EP1406006A1 - Brennstoffeinspritzventil - Google Patents
Brennstoffeinspritzventil Download PDFInfo
- Publication number
- EP1406006A1 EP1406006A1 EP03022035A EP03022035A EP1406006A1 EP 1406006 A1 EP1406006 A1 EP 1406006A1 EP 03022035 A EP03022035 A EP 03022035A EP 03022035 A EP03022035 A EP 03022035A EP 1406006 A1 EP1406006 A1 EP 1406006A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- fuel injection
- injection valve
- piston
- coupler
- 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
- 239000000446 fuel Substances 0.000 title claims description 67
- 238000002347 injection Methods 0.000 title claims description 26
- 239000007924 injection Substances 0.000 title claims description 26
- 238000007789 sealing Methods 0.000 claims description 6
- 238000002485 combustion reaction Methods 0.000 claims description 3
- 238000000227 grinding Methods 0.000 claims description 3
- 239000012530 fluid Substances 0.000 description 10
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000005284 excitation Effects 0.000 description 2
- 230000003044 adaptive effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000011038 discontinuous diafiltration by volume reduction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002996 emotional effect Effects 0.000 description 1
- 230000005281 excited state Effects 0.000 description 1
- 230000016507 interphase Effects 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 239000000126 substance Substances 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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
-
- 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
- F02M51/00—Fuel-injection apparatus characterised by being operated electrically
- F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
- F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
-
- 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
- F02M61/167—Means for compensating clearance or thermal expansion
Definitions
- the invention is based on a fuel injector according to the genus of the main claim.
- EP 0 477 400 A1 describes an arrangement for an in Adaptive mechanical acting stroke direction Tolerance compensation for a displacement transformer piezoelectric actuator for a fuel injector known.
- the actuator acts on a master piston that is connected to a hydraulic chamber.
- About the Pressure increase in the hydraulic chamber becomes a slave piston which moves a mass to be driven, to be positioned emotional.
- This mass to be driven is, for example Valve needle of a fuel injector.
- the hydraulic chamber is filled with a hydraulic fluid. With an expansion of the actuator and compression of the Hydraulic fluid in the hydraulic chamber flows a little Part of the hydraulic fluid with a defined leak rate. In the resting phase of the actuator, this hydraulic fluid added.
- DE 195 00 706 A1 describes a hydraulic one Known displacement transformer for a piezoelectric actuator, where a master piston and a slave piston in one common axis of symmetry are arranged and the Hydraulic chamber is arranged between the two pistons.
- a spring is arranged, which Pushes master cylinder and slave piston apart, whereby the master piston in the direction of the actuator and the slave piston in one working direction towards a valve needle be biased.
- this lifting movement is carried out by the Pressure of a hydraulic fluid in the hydraulic chamber on the Transfer slave piston because the hydraulic fluid in the Hydraulic chamber can not be compressed and only one low proportion of hydraulic fluid due to annular gaps between master piston and a guide bore and Slave piston and a pilot hole during the short Period of a stroke can escape.
- a disadvantage of this known prior art is that during a discharge period in which Hydraulic chamber there is no high pressure Hydraulic fluid can evaporate. However, there is a gas compressible and builds only with a strong one Volume reduction a correspondingly high pressure. The Master cylinder can now be pressed into its guide hole be, without there being a power transmission to the Master piston comes.
- a further disadvantage is that cavitation of the Fuel can come when the spring has a high tension exercises on the master cylinder and slave cylinder and the Movement of the actuator to its starting position very quickly he follows. The negative pressure that forms in the hydraulic chamber can then lead to cavitation and the resulting damage lead on components.
- the fuel injector according to the invention with the has characteristic features of the main claim in contrast, the advantage that a filling valve, which a Throttle bore in a master piston or slave piston of the hydraulic coupler, a valve seat and one with it cooperating valve body includes the fast Filling the coupler gap between the encoder and the Slave piston allows without the above mentioned disadvantages arise.
- the valve body is advantageously in one with the Actuator in non-positive connection Gimbaled actuator so that offsets can be compensated.
- the throttle bore ensures that the Coupler gap can be filled quickly enough without too much pressure of the hydraulic medium to one unintentional opening of the fuel injector can lead.
- the valve seat is ring-shaped in a simple manner and can on the valve body or on the encoder or Slave piston be arranged.
- the Sealing seat of the filling valve on the slave piston and the Valve body on the valve needle of the Fuel injector trained. This is a very simple and therefore inexpensive variant of the Filling valve.
- the master and slave pistons of the hydraulic coupler are advantageously hollow cylindrical, which reduces their mass and the switching dynamics of the Fuel injector is positively influenced.
- Fig. 1 shows a schematic section through the spray-side part of a first embodiment of a fuel injector 1 according to the invention.
