EP0970305B1 - Einspritzventil mit steuerventil - Google Patents
Einspritzventil mit steuerventil Download PDFInfo
- Publication number
- EP0970305B1 EP0970305B1 EP98966221A EP98966221A EP0970305B1 EP 0970305 B1 EP0970305 B1 EP 0970305B1 EP 98966221 A EP98966221 A EP 98966221A EP 98966221 A EP98966221 A EP 98966221A EP 0970305 B1 EP0970305 B1 EP 0970305B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- control chamber
- drain
- control
- closing element
- valve
- 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.)
- Expired - Lifetime
Links
- 238000002347 injection Methods 0.000 title description 21
- 239000007924 injection Substances 0.000 title description 21
- 238000007789 sealing Methods 0.000 claims description 37
- 239000000446 fuel Substances 0.000 claims description 27
- 230000006835 compression Effects 0.000 description 15
- 238000007906 compression Methods 0.000 description 15
- 239000002828 fuel tank Substances 0.000 description 4
- 238000011161 development Methods 0.000 description 3
- 230000018109 developmental process Effects 0.000 description 3
- 238000002485 combustion reaction Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 1
- 238000009795 derivation Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 230000000284 resting effect Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
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
- 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
- F02M2200/21—Fuel-injection apparatus with piezoelectric or magnetostrictive elements
Definitions
- the invention relates to an injection valve with a control valve according to the preamble of claim 1
- Injectors with a control valve are, for example used in a common rail injection system to the Control pressure in a control chamber, the pressure in the control chamber via a control piston onto an injection needle acts depending on the pressure of one Valve seat lifts off, and thereby fuel into an internal combustion engine is injected.
- EP 0 604 915 A1 already discloses an injection valve with a Control valve known in which a control chamber via a Throttle is connected to a drain by a control valve is controlled.
- the control valve has a closing member on that is associated with a valve seat that at the end the throttle is formed.
- the closing element is over spring elements from the low pressure side onto the valve seat pressed.
- An electromagnet is provided, which Closing member lifts off the associated valve seat, creating a Injection process is started.
- the injector described has the disadvantage, however, that the throttle at one Break of the spring elements is open.
- EP 0 826 876 A1 is the closest prior art an injector with a control valve known that a Has closing member which is assigned to a valve seat and that is connected to a piston that is connected to an actuator is in operative connection.
- the piston is of an annular shape Spring holder partially enclosed, with which a spring element is in operative connection so that the closing member over the piston from the low pressure side onto the valve seat is pressed.
- the closing element and the valve seat are open attached to the high pressure side.
- the object of the invention is an injection valve to provide with a control valve that the flow restrictor the control chamber closes reliably.
- An advantage of the invention is that the closing member of the control valve is arranged on the high pressure side and of the pressure in the control chamber pressed against the valve seat becomes. Another advantage is that the Locking element even if the pretensioning device is damaged the drain is closed securely.
- Another advantage of the invention is that the closing member is connected via a valve tappet with a small diameter to an actuator piston which has a larger diameter.
- the valve lifter is guided through a drain hole which has a correspondingly small diameter. Due to the large diameter, the actuator piston has great rigidity, so that the closing member can be moved precisely and quickly by an actuator that controls the actuator piston. Since the drain hole has a small diameter, the closing member can also be made correspondingly small, so that only a small force is required to move the closing member against the pressure in the control chamber and thereby open or close the drain hole.
- FIG. 1 schematically shows part of an injection valve, in which a control valve is arranged.
- a control valve for the sake of simplicity is only the control valve and not the entire injector shown.
- the functioning and structure of a corresponding injector is, for example, in EP 0 604 915 A1.
- the control valve has a control chamber 1, which has a Inlet throttle 4 in connection with a fuel inlet 3 stands.
- the control chamber 1 is delimited by a control piston 2, which is movably arranged in a piston bore 35 and which is connected to an injection needle.
- the control chamber 1 has a drain hole 5 which leads to a second recess 8 is guided via a derivative is connected to the fuel tank.
- the second recess 8 goes up into a wider guide bore 34.
