U.S. patent number 3,610,529 [Application Number 04/844,005] was granted by the patent office on 1971-10-05 for electromagnetic fuel injection spray valve.
This patent grant is currently assigned to Societe Des Procedes D'Injection Sopromi. Invention is credited to Robert Huber.
United States Patent |
3,610,529 |
Huber |
October 5, 1971 |
ELECTROMAGNETIC FUEL INJECTION SPRAY VALVE
Abstract
The nozzle valve needle is closed by a compression spring housed
in a space that is separate from the space in which the pressure
determines the opening and closing of the needle. In another
embodiment, a piston is acted upon by the pressure in this latter
space to close the needle.
Inventors: |
Huber; Robert (Zumikon,
CH) |
Assignee: |
Societe Des Procedes D'Injection
Sopromi (Les Mureaux, FR)
|
Family
ID: |
4387525 |
Appl.
No.: |
04/844,005 |
Filed: |
July 23, 1969 |
Foreign Application Priority Data
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Aug 28, 1968 [CH] |
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12911/68 |
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Current U.S.
Class: |
239/96; 239/124;
239/533.8; 239/585.3 |
Current CPC
Class: |
F02M
47/027 (20130101); F02M 2547/003 (20130101) |
Current International
Class: |
F02M
47/02 (20060101); F02m 047/00 () |
Field of
Search: |
;239/86,87,88,89,90,91,92,95,96,533,585 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Wood, Jr.; M. Henson
Assistant Examiner: Grant; Edwin D.
Claims
I claim:
1. An electromagnetic fuel-injection spray valve for internal
combustion engines, particularly diesel engines, including an
electromagnetic metering valve (4,5) at the upper end of the spray
valve body (16), a spray nozzle (10), a needle valve (8,9) arranged
immediately upstream of said spray nozzle, a nozzle valve needle
(8) incorporated by said needle valve and opened by the fall in the
pressure acting on said needle, caused when said metering valve
opens to establish a path to a fuel return line (23), and wherein
the improvement comprises a first space (20,38,45) in which the
fuel pressure determines the opening and closing of said nozzle
valve needle, and means operatively associated with said nozzle
valve needle for aiding the closing of said nozzle valve needle in
response to the closing of the metering valve.
2. The injection spray valve as defined in claim 1, wherein said
first space is provided with an inlet passage for the inflow of
fuel thereto and is connected to said metering valve to form part
of the path to the fuel return line, and the cross section of the
fuel flowing into said first space via said inlet passage is
smaller than that of the fuel flowing thereout vial said return
line path, for obtaining a quick opening and a slow closing of said
nozzle valve needle.
3. The injection spray valve as defined in claim 1, wherein said
first space is provided with an inlet passage for the inflow of
fuel thereto and is connected to said metering valve to form part
of the path to the fuel return line, and the cross section of the
fuel flowing into said first space via said inlet passage is
greater than that of the fuel flowing thereout via said return line
path, for obtaining a slow opening and a quick closing of said
nozzle valve needle.
4. The injection spray valve as defined in claim 1, wherein said
means operatively associated with said nozzle valve needle
comprise: a second space separate from said first space, and spring
means contained within said second space for aiding the closing of
said nozzle valve needle.
5. The injection spray valve as defined in claim 4, wherein said
nozzle valve needle is closed by said spring means, said second
space (11) is under fuel pressure at all times, and said first
space is located at the rear end of said nozzle valve needle, and
further including a rod (7) sealingly arranged in the spray valve
body (6) and free to slide axially for transmitting the force of
said spring means to said nozzle valve needle.
6. The injection spray valve as defined in claim 4, wherein said
nozzle valve needle is closed by said spring means, said second
space (30) is relieved of fuel pressure at all times, and said
first space (38) is in direct communication with said metering
valve at all times, and further including a rod (27) free to move
axially for transmitting the force of said spring means to said
nozzle valve needle, and a piston (28) connected to said rod to
move therewith, one end of said piston defining one side of said
first space.
7. The injection spray valve as defined in claim 4, wherein said
nozzle valve needle is in part closed by said spring means, said
second space (30) is relieved of fuel pressure at all times, and
said first space (38) is in direct communication with said metering
valve at all times, and further including a rod (27) free to move
axially for transmitting the force of said spring means to said
nozzle valve needle, and a piston (28) connected to said rod to
move therewith, said piston having a larger diameter than does the
shaft of said nozzle valve needle to help to close the latter, and
one end of said piston defining one side of said first space.
