aforesaid components are held in
assembled relationship by means of a cap nut 13.
[0011] The nozzle body defines a blind bore 14 at the blind end of which there is formed
a seating 15 which leads into a sac volume from which extends an outlet orifice 16.
Intermediate the ends of the bore 14 there is defined an annular chamber 17 which
is connected to a fuel inlet passage 18 extending through the distance piece and the
holder to a fuel inlet (not shown) which in the use of the nozzle, is connected by
a pipeline to the outlet of a fuel injection pump.
[0012] Within the bore 14 there is located a valve member 19, the portion of the valve member
lying between the chamber 17 and the seating being of reduced diameter so as to define
with the wall of the bore, an annular clearance. The portion of the valve member between
the chamber 17 and the open end of the bore is a sliding fit with the wall of the
bore. The inner end of the valve member is shaped for co-operation with the seating
and the opposite end of the valve member extends from the bore the latter adjacent
the distance piece 12, being enlarged to accommodate a flange 20 formed on the valve
member.
[0013] The holder 11 defines a cylindrical chamber 21 in which is located a coiled compression
sprng 22. The end of the spring remote from the distance piece is engaged with a suitable
spring abutment which may be adjustably mounted in the holder. The end of the spring
22 closer to the distance piece is engaged with a spring abutment 23 which is in engagement
with the end of the valve member 19 remote from the seating.
[0014] The distance piece 12 defines a bore 24 in which is slidably mounted a piston member
in the form of a sleeve 25. As is clearly shown in the drawings the sleeve 25 is of
stepped form with the narrower end located adjacent the nozzle body. The bore 24 is
also stepped but the step in the bore is relieved so as to define an annular chamber
26 surrounding the sleeve, the chamber 26 communicating by way of a drilling 27 with
the portion of the passage 18 lying within the distance piece. The diameter of the
narrower end of the sleeve is slightly greater than the diameter of the enlarged portion
of the bore 14 in the nozzle body so that a step is defined which acts to limit the
downward movement of the sleeve. In the closed position of the valve member as shown,
a clearance indicated by the reference letter A exists between the flange 20 on the
valve member and the adjacent end of the nozzle body. Moreover, the reference letter
B indicates the amount by which the spring abutment 23 projects beyond the end of
the holder in the closed position of the valve member. Furthermore, with the narrower
end of the sleeve 25 resting on the nozzle body 10 a small clearance indicated by
the reference letter C exists between the wider end of the sleeve and the spring abutment.
The end portion of the spring abutment 23 which engages the valve member, overhangs
the valve member so that it can be engaged by the sleeve 25 as will be described.
[0015] The bore in the sleeve is larger in diameter than the valve so that a clearance exists
between the valve member and the sleeve, the clearance communicating with the enlarged
portion of the bore 14 which accommodates the flange 20 and also by way of a drilling
28 in the abutment 23 and a groove in the end face of the valve member or spring abutment,
with the chamber 21 which accommodates the spring. This chamber in use, is connected
to a drain. It will be understood that the opposite end surfaces of the sleeve are
exposed to the same pressure.
[0016] In operation, when fuel under pressure is supplied through the fuel inlet, the fuel
pressure acts upon the valve member to produce a force acting to lift the valve member
away from the seating. In addition, the fuel under pressure supplied to the annular
chamber 26 produces by virtue of the difference in the diameters of the sleeve 25,
a force acting upwardly which causes the sleeve to move upwardly to take up the clearance
C, into engagement with the spring abutment so that the force is applied to the spring
abutment 23. The forces acting on the valve member and sleeve are therefore in the
same direction and when the fuel pressure rises to a sufficient value, the force exerted
by the spring 22 is overcome and the valve member is lifted from its seating to allow
flow of fuel from the chamber 17 through the outlet orifice 16. The extent of movement
of the valve member is determined by the clearance B because when the sleeve 25 engages
with the holder 11 the force acting on the sleeve due to the fuel pressure is no longer
transmitted to the spring abutment. This limited movement of the valve member allows
by virtue of the throttling effect of the small gap between the valve member and its
seating, a restricted flow of fuel to the associated engine. As the fuel pressure
at the inlet continues to increase, the fuel pressure acting on the valve member will
eventually produce a force which is sufficient to move the valve member against the
action of the spring and the valve member will move to its fully open position in
which the flange 20 engages the sleeve 25. The maximum movement of the valve member
from the closed position to the fully open position is therefore the sum of the clearances
A, B and C and the movement of the valve member in the first stage is equal to the
clearance B. When the fuel pressure at the inlet falls, the valve member will return
to the closed position and the sleeve due to the residual fuel pressure will tend
to remain in contact with the spring abutment 23.
[0017] By providing the step on the periphery of the sleeve the force developed on the sleeve
due to the fuel pressure at the fuel inlet can be easily adjusted by varying the difference
in diameters of the wider and narrower portions of the sleeve. At the same time the
wall of the sleeve can have sufficient thickness to enable it to withstand hydraulic
and mechanical forces.
[0018] As shown in the drawings the nozzle body 10 is of two piece construction. It can
of course be formed from a single piece of material.
[0019] If desired, the distance piece 12 can be formed integrally with the nozzle body.
1. A fuel injection nozzle for supplying fuel to an internal combustion engine comprising
a valve member (19) defining a surface against which fuel under pressure supplied
to an inlet can act to lift the valve member away from a seating (15) against the
action of resilient means (22), the valve member when lifted from the seating allowing
a flow of fuel from the inlet to an outlet (16), a piston member (25) defining a surface
against which fuel under pressure from the inlet can act, the piston member acting
to assist the initial movement of the valve member (19) against the action of the
resilient means (22) and stop means for limiting the movement of the piston member,
characterised in that said piston member (25) has a stepped peripheral surface and
is slidable in a stepped cylinder (24), the stepped portion of said cylinder being
relieved to define an annular chamber (26) which is connected to the fuel inlet, the
end surfaces of the piston member (25) being exposed to the same pressure.
2. A fuel injection nozzle according to claim 1 characterised in that said piston
member (5) is in the form of a sleeve through which the valve member extends.
3. A fuel injection nozzle according to claim 2 characterised in that said valve member
(19) extends with clearance through said sleeve (25) and said clearance communicates
with a drain whereby the opposite ends of said sleeve are exposed to drain pressure.
4. A fuel injection nozzle according to claim 3 characterised in that the end of said
sleeve (25) remote from said seating (15) is engageable with a spring abutment (23)
to assist the movement of the valve member (19) and said end of the sleeve is also
engageable with an end surface of a nozzle holder (11) to limit the movement of the
sleeve.
5. A fuel injection nozzle according to claim 4 characterised by a flange (20) on
the valve member (19), said flange being engageable with the opposite end of the sleeve
(25) to limit the total movement of the valve member (19) away from the seating (15).
6. A fuel injection nozzle according to claim 5 characterised in that said cylinder
(24) is formed in a distance piece (12) located between a nozzle body (10) and a nozzle
holder (11).