- In the control chamber 1 has a first closing element 10, which merges into a valve rod 11 through the drain hole 5 is guided into the second recess 8.
- a spring plate 13 is inserted in the second recess 8, which extends into the guide bore 35.
- the Spring plate 13 has a U-shape with a base plate 16 is completed.
- the bottom plate 16 is the drain hole 5 assigned.
- the valve rod 11 is in the second recess 8 through a central bore 27 of the base plate 16 out.
- the valve rod 11 preferably closes flush with the top of the bottom plate 16 and is preferred over a weld 17 in this area with the Bottom plate 16 connected.
- the bottom plate 16 merges into a sleeve 28 which an angled stop ring in the upper end area 29 has.
- the second recess 8 and the first recess 7, which forms part of the control chamber 1 preferably introduced into a valve plate 6.
- the valve plate 6 is non-positively connected to the housing 36 of the injection valve connected.
- a spring element preferably a compression spring 14 introduced under tension, so that in the rest position the first closing member 10 upwards in the direction of the drain hole 5 against an associated, first sealing seat 25 is pressed.
- too other spring means such as a disc spring can be used.
- the first sealing seat 25 is part of the wall surface of the control chamber formed in the entrance area to the drain hole 5.
- the drain hole 5 preferably provides a drain throttle However, in a further development of the invention the discharge throttle be formed after the discharge hole.
- the drain hole is in the rest position by the compression spring 14 5 closed by the first closing member 10. Moreover this embodiment offers the advantage that at one Failure of the compression spring 14, the spring plate 13 or the valve rod 11 the first closing member 10 from the pressure in the control chamber 1 prevails against the first sealing seat 25 is pressed and thereby the first closing member 10 the first Sealing seat 25 closes self-locking.
- the bottom plate 16, the sleeve 28 and the stop ring 29 form the spring plate 13, in its cylindrical cavity an actuator piston 12 is inserted with its end face abuts the bottom plate 16.
- the actuator piston 12 is movable arranged in the spring plate 13 and stands with an actuator, for example a piezoelectric actuator, in operative connection, that moves the actuator piston.
- the first sealing seat 25 is preferably designed as a conical seat.
- the first closing member 10 is partially spherical, the partial spherical shape associated with the first sealing seat 25 is.
- the partial spherical shape is centered on the upper vertex into the cylindrical shape of the valve rod 11.
- the part-spherical Shell surface of the first closing member 10 is adapted to the shape of the first sealing seat 25.
- the flow rate that flows through the drain hole 5 is determined by the annular drain channel 30, the results from the drain hole 5 and the rod 11.
- the drain channel 30 is designed in such a way that the drain channel 30 acts as a drain throttle.
- the small diameter of the drain hole 5 now brings that Disadvantage that the valve rod through the drain hole is guided, an even smaller diameter having. Due to the small diameter, the valve stem has 10 low rigidity. This is disadvantageous for one fast and precise control of the first closing element 10.
- the discharge throttle 5 as short as possible to make the valve rod 11 as short as possible can be trained.
- the overall drive, which results from the valve rod, is harder 11 and the actuator piston 12.
- the actuator piston 12 is located outside of the control chamber in a second Recess 8, which is connected to a guide bore 35.
- the actuator piston 12 can have a larger diameter be formed so that the elasticity of the actuator piston 12 is less than that of the valve rod 11. Since the actuator piston is harder than the valve rod 11, the length of the actuator piston 12 for the adjustment of the elastic properties of little importance.
- a further optimization of the control valve is achieved that the first closing member 10 of the shape of the control chamber 1 is adapted in such a way that the control volume in the Control chamber 1, which is not filled by the first closing member 10 is as small as possible. This makes it quick It is possible to empty and fill the control chamber, which makes the Switching times in which pressure is up or down in the control chamber is reduced, minimized. As a result, the switching times, with which the control piston 2 and thus the injection needle are moved, minimized.
- the control chamber preferably has a cylindrical shape, which changes into a cone shape in the upper area, and the thus in the direction of the centrally arranged drain hole 5 tapered.
