EP1658427A1 - Fuel injection valve for internal combustion engines - Google Patents
Fuel injection valve for internal combustion enginesInfo
- Publication number
- EP1658427A1 EP1658427A1 EP04738755A EP04738755A EP1658427A1 EP 1658427 A1 EP1658427 A1 EP 1658427A1 EP 04738755 A EP04738755 A EP 04738755A EP 04738755 A EP04738755 A EP 04738755A EP 1658427 A1 EP1658427 A1 EP 1658427A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- chamber
- needle
- control
- control chamber
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0014—Valves characterised by the valve actuating means
- F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
- F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
- F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
- F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
- F02M45/08—Injectors peculiar thereto
- F02M45/086—Having more than one injection-valve controlling discharge orifices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
- F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
- F02M45/10—Other injectors with multiple-part delivery, e.g. with vibrating valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
- F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
- F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/46—Valves, e.g. injectors, with concentric valve bodies
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
Definitions
- the invention is based on a fuel injection valve for internal combustion engines, as is known for example from DE 102 22 196 AI.
- the known fuel injection valve has a housing in which a valve seat is formed, from which a plurality of injection openings originate.
- an outer valve needle and an inner valve needle slidably mounted in it which cooperate with the valve seat end on the valve seat and thus control the opening of at least two injection openings.
- An outer control chamber is formed in the housing, the pressure of which, at least indirectly, can exert a closing force on the end of the outer valve needle remote from the valve seat.
- an inner control chamber is formed in the housing, the pressure of which, at least indirectly, can exert a closing force on the end of the inner valve needle facing away from the valve seat.
- the inner control chamber is connected to a control valve chamber of a control valve via an inner outlet throttle, and likewise the outer control chamber is connected to this control valve chamber via an outer outlet throttle.
- the control valve chamber can be connected to a leakage oil chamber via an outlet opening, the various inlets being controlled by a valve member which is arranged in the control valve chamber and which can assume various switching positions.
- the inner control chamber is formed within a control piston against which the valve outer needle rests.
- the pressure in the inner control chamber depends on the stroke of the valve outer needle.
- independent control of the outer valve needle and inner valve needle is no longer possible.
- the pressure drop in the inner control has the effect that a precisely balanced system of inlet throttles and outlet throttles must be available and, moreover, the pressure areas on the valve inner needle must be precisely adapted to the pressure conditions in order to be able to carry out the control. This is technically complex and costly to implement.
- the fuel injection valve according to the invention with the characterizing features of patent claim 1 has the advantage over the prior art that independent control of the outer valve needle and the inner valve needle can be achieved, which allows greater freedom in the design of the corresponding component dimensions and moreover enables a more precise metering of the injected fuel quantity ,
- the inner control chamber has an inner inlet throttle and the outer control chamber has an outer inlet throttle, which are connected to a fuel-filled high-pressure region formed in the housing.
- the control valve chamber can be connected to a leakage oil chamber by the valve member, which can assume a first, a second and a third switching position, in the first switching position the drain opening, which connects the control valve chamber to the leakage oil chamber, is closed by the valve member in which second switching position, both the inner outlet throttle and the outer outlet throttle are connected to the leakage oil chamber via the now opened outlet opening and in the third switching position the outer outlet throttle is connected to the leakage oil chamber and the inner outlet throttle is closed by the valve member.
- control valve which corresponds in its function to a 3/3-way valve
- The when the valve member is in its second switching position, relieves both the imieren and the outer control chamber, so that both valve needles open.
- the valve member can be moved via a piezo actuator connected to the valve member.
- the piezo actuator allows the valve member to go directly to any desired position can be brought between the first and the third switching position.
- the valve member is advantageously in its first switching position against a first valve seat and in its third switching position against a second valve seat, the valve member moving linearly between these two switching positions.
- the second switching position of the valve member is between the first and the third switching position.
- the inner control chamber and the outer control chamber are connected to one another when both the valve outer needle and the valve inner needle are in their closed position, i.e. are in contact with the valve seat.
- this common control chamber is connected to the control valve chamber via two flow restrictors, which now makes it possible, depending on the switching position of the valve member, to relieve the common control chamber via one or both flow restrictors.
