Information
-
Patent Grant
-
6732949
-
Patent Number
6,732,949
-
Date Filed
Monday, October 22, 200122 years ago
-
Date Issued
Tuesday, May 11, 200420 years ago
-
Inventors
-
Original Assignees
-
Examiners
Agents
-
CPC
-
US Classifications
Field of Search
US
- 239 1022
- 239 1021
- 239 584
- 251 12906
- 123 498
- 310 326
- 310 327
-
International Classifications
-
Abstract
A fuel injection valve has a valve body and a valve member axially movable within the valve body. The opening stroke of the valve member is limited by a stroke stop face provided on a control piston which surrounds the valve member. A control chamber, which may be filled with fuel, is located at one end of the control piston. At a certain pressure in the control chamber, the control piston moves from a first to a second stroke position to limit the opening stroke motion of the valve member. Part of the control piston is embodied as a piezoelectric actuator which, when supplied with electric current, changes its axial length to further vary the stroke of the valve member.
Description
PRIOR ART
The invention is based on a fuel injection valve for internal combustion engines as generically defined by the preamble to claim 1. One such fuel injection valve, known from German Patent Disclosure DE 196 23 211 A1, has a valve body in which, in a bore, a piston like valve member is disposed such that it is movable axially counter to the force of a closing spring. On the end toward the combustion chamber, the valve member changes over into a closing head, which is guided in the bore. In the outward-oriented opening stroke motion of the valve member, the closing head emerges from the bore, and a control edge embodied on the closing head uncovers at least one injection opening. A plurality of injection openings can also be provided, which are opened successively by the control edge. As a result, by a limitation of the opening stroke of the valve member to a partial stroke, it becomes possible to uncover only some of the injection openings or to open only a partial cross section of one injection opening, and thus to control the entire effective injection cross section as a function of the opening stroke of the valve member. The opening stroke motion is limited to a partial stroke by a control piston, disposed in the valve body, whose end face defines a hydraulic control chamber. The control chamber can be filled with fuel at high pressure and as a result can displace the control piston axially from a first stroke position to a second stroke position, as a result of which the valve member executes either the maximum stroke or only a partial stroke. A hydraulically adjustable stroke stop of this type has a black-and-white function; that is, it does not allow any graduations between the two opening strokes. This limits the control capability of the fuel injection event, making further optimization of the injection event more difficult.
In a fuel injection valve of the inward-opening type as well, such as that known from German Patent Disclosure DE 197 29 843, it can be desirable for the sake of precise metering of a preinjection quantity to have a partial stroke available that has more than a black-and-white function, allowing an optimal injection course to be attained.
ADVANTAGES OF THE INVENTION
The fuel injection valve of the invention for internal combustion engines, having the characteristics of the body of claim 1, has the advantage over the prior art that between the closing spring and the guided portion of the valve member, a combined hydraulically and piezoelectrically controlled stroke stop is embodied, with which the opening stroke motion of the valve member can be set to any value between the maximum opening stroke and the partial stroke. By combining the hydraulically adjustable piston with a piezoelectric actuator, it is possible to switch the hydraulic piston not only between maximum stroke and partial stroke but also, by the delivery of electric current to the piezoelectric actuator, to switch it between the partial stroke and any arbitrary value between partial stroke and the maximum opening stroke of the valve member. As a result, in a further performance graph range of the engine, an optimally adapted opening stroke of the valve member is feasible. If switching between only partial stroke and a maximum opening stroke is necessary, then the piezoelectric actuator need not be supplied with electric current, which is advantageous from an energy standpoint.
Besides the use of the combined hydraulic and piezoelectrically controlled stroke stop in an outward-opening vario-nozzle, it is also possible to use the subject of the invention in an inward-opening fuel injection valve in the same advantageous way.
In an advantageous feature of the stroke stop, the control piston is embodied as a hollow cylinder, on the end of which remote from the combustion chamber the piezoelectric actuator is disposed.