- the fuel injection valve 1 comprises an actuator 2, which is preferably a piezoelectric actuator 2 is trained.
- the actuator 2 is to protect against Tensile load and chemical influence of the fuel in encapsulated a sleeve 3. That from the sleeve 3, the actuator 2 and one clamped in the sleeve 3 against the actuator 2
- Preload spring 4 existing component can be pre-assembled and then into a housing 5 of the fuel injection valve 1 be introduced. The fully assembled component is through a support ring 6 fixed in the housing 5.
- the actuating element 7 and the sleeve 3 are against by means of a corrugated tube seal 8 flowing through the fuel injector 1 Fuel sealed.
- the actuating element 7 extends into a master piston 9 of a hydraulic coupler 10 of the fuel injector 1.
- the master piston 9 is executed hollow cylindrical, which in particular the Advantage of saving weight and resulting one has better switching dynamics of the fuel injector 1.
- Coupler gap 11 Downstream of the master piston 9 is forming a Coupler gap 11 is arranged a slave piston 12, which also to improve the switching dynamics in hollow cylindrical shape is executed.
- the components of the hydraulic coupler 10 are in a guide sleeve 13 arranged, which by means of a compression spring 14 relative to the Master piston 9 is clamped.
- the hydraulic coupler 10 can effect a stroke ratio depending on the requirement, as is the case in the illustrated embodiment , or only implement the stroke of actuator 2 1: 1.
- Hydraulic medium is used in the embodiment of the Fuel injector 1 flowing fuel.
- a valve needle 15 is connected to the slave piston 12 non-positively connected. It extends into Outflow direction in a valve group 16, which in any, the requirements of that Fuel injector 1 of sufficient type can.
- a valve closing body 22 is located on the valve needle 15 formed, which with a valve seat 23 to a Sealing seat interacts.
- a closing spring 24 acts the valve needle 15 against an outflow direction, so that the fuel injector 1 in the non-excited state of the Actuator 2 is kept closed.
- the Valve group 16 can, for example, by means of a Union nut 17 on the housing 5 of the Fuel injector 1 must be fixed.
- the valve group 16 is located in a nozzle body 26 through a Seal 27 against a cylinder head, not shown is sealed. Connects to the nozzle body 26 on the inlet side to a flange 28, which by means of a seal 29 is sealed against the housing 5.
- Adjustment disc 30 is used to adjust the width of the Coupling gap 11.
- the hydraulic coupler 10 has a Filling valve 18, which for the rapid filling of the Coupling gap 11 when operating the fuel injector 1 cares.
- the filling valve 18 is in the embodiment from a throttle bore 19 in the master piston 9 and one Valve body 20 in the actuator 7, which the Throttle bore 19 in the closed state of the filling valve 18 covers.
- the valve body 20 has an annular Valve seat 21, which is turned off, for example the valve body 20 can be produced.
- Throttle bore 19 can alternatively or additionally also in the slave piston 12 be trained.
- valve body 20 Due to the special shape of the valve body 20 in Partial spherical shape with a corresponding guide in one spherical recess 25 in the actuating element 7 becomes a gimbal mounting of the valve body 20 achieved which can serve to offset the actuating element 7 compensate. In this way, malfunctions of the Filling valve 18 due to manufacturing tolerances or thermal Processes excluded.
- the filling valve 18 is when the Fuel injector 1 is actuated when the actuator 2 contracts. If the actuator 2 is no longer a Applied to excitation voltage, it pulls quickly together so that the valve needle 15 and the slave piston 12 and the master piston 9, which over the Actuating element 7 is actuated by the actuator 2, the Follow actuator 2 movement.
- the actuator 7 with the valve body 20 arranged therein lifts from the annular valve seat 21, so that fuel in the Coupler gap 11 flows and which during the operation of the Fuel injection valve 1 occurring leakage loss is balanced.
- the filling of the coupler gap 11 by the throttle bore 19 continues until the Compression spring 14 again against the master piston 9 Valve body 20 presses and the throttle bore 19 is closed becomes.
- the quick fillability of the coupler gap 11 contributes to this an improved switching dynamics of the Fuel injector 1 at.
- the filling can take place considerably faster than through leakage gaps.
- Fig. 2 shows a second embodiment of a Fuel injection valve 1 according to the invention in area II 1. Components already explained in FIG. 1 are provided with the same reference numerals.
- the cutout shows the area of the hydraulic coupler 10 with the Master piston 9 and slave piston 12.
- valve seat 21 of the Filling valve 18 on the valve body 20 of the filling valve 18 is formed
- the valve seat 21 is in the position in FIG. 2 illustrated second embodiment now on the master piston 9 in the form of an annular, the throttle bore 19th surrounding essay trained.