- the two valve needles can be controlled independently, so that the inner valve needle can be kept closed while the outer valve needle is open.
- the end faces of the valve needles facing away from the valve seat do not directly delimit the inner or outer control chamber, but rather the valve needles abut an inner and an outer valve piston, which delimit the respective control rooms.
- the outer control space is designed as an annular space, which is always separated from the inner control space.
- the annulus can either the valve inner needle or the inner valve piston surround, so that a compact design of the fuel injector is made possible.
- the drawing shows two exemplary embodiments of the fuel injection valve according to the invention. It shows
- FIGS. 2a to 2c show an enlargement of the control valve in different switching positions
- FIG. 3 a and 3 b show an enlargement of the section from FIG. 1 designated III in the area of the control rooms and
- FIG. 4 shows a second exemplary embodiment of the fuel injection valve according to the invention, only the section labeled A of the fuel injection valve shown in FIG. 1 being shown here.
- FIG. 1 shows a first exemplary embodiment of the fuel injection valve according to the invention.
- the fuel injector is shown in a section A and a section B, the part between these two sections being omitted for the sake of clarity.
- Section B which represents the actual nozzle, is sufficiently known from the prior art, so that only its essential parts are described here, whereas the section
- A contains the essential parts for the invention.
- the fuel injection valve comprises a housing 1, which comprises a holding body 9, a throttle plate 7, a control body 5 and a valve body 3, which abut one another in this order.
- the valve body 3 is replaced by a Clamping nut 2, which rests on a shoulder of the valve body 3 and is screwed into a thread on the holding body 9, is pressed against the control body 5, so that the control body 5 presses on the holding body 9 via the throttle plate 7.
- a bore 11 is formed in the valve body 3, which is designed as a blind bore and which forms a conical valve seat 20 at its end on the combustion chamber side.
- Two rows of injection openings 26, 28 are formed in the conical valve seat 20, the outer row of injection openings 26 being formed upstream of the inner row of injection openings 28. Both rows of injection openings 26, 28 open into the combustion chamber of the same in the installed position of the fuel injection valve.
- an outer valve needle 17 is arranged to be longitudinally displaceable and is sealingly guided on a section in the bore 11 facing away from the combustion chamber. Between the outer valve needle 17 and the wall of the bore 11, a pressure chamber 12 is formed, which also has an inlet channel 8 running in the holding body 9, the throttle valve 7, the control body 5 and the valve body 3
- Fuel can be filled under high pressure.
- the inlet channel 8 opens into a radial extension of the pressure chamber 12, this radial extension directly adjoining the section of the bore 11 in which the valve outer needle 17 is guided.
- an outer valve sealing surface 22 is formed which is at least approximately frustoconical and which interacts with the valve seat 20.
- the outer valve needle 17 has a longitudinal bore 16, so that the outer valve needle 17 forms a hollow needle.
- a valve inner needle 15 is arranged so as to be longitudinally displaceable, which also has a conical valve sealing surface 24 at its end on the valve seat side, with which the valve inner needle 15 interacts with the valve seat 20.
- the control of the outer injection openings 26 and of the inner injection openings 28 takes place in such a way that when the pressure in the pressure chamber 12 is sufficiently high, a force is exerted on the pressure shoulder 13 which is directed away from the valve seat.
- the outer valve needle 17 moves away from the valve seat 20, so that the outer injection openings 26 are released and fuel is injected from the pressure chamber 12 through the outer injection openings 26 into the combustion chamber.
- the valve inner needle 15 which is directed away from the valve seat 20 due to the hydraulic pressure on parts of the valve sealing surface 24
- the inner injection openings 28 are released and fuel is injected simultaneously through the outer injection openings 26 and the inner injection openings 28.
- a piston chamber 32 is formed in the control body 5 and is open on both end faces of the control body 5.
- An outer valve piston 34 and an inner valve piston 36 arranged in the outer valve piston 34 are arranged in the piston chamber 32.
- the outer valve piston 34 abuts the valve outer needle 17, while the inner valve piston 36 abuts the valve inner needle 15.