This makes it easy to mount the control piston, since the piezoelectric actuator and the non-piezoelectrically active part of the control piston can be installed separately. In a control piston embodied in this way, in a further advantageous feature, the valve member in the opening stroke motion does not come into direct contact with the piezoelectric actuator but only with the interposition of a shim. This results in less wear on the piezoelectric actuator and thus a longer service life of the hydraulic stroke stop. Furthermore, the shim offers the capability, by replacement of this simple and hence economically produced shim, of setting the maximum opening stroke precisely by way of the thickness of the shim.
In a further advantageous feature, the control pressure for controlling the hydraulic stroke stop is drawn from a control line, which communicates with a high-pressure reservoir via a control valve. Furthermore, via a further control valve, the control line communicates with the largely pressureless fuel tank, so that by suitably triggering the two valves, loading and relieving of the control line are possible, without requiring a further high-pressure fuel source.
Further advantages and advantageous features of the subject of the invention can be learned from the description, drawing and claims.
DRAWING
One exemplary embodiment of the fuel injection valve according to the invention for internal combustion engines is shown in the drawing and will be described in further detail in the ensuing description. Shown are
FIG. 1
, a longitudinal section through the fuel injection valve;
FIG. 2
, an enlarged view of the detail marked II in
FIG. 1
, in the region of the closing head;
FIG. 3
, an enlarged view of the detail marked III in
FIG. 1
, in the region of the stroke stop;
FIG. 4
, the schematic layout of the fuel supply system for fuel injection and for furnishing fuel control pressure for the hydraulically adjustable stroke stop; and
FIG. 5
, a fuel injection valve of the invention, of the inward-opening type, in longitudinal section.
DESCRIPTION OF THE EXEMPLARY EMBODIMENT
FIG. 1
shows a fuel injection valve for internal combustion engines of the outward-opening type. In a valve body
1
, which can be constructed in multiple parts, a bore
2
is made in which a piston like valve member
5
is disposed, which is axially movable counter to the force of a closing spring
21
. In a portion, shown at the top in
FIG. 1
, of the bore
2
that is remote from the combustion chamber, the valve member
5
is guided, while the portion of the valve member
5
remote from the combustion chamber and shown at the bottom in
FIG. 1
is surrounded by a pressure chamber
11
, which can be made to communicate with a high-pressure fuel source via an inlet conduit
3
embodied in the valve body
1
. The valve member
5
merges toward the combustion chamber with a larger-diameter closing head
10
, which is guided in a larger-diameter portion of the bore
2
.
In
FIG. 2
, an enlarged view of the closing head
10
and the surrounding valve body
1
is shown. On the outer wall of the closing head
10
, two rows of injection openings
13
a
and
13
b
are provided, with one row including all the injection ports that are disposed at the same height as the closing head. The injection openings
13
a
and
13
b
communicate with the pressure chamber
11
via injection conduits
12
, which are embodied in the closing head
10
. In the closed state of the fuel injection valve, a valve sealing face
15
embodied on the closing head
10
comes to rest on the face end of the valve body
1
, which end is embodied as a valve seat face
17
, and the injection openings
13
a
,
13
b
are covered by the valve body
1
. Because the diameter of the closing head
10
is larger in comparison to the valve member
5
, a pressure shoulder
18
is embodied on the end of the closing head
10
remote from the combustion chamber, and this shoulder is exposed to the fuel pressure in the pressure chamber
11
. As an alternative to the embodiment shown in
FIG. 2
, it can also be provided that more than two rows of axially offset injection openings
13
a
,
13
b
are disposed on the outer jacket face of the closing head
10
. In a further embodiment, it can also be provided that only one rows of injection openings
13
a
,
13
b
is provided on the outer jacket face of the closing head
10
, and the cross section of this row is opened either entirely or only in part in the opening stroke motion of the valve member
5
.