- the conical shape represents the first sealing seat 25
- the first closing member 10 is preferably part-spherical formed, the diameter of the partial spherical shape somewhat is smaller than the diameter of the cylindrical shape Control chamber 1.
- the flat cutting surface on the underside of the first closing member 10 is parallel to the flat end surface of the control piston 1 and the end face of the Control piston 1 facing.
- the control chamber 1 is preferred formed in length so that when fully open first closing member 10, i.e. at maximum deflection of the first closing member 10, the closing member 10 is not on pushes the control piston 2 so that the control volume as possible is kept small. This tuning can be carried out precisely be because the cut surface of the first closing member and the end face of the spool is flat and parallel to each other are arranged.
- the operation of the control valve according to Figure 1 is as follows: The first closing member 10 is in the rest position pressed against the first sealing seat 25 by the compression spring 14, so that the drain hole 5 is closed. In order to is the control chamber 1 only via the inlet throttle 4 with the Fuel inlet 3 connected. In this state there is the control chamber 1 the same fuel pressure as in Fuel supply 3. As a result, the control piston is 2 acted upon by the high fuel pressure of the fuel inlet 3 and is pressed down with the appropriate force. The control piston 2 in turn presses an injection needle on an associated sealing seat so that no fuel is injected.
- the actuator piston 12 is removed from the assigned actuator is moved up to the rest position, so that the first closing member 10 essentially of the compression spring 14 pressed against the first sealing seat 25 becomes.
- the pressure is in the control chamber 1 at this time too low to make a noticeable contribution to closing the flow restrictor 5 to contribute. So that the drain hole 5 is closed and in the control chamber 1 turns out after some Time again the fuel pressure in the fuel supply 3 prevails, since fuel flows into the via the inlet throttle Control chamber 1 flows.
- the control piston is through the adjusting high pressure moves back down so that also the injection needle back on the assigned sealing seat is pressed, thus interrupting the injection of fuel becomes.
- the fuel pressure drops when the drain hole 5 is open, because more fuel flows through the drain hole 5 than flows through the inlet throttle 4.
- the drain hole 5 is dimensioned accordingly and preferably provides a flow restrictor represents.
- the arrangement according to FIG. 1 offers the advantage that the control volume is small in the control chamber 1, and thus the drain hole 5 opened faster and closed faster can be, since only the first closing member 10 in the control chamber 1 is arranged.
- the volume is under control volume the control chamber 1, which is filled with fuel can be.
- the compression spring 14, because of the large bias required is relatively large, is preferably outside the control chamber 1 and thus does not affect the control volume the control chamber 1.
- first closing member is essentially spherical. This has the advantage that the spherical closing member on a conical first sealing seat when closing of the first sealing seat 25 independently due to the spherical shape adjusted.
- the first closing member 10 can also in the sealing area preferably be conical, the Cone shape of the first closing member 10 to the cone shape of the first Sealing seat 25 is assigned symmetrically. At this Embodiment, however, the first closing member 25 should be in the middle and are guided symmetrically to the first sealing seat 25, so that the first sealing seat 25 is closed precisely.
- the dimensioning of the drain hole is particularly advantageous 5 or the discharge channel 30 as a discharge throttle, whereby an additional outlet throttle is saved, and the outlet throttle directly adjacent to the control chamber, creating a low tax volume is achieved.
- Derivation recess 37 is provided so that fuel from the Drain hole 5 even with the bottom plate 16 resting on the drain can drain, since the base plate 16 in the working position rests on the valve plate 6.
- the actuator piston 12 directly on the Valve rod 11 on, the valve rod 11 as short as possible is formed and nevertheless a relatively large compression spring 14 can be used. This creates a large contact pressure in the rest position for securely sealing the first sealing seat 25 guaranteed.
- An advantageous embodiment is a pre-assembled and to provide preset control valve unit, the throttle plate 6 with the drain hole 5 and with the first sealing seat 25, the first closing member 10 with the Valve rod 11, which is guided through the drain hole 5, the spring plate 13 to which the valve rod 11 is connected is, and the spring element 14, which between the spring plate 13 and the throttle plate 6 introduced biased is.