- a closing spring 38 is arranged in the piston chamber 32, which is supported at one end on a shoulder formed in the piston chamber 32 and at the other end on the outer valve piston 34, the closing spring 38 being pretensioned such that it engages the outer valve piston 34 and thus the outer valve needle 17 presses in the direction of the valve seat 20.
- FIGS. 3a and 3b each show an enlargement of the piston chamber 32.
- the outer valve piston 34 delimits, with its end facing away from the valve outer needle 17, an outer control chamber 56, which is delimited on the outside by the wall of the piston chamber 32 and the outer valve piston 34 opposite by the throttle plate 7.
- the outer control chamber 56 is connected to the inlet channel 8 via an inlet throttle 47, via a connecting groove 53 formed in the throttle plate 7.
- an outlet throttle 49 extends from the outer control chamber 56, which opens into a control valve chamber 60 of a control valve 30, which is arranged in the holding body 9.
- the inner valve piston 36 delimits, with its end facing away from the valve inner needle 15, an inner control chamber 54, which is connected to the inlet channel 8 via an inlet throttle 47, which is formed in the throttle plate 7, via the connecting groove 53.
- the inner control chamber 54 is also connected to the control valve chamber 60 via an inner outlet throttle 51.
- a leak oil chamber 40 is formed in the holding body 9, which is connected to a fuel return system and in which there is always a low fuel pressure prevails.
- the piston chamber 32 is connected to the leakage oil chamber 40 via an outlet channel 42, which runs in the holding body 9 of the throttle plate 7 and in the control body 5, so that there is always a low fuel pressure in the piston chamber 32.
- Fuel emerging from the pressure chamber 12 and flowing between the valve outer needle 17 and the wall of the bore 11 is discharged so that there is no pressure increase in the piston chamber 32.
- the leakage oil chamber 40 is also connected to the control valve chamber 60 via an outlet opening 68.
- Figure 2a shows the detailed structure of the control valve 30 and makes the mode of operation clear.
- a valve member 62 which is connected to a piezo actuator 66, is arranged in the control valve chamber 60. With the aid of the piezo actuator 66, the valve member 62 can be moved in the longitudinal direction in the control valve chamber 60.
- the valve member 62 has a first sealing surface 74 with which the valve member 62 in the first switching position shown in FIG. 2a bears against a first valve seat 70 formed in the control valve chamber 60.
- the drain opening 68 which is designed as an annular gap surrounding the valve member 62 and through which the
- Control valve chamber 60 is connected to the leak oil chamber 40, closed. Via a closing spring 64 arranged in the control valve chamber 60, the valve member 62 is pressed into contact with the first valve seat 70, so that the valve member 62 remains in this first switching position when the piezo actuator 66 is not energized. In the first switching position, both flow restrictors 49, 51, which open into the control valve chamber 60, are open. Since the control valve chamber 60 now has no connection to the leakage oil chamber 40, the high fuel pressure that is present in the high-pressure region of the fuel injection valve, that is to say in the inlet channel 8, builds up in the latter. As a result, there is also a high fuel pressure in the outer control chamber 56 and in the inner control chamber 54, which both the outer valve piston 34 and thus the
- the control spaces 54, 56 are connected to one another and form a common control space. Since the outer valve piston 36 has a larger area delimiting the outer control chamber 56 than the pressure shoulder 13 of the outer valve needle 17, the outer valve needle 17 remains closed, although there is always a high fuel pressure in the pressure chamber 12.
- FIG. 2 c Switching position of the valve member 62 is shown in FIG. 2 c and shows the valve member 62 as it rests with its end face opposite the first sealing surface 74, which is designed as a second sealing surface 76, on the second valve seat 72, which is designed on the throttle plate 7.
- the inner outlet throttle 51 is closed, so that the outer control chamber 56 is now connected to the control valve chamber 60.
- the drain opening 68 remains open.