On its end remote from the combustion chamber, the valve member
5
changes over into a spring tappet
24
, which protrudes as far as the inside of a spring chamber
20
embodied in the region of the valve body
1
remote from the combustion chamber. On the end of the spring tappet
24
remote from the combustion chamber, a spring plate
23
is embodied, on which the closing spring
21
is braced by its end remote from the combustion chamber. The spring chamber
20
communicates, via an outlet conduit embodied in the valve body
1
but not shown in the drawing, with an outlet line in order to carry away the leaking oil entering the spring chamber
20
.
FIG. 3
shows an enlarged view of the adjustable stroke stop of FIG.
1
. Between the guided portion of the valve member
5
and the spring chamber
20
, a larger-diameter guide bore
6
is formed. Disposed in the guide bore
6
are a control stop
31
, connected to the valve body
1
, and a control piston
30
, which is movable axially in the guide bore
6
. The control stop
31
is disposed on the end of the guide bore
6
remote from the spring chamber
20
and is embodied as a hollow cylinder, whose inside diameter is graduated, with the portion having the larger inside diameter being toward the spring chamber
20
. The control piston
30
is likewise embodied as a hollow cylinder, and its outer diameter is graduated, and the portion having the smaller diameter is located remote from the spring chamber
20
. The portion of the control piston
30
having the smaller outer diameter plunges into the portion of the control stop
31
of larger inside diameter, and between the control piston
30
and the control stop
31
, a throttle gap
45
is formed. The outer annular end face
35
, formed on the control piston
30
toward the combustion chamber by the graduated outer diameter, on the one hand and the control stop
31
on the other define a control chamber
33
, to which a control conduit
34
extends that is embodied in the valve body
1
. Via the throttle gap
45
, only little fuel can flow from the control chamber
33
past the valve member
5
into the spring chamber
20
. The control piston
30
is constructed in two parts; the hollow-cylindrical portion toward the spring chamber
20
is embodied as a piezoelectric actuator
26
, and the other part forms a graduated hydraulic piston
27
. For delivering electric current to the piezoelectric actuator
26
, suitable electrical contacts are disposed on it, which are connected to a suitable voltage source via an electric line, not shown in the drawing. The electric line can for instance be guided in a separate conduit embodied in the valve body
1
, or it can be extended to the outside through the spring chamber and the outlet conduit, not shown in the drawing, of the spring chamber
20
.
Toward the spring chamber
20
, a support disk
25
is disposed on the piezoelectric actuator
26
, and its face end toward the spring chamber
20
is embodied as a stroke stop face
42
, which in the stroke motion of the control piston
30
, oriented toward the spring chamber
20
, comes to rest on a control piston stop
43
formed by the cross-sectional reduction from the guide bore
6
to the spring chamber
20
. A spring support ring
22
is disposed in the spring chamber
20
, and the closing spring
21
is braced on this ring by its end toward the combustion chamber. The spring support ring
22
is guided in the spring chamber
20
and is pressed against the support disk
25
by the force of the closing spring
21
. At the transition from the valve member
5
to the spring tappet
24
, a annular collar
40
extending all the way around is embodied on the valve member
5
; its annular end face toward the combustion chamber is embodied as a stop face
41
. In the opening stroke motion of the valve member
5
oriented toward the combustion chamber, this stop face
41
comes to rest on the stroke stop face
42
embodied on the shim
25
, thereby defining the opening stroke.