- the throttle plate 6 preferably has the first recess 7, which represents at least part of the control chamber 1. Furthermore, in one embodiment, a second recess 8 for receiving the spring plate 13 in the Throttle plate 6 may be incorporated.
- the control valve unit has the advantage that the individual Components are pre-assembled, and that an adjustment of maximum stroke of the first closing member 10 is made.
- the spring plate 13 from one side against the Spring force of the spring element 14 against the throttle plate 6 pressed and the first closing member 10 from the other side with the valve rod 11 through the drain hole 5 into the hole 27 pushed the bottom plate 16.
- the valve rod 11 becomes fixed to the base plate 16 welded. This is preferably done using laser welding. The laser beam falls over the open U-shape of the spring plate 13 and welds the valve rod 11 on the Top of the bottom plate 16 with a weld 17 with the Base plate 16.
- Figure 2 shows schematically an injection valve with a Control valve in which the essential Differences compared to Figure 1 in the form of Closing member, the shape of the spring plate and an outlet throttle 23 lie.
- a second closing member 19 is one assigned second sealing seat 26, the second sealing seat 26 and the associated second sealing surface 31 of the second Closing member 19 are formed as plane-parallel surfaces, that are associated with each other.
- the second closing member 19 has essentially the shape of a T-piece, which in a second rod 20 passes through the drain hole 5 and through a second bore 32 of a second spring plate 21 is guided up to the top of the second spring plate 21.
- the second spring plate 21 At the top of the second spring plate 21 is the second Rod 20 via a second weld 24 to the second Spring plate 21 connected.
- the second spring plate is in the designed essentially cylindrical and points in the upper End area a second stop ring 33. Between the second stop ring 33 and the valve plate 6 is one Compression spring 14 clamped, the second closing member 19th biased upward against the second sealing seat 26.
- the second spring plate 21 On the top of the second spring plate 21 there is a second one Actuator piston 22.
- the second actuator piston 22 and the second spring plate 21 are in a guide bore 34 of the injector.
- the guide bore 34 extends a drain line from a drain throttle 23 to Fuel tank is guided.
- a discharge duct 37 is provided in the lower area, that from the mouth of the drain hole 5 to the edge region in which the compression spring 14 is arranged is.
- the outlet throttle 23 can also be used 5 or the drain channel 30 is designed as a drain throttle his.
- the arrangement according to FIG. 2 works as follows: In the rest position is the second closing member 19 through the Compression spring 14 with the second sealing surface 31 against the second Sealing seat 26 pressed and thus the drain hole 5 closed. So there is in the rest position in the control chamber 1 the same fuel pressure as in the fuel supply 3 is present. Consequently, the control piston 2 with a correspondingly large pressure.
- the second actuator piston 22 is assigned by the Actuator moved down towards drain hole 5, so the second closing member 19 gives the drain channel 30 free, in the drain hole 5 from the free space results that the second rod 20 does not fill.
- the derivative and the outlet throttle 23 to the fuel tank back. Since the inlet throttle 4 has a smaller cross section has as the outlet throttle 23, the fuel pressure drops in the control chamber 1.
- the drain channel 30 with such a large flow cross section, that the throttle function by the discharge throttle 23rd is pictured. Consequently, the force on the spool increases 2 acts.
- the flow restrictor can 23 omitted and the function of the outlet throttle 23 is by appropriate dimensioning of the drain channel 30 reached.
- a control valve unit can be used that made the throttle plate 6 with the second closing member 19, that via the second spring plate 21 and a spring means 14 is biased and by determining the distance between the second closing member 19 and the second spring plate 21 is set to a defined maximum stroke.