8. An electromagnetic fuel-injection spray valve as defined in
claim 1 wherein said means operatively associated with said nozzle
valve needle comprised closing means operated by the pressure in
said first space for closing said nozzle valve needle.
9. The injection spray valve as defined in claim 8, wherein said
nozzle valve needle is closed by said closing means and said
closing means is a piston (28) of which one end defines one side of
said first space, and said first space is in direct communication
with said metering valve at all times, and further including a rod
(27) free to move axially for transmitting the pressure within said
first space acting on said piston to said nozzle valve needle to
close the latter.
10. The injection spray valve as defined in claim 8, wherein said
nozzle valve needle is closed by said closing means and the latter
is an operating piston (40) of which one end defines one side of
said first space (45), said operating piston having a cross section
greater than does said nozzle valve needle and acting directly on
the latter, whereby the fuel pressure in said first space
determines the closing of said nozzle valve needle.
11. The injection spray valve as defined in claim 10, including an
auxiliary piston (51) arranged within said operating piston for
acting on said nozzle valve needle, and a compression spring (50)
pressing on said auxiliary piston to keep said nozzle valve needle
closed when the fuel pressure is absent.
Description
BACKGROUND OF THE INVENTION
The invention relates to an electromagnetic fuel-injection spray
valve for internal combustion engines, particularly diesel engines,
including an electromagnetic metering valve at the upper end of the
spray valve body, a spray nozzle, a needle valve arranged
immediately upstream of the spray nozzle, and a nozzle valve needle
incorporated by the needle valve and opened by the fall in the
pressure acting on the needle, caused when the metering valve opens
to establish a path to a fuel return line.
An injection valve of this kind is prior art, the quantity of the
fuel injected being determined by the length of the current pulse
fed to the electromagnetic metering valve.
A spring closes the nozzle valve needle after each injection. This
spring is contained in a space the fuel pressure in which
determines the opening and closing of the nozzle valve needle by
the spring, the space being connected to a relief line. As a
consequence of the additional volume required by this space to
house the spring, the total volume is relatively large in which the
fuel pressure must be reduced for each injection. This fact slows
down the rise and fall of the fuel pressure in this space, and
delays control of the engine, particularly at high r.p.m.
SUMMARY OF THE INVENTION
The purpose of the invention is to provide an electromagnetic
fuel-injection spray valve of the aforesaid kind that avoids this
disadvantage. In accordance with the invention, spring means to
close the nozzle valve needle is housed in a space separate from
that determining the opening and closing of the needle, or
nozzle-valve-needle closing means is provided operated by the fuel
pressure in the space determining opening and closing of the
needle.
BRIEF DESCRIPTION OF THE DRAWINGS
Several embodiments of the invention will be described, with
reference to the figures of the accompanying drawings, wherein:
FIGS. 1 2, and 3 are longitudinal sections of three different
embodiments of the invention; and
FIG. 4 is a modification of the embodiment shown in FIG. 3.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
With reference to FIG. 1, the electromagnetic part of the valve
comprises in a known manner a core 1 having a winding 2 and a
movable armature 3, which is rigidly connected to the needle 4 of a
metering valve. The needle cooperates with the valve seat 5. A
compression spring 24 presses the armature downwards, seating the
metering needle 4 on its seat 5. The upper end of the spring 24
presses against a stop 25 slidably held in the armature 3 and
pressed against the core 1. A rod 7 is sealingly held in the valve
body 6 free to slide axially. Joined to the lower end of the rod 7
is a nozzle valve needle 8, which cooperates with the valve seat 9
and forms the actual injection spray valve controlling the flow of
fuel to the spray nozzle 10. A compression spring 12, located in a
chamber 11, presses on the rod 7 and hence on the nozzle valve
needle 8 to keep the injection spray valve closed.
The fuel, delivered by a high-pressure supply pump, flows through
the line 13 and the bores 14 and 15 to be delivered simultaneously
to the chamber 11 and the space 16 just upstream of the seat 9.
The bore 15 is connected to an annular space 17, which a throttling
bore 18 connects to bores 19 that form a relief line connecting a
space 20 above the nozzle valve needle 8 with the valve seat 5 of
the metering valve 4 and 5. When the latter is open the space 20
communicates with a space 21 that a bore 22 connects with a return
line 23, in which the fuel is at approximately atmospheric
pressure. The fuel flows through bores (not shown) in the core 1 to
the return line 23. The injection spray valve operates in the
following manner. The fuel delivered under pressure by the line 13
flows through the bores 14 and 15 to fill the spaces 11, 16, and
17, and through the throttling bore 18 into the relief line 19 and
the space 20. When a current pulse energizes the winding 2, the
armature 3 and its metering needle 4 are raised, the pressure in
the relief line 19 and the space 20 consequently falling. Since the
cross-sectional area of the nozzle valve needle 8 is greater than
that of the rod 7, the needle 8 is raised from its seat 9 and fuel
sprayed from the spray nozzle 10 into the cylinder, not shown. As
soon as the flow of current in the winding 2 stops, the metering
needle 4 closes. The spring 12 presses the nozzle valve needle 8
back onto its seat 9, and at the same time the pressure in the
relief line 19 and the space 20 rises.