In
FIG. 4
, the layout of the high-pressure fuel supply is shown schematically. From a fuel tank
50
, fuel is delivered via a low-pressure line
51
to a high-pressure fuel pump
52
. The high-pressure fuel pump
52
pumps fuel at high pressure through a high-pressure line
5
into a high-pressure reservoir
55
. For each fuel injection valve
101
of the internal combustion engine, one fuel inlet line
60
leads away from the high-pressure reservoir
55
and communicates at the fuel injection valve
101
with the inlet conduit
3
. Between the inlet conduit
3
and the fuel inlet line
60
, there is a metering valve
67
, with which the communication from the high-pressure reservoir
55
to the inlet conduit
3
can be opened or closed. The high-pressure reservoir
55
can be made to communicate with a control line
58
via a control valve
57
. Since a certain high fuel pressure is always maintained in the high-pressure reservoir
55
, by opening the control valve
57
fuel can be carried at high pressure into the control line
58
, as a result of which the pressure in the control line
58
adapts to that in the high-pressure reservoir
55
. Each fuel injection valve
101
communicates with the control line
58
via a control inlet line
59
that communicates with the control conduit
34
in the valve body
1
. The control line
58
can be made to communicate with the fuel tank
50
, acting as a relief chamber, via an outlet line
63
in which a control valve
61
is disposed. By opening the control valve
61
, the pressure in the control line
58
can be relieved at any time to the pressure level of the fuel tank
50
, which is approximately equivalent to atmospheric pressure. The entire fuel injection system is controlled by a control unit
65
, which includes a computer, which by means of the measured values of various sensors, not shown in the drawing, controls the high-pressure fuel pump
52
, the control valves
61
and
57
, the metering valves
67
, and the supply of electric current to the piezoelectric actuator
26
.
The mode of operation of the fuel injection valve shown in
FIG. 1
is as follows:
At the onset of the injection event, the metering valve
67
opens the communication from the fuel inlet line
60
to the inlet conduit
3
. As a result, fuel flows out of the high-pressure reservoir
55
through the fuel inlet line
60
and the inlet conduit
3
into the pressure chamber
11
. The fuel pressure in the pressure chamber
11
rises, until the resultant force in the axial direction on the pressure shoulder
18
is greater than the force of the closing spring
21
. The valve member
5
moves outward toward the combustion chamber, and as a result the two injection openings
13
a
and
13
b
emerge in succession from the bore
2
, as a result of which the pressure chamber
11
communicates with the combustion chamber, and fuel is injected into the combustion chamber. By means of the outward-oriented opening stroke motion of the valve member
5
, the annular collar
40
also moves toward the combustion chamber, and thus the stop face
41
moves toward the stroke stop face
42
. Whether the valve member
5
executes the maximum stroke h or only a partial stroke depends on the status of the control piston
30
.
The mode of operation of the adjustable stroke stop is as follows:
In the closed state of the fuel injection valve, that is, when the valve sealing face
15
is in contact with the valve seat face
17
and when the control chamber
33
of the hydraulic stroke stop is pressureless and there is no current to the piezoelectric actuator
26
, the stroke stop face
42
has an axial spacing from the stop face
41
of the annular collar
40
that is equivalent to the maximum opening stroke h of the valve member
5
. This status is shown in the left half of FIG.
3
. If the control chamber
33
is without fuel pressure, then the inner annular end face
36
of the control piston
30
is in contact with the seat face
37
of the control stop
31
. If then, with the control valve
57
open and the control valve
61
closed, fuel is introduced into the control chamber
33
via the control conduit
34
, the pressure in the control chamber
33
then rises until the resultant force on the outer annular end face
35
is greater than the force of the closing spring
21
. The control piston
30
moves toward the spring chamber
20
, until after the execution of the control stroke s, it comes to rest with the stroke stop face
42
on the control piston stop
43
. This status is shown in the right half of FIG.