- the invention was based on the example of a control chamber with a Inlet and an outlet throttle described, but the Invention is applicable to any type of injection valve.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Description
Ein weiterer Vorteil der Erfindung beruht darin, daß das Schließglied über einen Ventilstößel mit einem kleinen Durchmesser mit einem Aktorkolben verbunden ist, der einen größeren Durchmesser aufweist. Der Ventilstößel ist durch eine Ablaufbohrung geführt, die einen entsprechend kleinen Durchmesser aufweist. Der Aktorkolben weist aufgrund des großen Durchmessers eine große Steifigkeit auf, so daß das Schließglied von einem Aktor, der den Aktorkolben steuert, präzise und schnelle bewegt werden kann. Da die Ablaufbohrung einen kleinen Durchmesser aufweist, kann auch das Schließglied entsprechend klein ausgebildet werden, so daß nur eine geringe Kraft notwendig ist, um das Schließglied gegen den Druck in der Steuerkammer zu bewegen, und dadurch die Ablaufbohrung zu öffnen oder zu schließen.
Claims (6)
- Einspritzventil mit einem Gehäuse (36), in das eine Steuerkammer (1) eingebracht ist,
mit einem Steuerkolben (2), der die Steuerkammer (1) begrenzt und verschiebbar im Gehäuse (36) angeordnet ist,
mit einem Zulauf (4), der die Steuerkammer (1) mit Druckmittel, insbesondere mit Kraftstoff versorgt,
mit einem Ablauf (5,37), über den Druckmittel aus der Steuerkammer abfließt,
mit einem Schließglied (10,19), das einem Dichtsitz (25,26) des Ablaufs (5) zugeordnet ist, und das den Ablauf (5) öffnet oder schließt,
mit einem Steuermittel, das außerhalb der Steuerkammer (1) angeordnet ist, und das in Wirkverbindung mit dem Schließglied (10,19) steht, wobei
der Dichtsitz (25,26) auf der Hochdruckseite ausgebildet ist, das Schließglied (10,19) auf der Hochdruckseite angeordnet ist,
das Schließglied (10,19) mit einer Ventilstange (11,20) verbunden ist,
die Ventilstange (11,20) durch den Ablauf (5) geführt ist, die Ventilstange (11,20) mit dem Steuermittel in Wirkverbindung steht,
das Schließglied (10,19) in der Steuerkammmer (1) angeordnet ist und das Schließglied (11,19) von einem Federmittel (14), das außerhalb der Steuerkammer (1) angeordnet ist, gegen den Dichtsitz (25,26) vorgespannt ist,
dadurch gekennzeichnet, daßdie Ventilstange (11,20) auf der Niederdruckseite mit einem Federhalter (13) verbunden ist,das Federmittel (14) zwischen den Federhalter (13) und das Gehäuse (36) gespannt ist, so daß das Schließglied (11,19) gegen den Dichtsitz (25,26) gedrückt ist,der Federhalter (13) in Form einer Hülse ausgebildet ist, die an einem Ende eine Bodenplatte (16) aufweist, die die Hülsenform abschließt, und die dem Ablauf (5) zugeordnet ist,die Bodenplatte (16) mit der Ventilstange (11) verbunden ist, undin die Hohlform der Hülse ein Aktorkolben (12) eingeschoben ist, der in Wirkverbindung mit dem Steuermittel steht. - Einspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß die Bodenplatte (16) eine Bohrung (27) aufweist, daß die Ventilstange (11) in die Bohrung (27) geführt ist, und daß die Ventilstange (11) im oberen Bereich der Bodenplatte (16) mit der Bodenplatte (16) verbunden ist.
- Einspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß der Ablauf (5) als Drossel ausgebildet ist.
- Einspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß eine Platte (6) vorgesehen ist, in die der Ablauf (5) eingebracht ist, daß in der Platte (6) eine zweite Ausnehmung (8) zur teilweisen Aufnahme eines Federhalters (13) ausgebildet ist, und
daß eine erste Ausnehmung (7) zur mindestens teilweisen Ausbildung der Steuerkammer (1) und zur Ausbildung des Dichtsitzes (25,26) ausgebildet ist. - Einspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß die Form des Schließgliedes (10,19) an die Form der Steuerkammer (1) in der Weise angepaßt ist, daß das Steuervolumen der Steuerkammmer (1) klein gehalten ist.
- Einspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß eine Steuerventil-Einheit vorgesehen ist,die eine Platte (6) aufweist, in die der Ablauf (5) eingebracht ist,die das Schließglied (10) mit der Ventilstange (11) aufweist, die durch den Ablauf (5) geführt ist,die den Federhalter (13) aufweist, mit dem die Ventilstange (11) verbunden ist,die ein Federlement (14) aufweist, das zwischen dem Federhalter (13) und der Platte (6) eingespannt ist, und das Schließglied (10) gegen den Dichtsitz (25) vorspannt, wobei der Abstand zwischen dem Schließglied (10) und dem Federhalter (13) auf einen vorgegebenen Wert festgelegt ist, so daß ein maximaler Hub des Schließgliedes (10) eingestellt ist.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19757656 | 1997-12-23 | ||
DE19757656 | 1997-12-23 | ||
PCT/DE1998/003746 WO1999034111A1 (de) | 1997-12-23 | 1998-12-18 | Einspritzventil mit steuerventil |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0970305A1 EP0970305A1 (de) | 2000-01-12 |
EP0970305B1 true EP0970305B1 (de) | 2003-05-21 |
Family
ID=7853253
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98966221A Expired - Lifetime EP0970305B1 (de) | 1997-12-23 | 1998-12-18 | Einspritzventil mit steuerventil |
Country Status (4)
Country | Link |
---|---|
US (1) | US6168132B1 (de) |
EP (1) | EP0970305B1 (de) |
DE (1) | DE59808465D1 (de) |
WO (1) | WO1999034111A1 (de) |
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DE19937677C2 (de) * | 1999-08-10 | 2003-06-26 | Siemens Ag | Einspritzventil mit verbesserter Dichtflächenanordnung |
DE19939419A1 (de) * | 1999-08-20 | 2001-03-01 | Bosch Gmbh Robert | Kraftstoffeinspritzeinrichtung |
DE19945314A1 (de) * | 1999-09-22 | 2001-04-05 | Bosch Gmbh Robert | Common-Rail-Injektor |
DE10003863B4 (de) * | 2000-01-28 | 2004-11-18 | Robert Bosch Gmbh | Einspritzdüse |
AUPQ708200A0 (en) * | 2000-04-20 | 2000-05-18 | Orbital Engine Company (Australia) Proprietary Limited | Deposit control in fuel injector nozzles |
US6647966B2 (en) * | 2001-09-21 | 2003-11-18 | Caterpillar Inc | Common rail fuel injection system and fuel injector for same |
DE10148874C2 (de) * | 2001-10-04 | 2003-12-24 | Siemens Ag | Düseneinrichtung, insbesondere zur Kraftstoffeinspritzung |
DE10149286C2 (de) * | 2001-10-05 | 2003-12-11 | Siemens Ag | Düseneinrichtung, insbesondere zur Kraftstoffeinspritzung |
DE10160263A1 (de) * | 2001-12-07 | 2003-06-18 | Bosch Gmbh Robert | Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine |
US6837221B2 (en) | 2001-12-11 | 2005-01-04 | Cummins Inc. | Fuel injector with feedback control |
US6647964B1 (en) * | 2002-06-14 | 2003-11-18 | Caterpillar Inc | End of injection pressure reduction |
GB0215490D0 (en) * | 2002-07-04 | 2002-08-14 | Delphi Tech Inc | Control valve arrangement |
DE102004045249A1 (de) * | 2004-09-17 | 2006-03-23 | Robert Bosch Gmbh | Kraftstoffeinspritzvorrichtung |
DE102005029472B4 (de) * | 2005-06-24 | 2009-09-17 | Continental Automotive Gmbh | Einspritzventil zum Einspritzen von Dieselkraftstoff in eine Brennkraftmaschine |
DE102006057425A1 (de) * | 2006-05-23 | 2007-11-29 | Robert Bosch Gmbh | Vorrichtung zur Regeneration, zur Temperaturbeaufschlagung und/oder zum Thermomanagement, zugehöriges Einspritzventil und Verfahren |