- Fig. 3 shows a third embodiment of a Fuel injector according to the invention 1. Already in 1 and 2 components are explained with the same Provide reference numerals. The section shows the area of the hydraulic coupler 10 with the master piston 9 and Slave piston 12.
- the filling valve 18 in Shape of a spherical valve body 20 with a Valve seat 21 is formed, the filling valve 18 is now with the valve needle 15 and one on the slave piston 12 trained valve seat 21.
- the valve body 20 is formed in one piece with the valve needle 15 and has lateral surface grindings 33. It is advantageous in particular the simple design of the valve body 20 the filling valve 18.
- the coupler gap 11 is emptied, the coupler gap 11 between the master piston 9 and slave piston 12 so smaller. Pulls off after injection Fuel from the fuel injector 1 through Shutdown of the excitation of the actuator 2 Actuator 7 back during the closing movement, lifts the valve needle 15 from the sealing seat 21 of the slave piston 12. By the force of one between the master piston 9 and the Slave piston 12 arranged disc spring 31 is the Refill the coupler gap 11 with coupler medium initiated. Fuel flows over the Surface grindings 33 on the valve needle 15 and on the Valve needle 15 formed valve body 20 over and through the filling hole 19 into the coupler gap 11. As soon as the valve needle 15 in the sealing seat 21 is the Refill completed.
- valve needle 15 is during the closing process by the closing spring 24, which is between the Nozzle body 26 and one formed on the valve needle 15 Flange 32 is clamped again in the sealing seat 21 pressed and the fuel injector 1 thereby closed.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
- Fig. 1
- eine schematische Darstellung des abspritzseitigen Teils eines ersten Ausführungsbeispiels eines erfindungsgemäßen Brennstoffeinspritzventils;
- Fig. 2
- ein zweites Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils entsprechend einer Variante im Bereich II in Fig. 1; und
- Fig. 3
- eine schematische Darstellung des mittleren Teils eines dritten Ausführungsbeispiels eines erfindungsgemäßen Brennstoffeinspritzventils.
- 1
- Brennstoffeinspritzventil
- 2
- Aktor
- 3
- Hülse
- 4
- Vorspannfeder
- 5
- Gehäuse
- 6
- Stützring
- 7
- Betätigungselement
- 8
- Wellrohrdichtung
- 9
- Geberkolben
- 10
- hydraulischer Koppler
- 11
- Kopplerspalt
- 12
- Nehmerkolben
- 13
- Führungshülse
- 14
- Druckfeder
- 15
- Ventilnadel
- 16
- Ventilgruppe
- 17
- Überwurfmutter
- 18
- Befüllventil
- 19
- Drosselbohrung
- 20
- Ventilkörper
- 21
- Ventilsitz
- 22
- Ventilschließkörper
- 23
- Ventilsitzfläche
- 24
- Rückstellfeder
- 25
- Ausnehmung
- 26
- Düsenkörper
- 27
- Dichtung
- 28
- Flansch
- 29
- Dichtung
- 30
- Einstellscheibe
- 31
- Tellerfeder
- 32
- Flansch
- 33
- Flächenanschliffe
Claims (14)
- Brennstoffeinspritzventil (1), insbesondere Brennstoffeinspritzventil (1) für Brennstoffeinspritzanlagen von Brennkraftmaschinen, mit einem piezoelektrischen oder magnetostriktiven Aktor (2), der über einen hydraulischen Koppler (10) einen an einer Ventilnadel (15) ausgebildeten Ventilschließkörper (22) betätigt, der mit einer Ventilsitzfläche (23) zu einem Dichtsitz zusammenwirkt, wobei der hydraulische Koppler (10) einen Geberkolben (9) und einen Nehmerkolben (12) aufweist, die in einer Führungshülse (13) angeordnet und durch einen Kopplerspalt (11) voneinander beabstandet sind,
dadurch gekennzeichnet, daß der Geberkolben (9) und/oder der Nehmerkolben (12) eine Drosselbohrung (19) aufweist, welche zusammen mit einem Ventilkörper (20) und einem Ventilsitz (21) ein Befüllventil (18) für den Kopplerspalt (11) bildet. - Brennstoffeinspritzventil nach Anspruch 1,
dadurch gekennzeichnet, daß der Ventilkörper (20) in einem Betätigungselement (7) angeordnet ist. - Brennstoffeinspritzventil nach Anspruch 2,
dadurch gekennzeichnet, daß das Betätigungselement (7) in kraftschlüssiger Verbindung mit dem Aktor (2) steht. - Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 3,
dadurch gekennzeichnet, daß der Ventilkörper (20) kardanisch in dem Betätigungselement (7) gelagert ist. - Brennstoffeinspritzventil nach Anspruch 4,