3
. The control stroke s is shorter than the maximum opening stroke h. In the opening stroke motion of the valve member
5
, the stop face
41
, after the execution of the stroke h-s, comes to rest on the stroke stop face
42
. The control stroke s amounts to approximately 30 to 70% of the maximum opening stroke h, so that by subjecting the control chamber
33
to pressure with the resultant stroke motion of the control piston
30
, the opening stroke motion of the valve member
5
is limited to from 70 to 30% of the maximum opening stroke h. If the valve member
5
is meant to execute the maximum opening h again, then the pressure in the control chamber
33
is reduced by relief of the control line
58
into the fuel tank
50
, with the control valve
57
closed, via the control valve
61
and the outlet line
63
. If the force of the closing spring
21
exceeds the force of the fuel pressure on the inner annular end face
36
of the control chamber
33
, then the control piston
30
is pressed toward the combustion chamber by the closing spring
21
, until the inner annular end face
36
rests on the seat face
37
. If the stroke stop face
42
is meant to execute only a portion of the control stroke s, then current is supplied to the piezoelectric actuator
26
. Because of the change in length of the piezoelectric actuator
26
in response to the voltage applied, the stroke stop face
42
can be raised continuously variably to any arbitrary portion of the control stroke s. The maximum possible change in length of the piezoelectric actuator
26
is then equivalent approximately to the control stroke s, for instance.
In
FIG. 5
, a fuel injection valve of the invention of the inward-opening type is shown in longitudinal section. A bore
90
embodied as a blind bore is disposed in a valve body
80
, and its bottom face is oriented toward the combustion chamber. A conical valve seat
83
is embodied on the bottom face along with at least one injection opening
92
, which connects the bore
90
with the combustion chamber. By means of a lock nut
98
and with the interposition of a shim
94
, the valve body
80
is braced against a valve holding body
96
, which can be constructed in multiple parts.
A pistonlike valve member
100
that is longitudinally adjustable counter to the force of a closing spring
21
is disposed in the bore
90
; it is guided in sealing fashion in a portion of the bore
90
remote from the combustion chamber, and toward the combustion chamber, it changes over into a portion of smaller diameter, forming a pressure shoulder
88
. On the end toward the combustion chamber, a valve sealing face
81
is formed on the valve member
100
, which face cooperates with the valve seat
83
and thus opens and closes the injection openings
92
by means of the longitudinal motion of the valve member
100
. The pressure shoulder
88
is disposed in a pressure chamber
11
, embodied in the valve body
80
, which chamber continues, toward the valve seat
83
, into an annular gap surrounding the valve member
100
and can be filled with fuel via an inlet conduit
3
embodied in the valve body
80
. By the hydraulic force on the pressure shoulder
88
, the valve member
100
can be moved within the bore
90
, counter to the force of the closing spring
21
, so that the injection openings are opened.
On the end remote from the combustion chamber, the valve member
90
changes into a spring plate
103
and adjoining that into a spring tappet
107
, both of which are disposed in a spring chamber
105
embodied in the valve holding body
96
. The spring chamber
105
is embodied with a graduated diameter and is enlarged toward the end remote from the combustion chamber, forming a control piston stop face
43
embodied as an annular shoulder.
On the end of the spring chamber
105
remote from the combustion chamber, a combined hydraulically and piezoelectrically controlled stroke stop is provided, of the kind already described above in the description of the outward-opening fuel injection valve of
FIGS. 1 and 3
, so that only some details of it need to be addressed here. Toward the combustion chamber, the control piston
30
is disposed toward the control stop
31
, and the closing spring
21
surrounding the spring tappet
107
is disposed between the control piston's face end toward the combustion chamber and the spring plate
103
and, with the valve sealing face
81
, presses the valve member
100
against the valve seat
83
. The valve member
100
, on its end remote from the combustion chamber, has a stop face
109
, which as a result of the opening stroke motion of the valve member
100
in the direction away from the combustion chamber comes to rest on the control piston
30
. Upon activation of the hydraulic stop or piezoelectric actuator, the control piston
30
moves counter to the force of the closing spring
21
; the control piston stop face
43
defines the maximum path of the control piston
30
. As a result, the stroke stop face
42
embodied on the control piston
30
is displaced as well and thus reduces the maximum possible opening stroke of the valve member
100
.