- the fuel injector works as follows: at the beginning of the injection process, the valve member 62 of the control valve 30 is in its first
- valve member 62 is supplied with current through the piezo actuator 66 from its first switching position to the third
- the outer outlet throttle 49 is dimensioned in such a way that the pressure in the two control spaces 54, 56 also drops when the inner outlet throttle 51 is closed by the valve member 62. So less fuel flows into the control chambers 54, 56 via the inlet throttles 45, 47 than via the outer outlet throttle 49 into the Leakage oil chamber 40 flows out. As a result, the pressure in the outer control chamber 56 and in the inner control chamber 54 drops until the hydraulic force on the pressure shoulder 13 of the outer valve needle 17 is greater than the hydraulic force and the spring force of the closing spring 38 on the outer valve piston 34. This moves the valve outer needle 17 away from the valve seat 20 and opens the outer
- the movement of the valve outer needle 17 also moves the outer valve piston 34 until it comes into contact with the throttle disk 7. Due to the beveling of the end face of the outer valve piston 34, a sealing edge 37 is formed on the latter, which, due to its abutment on the throttle disk 7, the outer
- Control room 56 separates from the inner control room 54. Since the inner control chamber 54 now has no hydraulic connection to the control valve chamber 60 and thus to the leakage oil chamber 40, the pressure in the inner control chamber 54 does not drop further, but rises again to the level of the inlet channel 8 via a corresponding fuel supply through the inner inlet throttle 47 on. As a result, the hydraulic force on the inner valve piston 36 and thus on the valve inner needle 15 remains so great that the valve inner needle 15 remains in its closed position and closes the inner injection openings 28. To end the injection process, the valve member 62 of the control valve 30 is moved back into the first switching position by the piezo actuator 66, as shown in FIG. 2a.
- the pressure in the outer control chamber 56 quickly rises again as fuel flows in through the outer inlet throttle 45, since no more fuel flows out through the outer outlet throttle 49. As soon as the fuel pressure in the outer control chamber 56 has risen so far that the force exerted thereby is greater than the hydraulic force on the pressure shoulder 13 of the outer valve needle 17, the outer valve needle 17, driven by the outer valve piston 34, moves back into its closed position, i.e. in contact with the valve seat 20 and thereby closes the outer injection openings 26.
- the control valve 30 is actuated such that the valve member 62 moves into its second switching position, as shown in FIG. 2b.
- the common control chamber which is formed by the outer control chamber 56 and the inner control chamber 54, is connected to the control valve chamber 60 via the outer outlet throttle 49 and the inner outlet throttle 51. Since a significantly higher discharge cross-section is now available, the pressure in the control spaces 54, 56 drops very rapidly and the valve outer needle 17 first opens in the manner described above and, depending on the design of the pressure surface on the inner valve sealing surface 24 of the valve inner needle 15, with a short or somewhat longer distance also the valve inner needle 15.
- the inner valve piston moves here
- valve member 62 of the control valve 30 is moved back to its first switching position, as shown in FIG. 2a. Due to the now closed drain opening 68, there is no connection to the leakage oil chamber 40, which allows the pressure in the inner control chamber 54 and the outer control chamber 56 to rise again rapidly via fuel inflow through the inner inlet throttle 47 and the outer inlet throttle 45, so that the corresponding hydraulic ones Forces on the outer valve piston 34 and the inner valve piston 36 drive both valve needles 15, 17 back into their closed position.
- valve member 62 first moves into the third switching position, so that, as described above, valve outer needle 17 opens.
- the valve member 62 can then be moved into the second switching position, in which the inner control chamber 54 is also relieved via the inner outlet throttle 51.
- the valve inner needle 15 now also opens, so that the injection takes place first only through the outer injection openings 26 and then through all the injection openings 26, 28, so that an injection profile is formed, the exact profile of which is also via the switching speed of the piezo actuator 66 can be influenced.
- the valve member 62 is then moved back into its first switching position, so that the valve needles 15, 17 close again in the manner described above.
- FIG. 4 shows a second exemplary embodiment of the fuel injection valve according to the invention, only the section of the fuel injection valve designated by A in FIG. 1 being drawn again.
- Section B of FIG. 1 is identical to the end of the fuel injection valve on the combustion chamber side, as shown in FIG.