dadurch gekennzeichnet, daß der Ventilkörper (20) teilkugelförmig ausgebildet ist und in eine sphärische Ausnehmung (25) des Betätigungselements (7) eingreift. - Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 5,
dadurch gekennzeichnet, daß der Ventilsitz (21) an dem Ventilkörper (20) ausgebildet ist. - Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 5,
dadurch gekennzeichnet, daß der Ventilsitz (21) an dem Geberkolben (9) oder dem Nehmerkolben (12) des hydraulischen Kopplers (10) ausgebildet ist. - Brennstoffeinspritzventil nach Anspruch 7,
dadurch gekennzeichnet, daß der Ventilsitz (21) die Drosselbohrung (19) ringförmig umgibt. - Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 8,
dadurch gekennzeichnet, daß der Geberkolben (9) und der Nehmerkolben (12) des hydraulischen Kopplers (10) hohlzylindrisch ausgebildet sind. - Brennstoffeinspritzventil nach Anspruch 1,
dadurch gekennzeichnet, daß der Ventilkörper (20) einstückig mit der Ventilnadel (15) des Brennstoffeinspritzventils (1) ausgebildet ist. - Brennstoffeinspritzventil nach Anspruch 10,
dadurch gekennzeichnet, daß der Ventilkörper (20) Flächenanschliffe (33) aufweist. - Brennstoffeinspritzventil nach Anspruch 10 oder 11,
dadurch gekennzeichnet, daß der Ventilkörper (20) mit einem an dem Nehmerkolben (12) des hydraulischen Kopplers (10) ausgebildeten Ventilsitz (21) zusammenwirkt. - Brennstoffeinspritzventil nach Anspruch 12,
dadurch gekennzeichnet, daß die Drosselbohrung (19) zuströmseitig des Ventilsitzes (21) in dem Nehmerkolben (12) angeordnet ist. - Brennstoffeinspritzventil nach einem der Ansprüche 10 bis 13,
dadurch gekennzeichnet, daß zwischen dem Geberkolben (9) und dem Nehmerkolben (12) eine Tellerfeder (31) angeordnet ist.
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10246315 | 2002-10-04 | ||
DE10246315 | 2002-10-04 | ||
DE10342034A DE10342034A1 (de) | 2002-10-04 | 2003-09-11 | Brennstoffeinspritzventil |
DE10342034 | 2003-09-11 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1406006A1 true EP1406006A1 (de) | 2004-04-07 |
EP1406006B1 EP1406006B1 (de) | 2005-06-29 |
Family
ID=31995073
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20030022035 Expired - Lifetime EP1406006B1 (de) | 2002-10-04 | 2003-10-01 | Brennstoffeinspritzventil |
Country Status (1)
Country | Link |
---|---|
EP (1) | EP1406006B1 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1331191A1 (de) | 2002-01-25 | 2003-07-30 | IHC Gusto Engineering B.V. | Schwimmendehebevorrichtung |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3742241A1 (de) * | 1987-02-14 | 1988-08-25 | Daimler Benz Ag | Piezosteuerventil zur steuerung der kraftstoffeinspritzung ueber ein einspritzventil bei brennkraftmaschinen |
DE19500706A1 (de) * | 1995-01-12 | 1996-07-18 | Bosch Gmbh Robert | Zumeßventil zur Dosierung von Flüssigkeiten oder Gasen |
DE19743640A1 (de) * | 1997-10-02 | 1999-04-08 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
EP0909891A1 (de) * | 1997-10-18 | 1999-04-21 | Robert Bosch Gmbh | Ventil zum Steuern von Flüssigkeiten |
WO2003018993A1 (de) * | 2001-08-20 | 2003-03-06 | Robert Bosch Gmbh | Brennstoffeinspritzventil |
-
2003
- 2003-10-01 EP EP20030022035 patent/EP1406006B1/de not_active Expired - Lifetime
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3742241A1 (de) * | 1987-02-14 | 1988-08-25 | Daimler Benz Ag | Piezosteuerventil zur steuerung der kraftstoffeinspritzung ueber ein einspritzventil bei brennkraftmaschinen |
DE19500706A1 (de) * | 1995-01-12 | 1996-07-18 | Bosch Gmbh Robert | Zumeßventil zur Dosierung von Flüssigkeiten oder Gasen |
DE19743640A1 (de) * | 1997-10-02 | 1999-04-08 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
EP0909891A1 (de) * | 1997-10-18 | 1999-04-21 | Robert Bosch Gmbh | Ventil zum Steuern von Flüssigkeiten |
WO2003018993A1 (de) * | 2001-08-20 | 2003-03-06 | Robert Bosch Gmbh | Brennstoffeinspritzventil |
Also Published As
Publication number | Publication date |
---|---|
EP1406006B1 (de) | 2005-06-29 |
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