Alternatively to the hydraulic stroke stop shown in
FIG. 3
or
FIG. 5
, it can also be provided that the entire control piston
30
is embodied as a piezoelectric actuator. Then there is no need for connecting the preferably metal hydraulic piston
27
to the piezoelectric actuator
26
. It can also be provided that the support disk
25
is omitted and that the stroke stop face
42
is embodied on the piezoelectric actuator
26
.
It should be noted in
FIGS. 1
,
3
and
5
that the piezoelectric actuator
26
has been shown only schematically, for the sake of simplicity. The size and in particular the axial length of the piezoelectric actuator
26
must be selected to suit the particular application, taking into account the slight relative change in length of the piezoelectric actuator.
Claims
- 1. A fuel injection valve for an internal combustion engine comprising: a valve body (1, 80) having an axially extending bore (2), a piston like valve member (5, 100) movable axially within said bore (2) counter to a closing force, said valve member being guided in said bore (2) over a portion of its length and controlling at least one injection opening (13a, 13b, 92), which can be opened entirely or in part by an opening stroke motion of said valve member (5, 100), a pressure chamber (11) formed in said valve body surrounding a portion of said valve member and adapted for connection with a high-pressure fuel source (55), a pressure shoulder (18) formed on said valve member and being located within said pressure chamber whereby connection of said pressure chamber to said high-pressure fuel source exposes said pressure shoulder to high-pressure causing said valve member to initiate its opening stroke motion counter to said closing force and said at least one injection opening to communicate with said pressure chamber (11), and an axially moveable control piston (30), defining the maximum opening stroke of the valve member (5, 100), one end face of said control piston acting as a stroke stop face (42) to limit the opening stroke motion of said valve member (5, 100) and an opposite end face (35) of said control piston defining a control chamber (33) adapted for connection to said high-pressure fuel source,the improvement wherein said control piston (30) comprises a piezoelectric actuator (26).
- 2. The fuel injection valve of claim 1, wherein said valve member (5, 100) is formed with a stop face (41, 109) which, in the opening stroke motion of the valve member, comes to rest on the stroke stop face (42) of said control piston (30).
- 3. The fuel injection valve of claim 2, wherein the control piston (30) comprises a hollow cylinder, which is disposed coaxially to the valve member (5, 100) and is guided in a guide bore (6) in said valve body.
- 4. The fuel injection valve of claim 3, wherein the control piston (30) comprises a stepped piston having portions of different diameters, including a larger diameter portion having an end face located near the stop face (41, 109) of said valve member (5, 100) and serving as said stroke stop face (42), and a smaller diameter portion having an end face (35) remote from the stroke stop face (42) which defines a wall of said control chamber (33).
- 5. The fuel injection valve of claim 4, wherein the piezoelectric actuator (26) comprises a hollow cylinder and is disposed coaxially to the valve member (5, 100).
- 6. The fuel injection valve of claim 5, wherein only a part of the control piston (30) is formed by the piezoelectric actuator (26), and the piezoelectric actuator (26) is disposed such that it is oriented toward the stop face (41, 109) of the valve member (5, 100).
- 7. The fuel injection valve of claim 6, wherein the valve member (5), to open the injection openings (13a, 13b), executes said opening stroke motion oriented outward, toward a combustion chamber of said internal combustion engine when the fuel injection valve is mounted on the engine.
- 8. The fuel injection valve of claim 7, wherein the valve member (5) includes an annular collar (40) having an annular end face, which is oriented toward the combustion chamber of said internal combustion engine when the fuel injection valve is mounted on the engine, and serving as the stop face (41), which cooperates with the stroke stop face (42) of the control piston (30).
- 9. The fuel injection valve of claim 3, wherein the valve member (5), to open the injection openings (13a, 13b), executes said opening stroke motion oriented outward, toward a combustion chamber of said internal combustion engine when the fuel injecting valve is mounted on the engine.
- 10. The fuel injection valve of claim 9, wherein the valve member (5) includes an annular collar (40) having an annular end face, which is oriented toward the combustion chamber of said internal combustion engine when the fuel injection valve is mounted on the engine, and serving as the stop face (41), which cooperates with the stroke stop face (42) of the control piston (30).