- the fuel injection valve shown in FIG. 4 also has a housing 1, a separate control body 5 being dispensed with and the holding body 9 directly adjoining the throttle disk 7 and this in turn bordering the valve body 3.
- the valve body 3 is pressed by a clamping nut 2 in the same manner as in the exemplary embodiment shown in FIG. 1 via the throttle disk 7 against the holding body 9.
- a bore 11 is formed in the valve body 3, in which a valve outer needle 17 and a
- Valve inner needle 15 are arranged, which are longitudinally displaceable in the bore 11. At the end facing away from the valve seat, the bore 11 is expanded to a spring chamber 14, in which the closing spring 38 is arranged.
- the valve outer needle 17 is surrounded by a sleeve 18 which is arranged in the spring chamber 14 and between which and a support ring 19 the closing spring 38 is arranged under prestress.
- the sleeve 18 abuts the throttle disc 7, so that a closing force is exerted on the valve outer needle 17 via the closing spring 38 and the support ring 19.
- the inlet channel 8 opens into the spring chamber 14, so that the function of the spring chamber 14 corresponds to the pressure chamber 12 of the exemplary embodiment shown in FIG.
- the pressure chamber 12 continues as an annular space between the outer valve needle 17 and the wall of the bore 11 up to the valve seat 20.
- a bore 39 is formed in the throttle disk 7, into which the valve inner needle 15 projects and in which it is guided.
- the valve inner needle 15 is longer than the valve outer needle 17, and it has a first annular groove
- the first annular groove 77 and the second annular groove 78 are connected to one another via a connecting groove 79 on the outside of the valve inner needle 15, and the second annular groove 78 is also connected via an outlet channel 58 running in the throttle valve 7 and the holding body 9 connected to the leakage oil chamber 40, so that there is always a low fuel pressure both in the first annular groove 77 and in the second annular groove 78.
- the outer control chamber 56 which is connected to the control valve chamber 60 of the control valve 30 via the outer outlet throttle 49, is delimited by the end of the valve outer needle 17 facing away from the valve seat, the sleeve 18, the throttle disk 7 and the valve inner needle 15.
- the control valve 30 corresponds here in its function and structure to the control valve 30, which is shown in FIG. 1 or FIGS. 2a to 2c.
- the inner control chamber 54 which is connected to the control valve chamber 60 via the inner outlet throttle 51, is delimited by the end of the valve inner needle 15 facing away from the valve seat and the bottom of the bore 39.
- the inner control chamber 54 is connected to the outer inlet throttle 49, which in turn opens into the high-pressure region, that is to say into the inlet channel 8.
- the control valve chamber 60 can be connected to the leakage oil chamber 40 via the drain opening 68 in the same manner as shown in FIGS. 2a to 2c.
- the design of the fuel injection valve means that the outer control chamber 56 is always separated from the inner control chamber 54.
- the operation of the control rooms 54, 56 and their control by the control valve 30 are, however, the same as in the exemplary embodiment shown in FIG. 1.
- the valve member 62 is also moved here from the first to the third switching position, as shown in FIG. 2c.
- the valve member 62 comes into contact with its second sealing surface 76 on the second valve seat 72, which is formed here in the throttle disk 7.
- the inner outlet throttle 51 is thus closed and the connection of the control valve chamber 60 to the leakage oil chamber 40 is opened via the outlet opening 68.
- the pressure in the outer control chamber 56 drops and the valve outer needle 17 opens in the known manner already described above.
- the pressure shoulder 13, which is not shown in FIG. 4, is formed closer to the valve seat than in the embodiment shown in FIG. 1.
- valve member 62 remains in the third switching position, the high pressure remains in the inner control chamber 54, and a fuel flow through the annular gap between the wall of the bore 39 and the inner valve needle 15 is prevented by the second annular groove 78, which is always depressurized via the outlet channel 58, prevented by diverting any fuel that might penetrate. To end the Injection, the valve member 62 is in turn quickly moved back into the first switching position.
- valve member 62 For injection via all injection openings 26, 28, the valve member 62 is moved into the second switching position, as shown in FIG. 2b.
- both the inner discharge throttle 51 and the outer discharge throttle 49 are turned on in the same way as already described above, as a result of which the pressure drops both in the inner control chamber 54 and in the outer control chamber 56.