In the embodiment shown in FIG. 2, a piston 28 is arranged above a
rod 27, which corresponds to the rod 7 in FIG. 1. The rod 27 is
arranged with lateral play in the valve body 6. The space 29 above
the injection spray needle 8 is connected to a space 30, which a
passage 31 and a bore 32 connect to a space 34, and which a bore 33
and passages in the core 1 connect to the return line 23, so that
an approximately atmospheric pressure is present in all of these
spaces and connecting bores and passages.
Fuel delivered under high pressure by the line 3 flows through the
bores 35 into the space 36 and through the throttling bore 37 into
the space 38 above the piston 28. When the winding 2 is energized,
the metering needle 4 is raised, causing the high pressure in the
space 38 to fall. As a consequence of the high pressure in the
space 36, the injection spray needle 8 is raised from its seat 9,
and fuel sprays from the spray nozzle 10 into the cylinder, not
shown. The space 38, which must be relieved of its pressure for
each injection, has in this embodiment a very small volume. As soon
as the metering needle 4 is again seated, the spring 12 reseats the
needle 8, and the pressure in the space 38 rises.
In the embodiment shown in FIG. 1, the spring 12 is the only means
for closing the needle 8, whereas in the embodiment shown in FIG. 2
the spring 12 can be eliminates or can be weak, provided that the
piston 28 has a somewhat larger diameter than does the shaft of the
needle 8, so that the downward closing force acting on the piston
28 is greater than the upward force acting on the needle 8.
In the embodiment shown in FIG. 3 is closing spring 12 is also not
essential. A piston 40, having a larger cross section than does
injection spray needle 8, is arranged immediately above the needle
8. The fuel delivered at high pressure by the line 13 flows through
the bores 41 to the space 42 and through the throttling bore 43 and
the bore 44 into the space 45.
In contrast to the first embodiment, the space 46 between the
piston 40 and the injection spray needle 8 is connected at all
times to a space 48 by the bores 47 and to the return line 23 by a
bore 49 and the passages (not shown) in the core 1. As a
consequence of the greater cross sectional surface area of the
piston 40, the latter exerts a closing force on the needle 8. As
soon, however, as the energized winding 2 opens the metering valve
4 and 5, the pressure in the space 45 falls; and the injection
spray needle 8, because of the unchanged pressure in the space 42,
is raised, and fuel is sprayed from the nozzle 10. When the
metering valve 4 and 5 closes, the pressure in the space 45
immediately rises, and the piston 40 presses the needle 8 back onto
its seat 9.
In order to keep the needle 8 seated when the fuel pressure is
absent (engine shut off) there can be incorporated in the piston
40, as shown in FIG. 4, a weak spring 50, which presses against the
needle 8 by means of an auxiliary piston 51.
In the three embodiments the spaces 20, 38, and 45, the relative
pressure in which determines the opening and closing of the
injection spray valve, are connected by the calibrated throttling
bores 18, 37, and 43 to the fuel supply line 13 and are connected
directly, or by the bores 19 and 44, with the electromagnetically
controlled metering valve 4 and 5. The dimensions of the calibrated
cross section and of the cross section exposed by the valve
fundamentally influence the manner in which the spray valve 8 and 9
opens and closes. If the calibrated inlet is made relatively large
as compared to the cross section controlled by the valve, for
example, the needle 8 opens relatively slowly, since the fuel that
must be pushed away by the needle 8 (FIG. 1), or by the piston 28
or 40 (FIGS. 2 and 3), cannot quickly escape. But the valve closes
quickly because of the large inlet cross section.
On the other hand, if the inlet cross section is small and the
valve cross section large, the valve opens quickly but closes much
more slowly.
By suitable choice of the cross sections through which the fuel
flows, the fuel injection spray valve can be adapted to the
engine.
Although the preferred embodiments of the invention have been
described, the scope of, and the breadth of protection afforded to,
the invention are limited solely by the appended claims.
* * * * *