- 11. The fuel injection valve of claim 3, wherein the control chamber (33) is adapted to communicate with the high-pressure fuel source (55) via a control valve (57).
- 12. The fuel injection valve of claim 11, wherein the control chamber (33) is adapted to communicate with a relief chamber (50) via a control valve (61).
- 13. The fuel injection valve of claim 12, wherein the high-pressure fuel source is embodied as a high-pressure reservoir (55).
- 14. The fuel injection valve of claim 2, wherein the control piston (30) includes a support disk (25) disposed at an end face of the control piston (30) toward the stop face (41, 109) of the valve member (5, 100), and a face of said a support disk (25) serves as the stroke stop face (42).
- 15. The fuel injection valve of claim 14, wherein the valve member (5), to open the injection openings (13a, 13b), executes said opening stroke motion oriented outward, toward a combustion chamber of said internal combustion engine when the fuel injection valve is mounted on the engine.
- 16. The fuel injection valve of claim 14, wherein the control chamber (33) is adapted to communicate with the high-pressure fuel source (55) vial a control valve (57).
- 17. The fuel injection valve of claim 2, wherein said closing force is supplied by at least one closing spring (21) disposed in a spring chamber (20, 105) in said valve body.
- 18. The fuel injection valve of claim 17, wherein the control piston (30) is guided in a guide bore (6) adjacent said spring chamber (20) in said valve body, said guide bore (6) having a larger diameter than said spring chamber (20) and an annular end face (43) at the transition from the guide bore diameter to the spring chamber diameter, which limits the axial motion of the control piston (30) in the direction of the stop face (41, 109) of the valve member (5, 100).
- 19. The fuel injection valve of claim 18, wherein the closing spring (21) rests at least indirectly on the stroke stop face (42) of the control piston (30), so that the closing spring (21) acts counter to the stroke of the control piston (30).
- 20. The fuel injection valve of claim 17, wherein the closing spring (21) rests at least indirectly on the stroke stop face (42) of the control piston (30), so that the closing spring (21) acts counter to the stroke of the control piston (30).
- 21. The fuel injection valve of claim 1, wherein the valve member (5), to open the injection openings (13a, 13b), executes said opening stroke motion oriented outward, toward the combustion chamber of said internal combustion engine when the fuel injection valve is mounted on the engine.
- 22. The fuel injection valve of claim 21, wherein the valve member (5) includes an annular collar (40) having an annular end face, which is oriented toward the combustion chamber of said internal combustion engine when the fuel injection valve is mounted on the engine, and serving as a stop face (41), which cooperates with the stroke stop face (42) of the control piston (30).
- 23. The fuel injection valve of claim 1, wherein the control chamber (33) is adapted to communicate with a high-pressure fuel source (55) vial a control valve (57).
- 24. The fuel injection valve of claim 23, wherein the control chamber (330 is adapted to communicate with a relief chamber (50) via a control valve (61).
- 25. The fuel injection valve of claim 23, wherein the high-pressure fuel source is embodied as a high-pressure reservoir (55).
Priority Claims (1)
Number |
Date |
Country |
Kind |
199 56 510 |
Nov 1999 |
DE |
|
PCT Information
Filing Document |
Filing Date |
Country |
Kind |
PCT/DE00/04181 |
|
WO |
00 |
Publishing Document |
Publishing Date |
Country |
Kind |
WO01/38724 |
5/31/2001 |
WO |
A |
US Referenced Citations (2)
Number |
Name |
Date |
Kind |
5697554 |
Auwaerter et al. |
Dec 1997 |
A |
6585171 |
Boecking |
Jul 2003 |
B1 |
Foreign Referenced Citations (2)
Number |
Date |
Country |
4332124 |
Mar 1995 |
DE |
19623211 |
Dec 1997 |
DE |