- the valve outer needle 17 and the valve inner needle 15 open in quick succession and open all the injection openings 26, 28.
- control spaces 54, 56 fill again with fuel under high pressure, so that the outer valve needle 17 and the inner valve needle 15 slide back into their closed position.
- the pressure drop in the outer control chamber 56 cannot be varied, so that the pressure there drops at the same rate with each opening movement.
- the outer valve needle 17 always opens at approximately the same opening speed.
- valve member 62 can also be moved by another drive which allows the valve member 62 to be moved in the linear direction and to be moved into the first, second and third switching positions.
- Piezo actuators are very suitable for this, however, because they work very quickly and can start any length change between their maximum deflections.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE2003138228 DE10338228A1 (en) | 2003-08-20 | 2003-08-20 | Fuel injection valve for internal combustion engines |
PCT/DE2004/001306 WO2005019638A1 (en) | 2003-08-20 | 2004-06-22 | Fuel injection valve for internal combustion engines |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1658427A1 true EP1658427A1 (en) | 2006-05-24 |
EP1658427B1 EP1658427B1 (en) | 2008-02-13 |
Family
ID=34177708
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04738755A Expired - Fee Related EP1658427B1 (en) | 2003-08-20 | 2004-06-22 | Fuel injection valve for internal combustion engines |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP1658427B1 (en) |
DE (2) | DE10338228A1 (en) |
WO (1) | WO2005019638A1 (en) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10357769B4 (en) * | 2003-12-10 | 2007-06-21 | Siemens Ag | Fuel injection valve |
DE102004030448A1 (en) * | 2004-06-24 | 2006-01-12 | Robert Bosch Gmbh | Fuel injector |
DE102004051756A1 (en) | 2004-10-23 | 2006-04-27 | Robert Bosch Gmbh | Fuel injection valve for internal combustion engines |
DE102004061800A1 (en) * | 2004-12-22 | 2006-07-06 | Robert Bosch Gmbh | Injector of a fuel injection system of an internal combustion engine |
DE102005020832A1 (en) * | 2005-05-04 | 2006-11-09 | Robert Bosch Gmbh | Automotive fuel injection jet has two sliding needles both linked to a common fuel flow regulation chamber |
DE102007002281A1 (en) | 2007-01-16 | 2008-07-17 | Robert Bosch Gmbh | Injector for fuel injection system of internal-combustion engine in motor vehicle, has guidance for servo piston designed at separation element and limiting coupler space together with separation element and piston |
DE102008001330A1 (en) * | 2008-04-23 | 2009-10-29 | Robert Bosch Gmbh | Fuel injection valve for internal combustion engines |
DE102014209961A1 (en) * | 2014-05-26 | 2015-11-26 | Robert Bosch Gmbh | Nozzle assembly for a fuel injector and fuel injector |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4221913B2 (en) * | 2001-04-26 | 2009-02-12 | トヨタ自動車株式会社 | Fuel injection device |
DE10122241A1 (en) * | 2001-05-08 | 2002-12-05 | Bosch Gmbh Robert | Fuel injection valve for internal combustion engines |
DE10210927A1 (en) * | 2002-03-13 | 2003-10-02 | Bosch Gmbh Robert | Fuel injection valve for internal combustion engines |
-
2003
- 2003-08-20 DE DE2003138228 patent/DE10338228A1/en not_active Withdrawn
-
2004
- 2004-06-22 EP EP04738755A patent/EP1658427B1/en not_active Expired - Fee Related
- 2004-06-22 WO PCT/DE2004/001306 patent/WO2005019638A1/en active IP Right Grant
- 2004-06-22 DE DE502004006203T patent/DE502004006203D1/en active Active
Non-Patent Citations (1)
Title |
---|
See references of WO2005019638A1 * |
Also Published As
Publication number | Publication date |
---|---|
EP1658427B1 (en) | 2008-02-13 |
DE10338228A1 (en) | 2005-03-10 |
WO2005019638A1 (en) | 2005-03-03 |
DE502004006203D1 (en) | 2008-03-27 |
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