DE102006049885A1 (de) * | 2006-10-23 | 2008-04-24 | Robert Bosch Gmbh | Injektor zur Einspritzung von Kraftstoff in Brennräume von Brennkraftmaschinen |
DE102007042466B3 (de) | 2007-09-06 | 2009-04-09 | Continental Automotive Gmbh | Einspritzsystem mit reduzierter Schaltleckage und Verfahren zum Herstellen eines Einspritzsystems |
DE102008032385B4 (de) * | 2008-07-09 | 2018-03-29 | Audi Ag | Hochdruckeinspritzanordnung für eine direkteinspritzende Brennkraftmaschine |
DE102008040637A1 (de) * | 2008-07-23 | 2010-01-28 | Robert Bosch Gmbh | Kraftstoffeinspritzventileinrichtung |
DE102012212264B4 (de) | 2012-07-13 | 2014-02-13 | Continental Automotive Gmbh | Verfahren zum Herstellen eines Festkörperaktuators |
DE102012212266B4 (de) * | 2012-07-13 | 2015-01-22 | Continental Automotive Gmbh | Fluidinjektor |
EP2975257B1 (de) * | 2014-07-18 | 2018-01-10 | Continental Automotive GmbH | Steuereinheit zur Steuerung einer Ventilnadel eines Kraftstoffeinspritzventils und Kraftstoffeinspritzventil |
JP2019148192A (ja) * | 2018-02-26 | 2019-09-05 | 株式会社Soken | 燃料噴射装置 |
IT201900001413A1 (it) * | 2019-01-31 | 2020-07-31 | Bosch Gmbh Robert | Valvola di aspirazione per una pompa di alta pressione di alimentazione di carburante ad un motore a combustione interna e pompa comprendente tale valvola |
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JPH01224454A (ja) * | 1988-03-04 | 1989-09-07 | Yamaha Motor Co Ltd | エンジンの高圧燃料噴射装置 |
JPH0286953A (ja) * | 1988-09-21 | 1990-03-27 | Kanesaka Gijutsu Kenkyusho:Kk | 燃料噴射弁 |
US5271599A (en) * | 1990-09-28 | 1993-12-21 | Kolchinsky Abel E | Modular solenoid valve |
IT1257958B (it) | 1992-12-29 | 1996-02-19 | Mario Ricco | Dispositivo di registrazione di una valvola di dosaggio a comando elettromagnetico, per un iniettore di combustibile |
DE4341546A1 (de) * | 1993-12-07 | 1995-06-08 | Bosch Gmbh Robert | Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen |
JPH08158981A (ja) * | 1994-12-02 | 1996-06-18 | Nippondenso Co Ltd | 燃料噴射装置 |
US5526791A (en) * | 1995-06-07 | 1996-06-18 | Diesel Technology Company | High-pressure electromagnetic fuel injector |
DE19624001A1 (de) * | 1996-06-15 | 1997-12-18 | Bosch Gmbh Robert | Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen |
US5779149A (en) * | 1996-07-02 | 1998-07-14 | Siemens Automotive Corporation | Piezoelectric controlled common rail injector with hydraulic amplification of piezoelectric stroke |
JP3823391B2 (ja) | 1996-08-31 | 2006-09-20 | いすゞ自動車株式会社 | エンジンの燃料噴射装置 |
US5875764A (en) * | 1998-05-13 | 1999-03-02 | Siemens Aktiengesellschaft | Apparatus and method for valve control |
-
1998
- 1998-12-18 WO PCT/DE1998/003746 patent/WO1999034111A1/de active IP Right Grant
- 1998-12-18 DE DE59808465T patent/DE59808465D1/de not_active Expired - Lifetime
- 1998-12-18 EP EP98966221A patent/EP0970305B1/de not_active Expired - Lifetime
-
1999
- 1999-08-23 US US09/379,219 patent/US6168132B1/en not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
US6168132B1 (en) | 2001-01-02 |
DE59808465D1 (de) | 2003-06-26 |
WO1999034111A1 (de) | 1999-07-08 |
EP0970305A1 (de) | 2000-01-12 |
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