EP1799993A1 - Fuel injector - Google Patents
Fuel injectorInfo
- Publication number
- EP1799993A1 EP1799993A1 EP05789635A EP05789635A EP1799993A1 EP 1799993 A1 EP1799993 A1 EP 1799993A1 EP 05789635 A EP05789635 A EP 05789635A EP 05789635 A EP05789635 A EP 05789635A EP 1799993 A1 EP1799993 A1 EP 1799993A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fuel injector
- chamber
- injector according
- fuel
- pressure
- 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.)
- Withdrawn
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
- 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
- F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
- F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
-
- 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
- F02M57/00—Fuel-injectors combined or associated with other devices
- F02M57/02—Injectors structurally combined with fuel-injection pumps
- F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
- F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
-
- 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
- F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
- F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means
Definitions
- the fuel supply to the combustion chambers of self-igniting internal combustion engines is generally carried out by means of fuel injectors.
- the required injection pressure can be provided by high-pressure storage systems. A further pressure increase takes place, for example, by pressure booster in the fuel injector.
- the needle stroke of the injection valve member is damped.
- a device for injecting fuel into a Brenn ⁇ space of an internal combustion engine is known.
- the device for injecting fuel comprises a fuel injector, which can be acted upon by a high-pressure source with high-pressure fuel and actuated via a metering valve.
- the injection valve member which closes or releases at least one injection opening, is associated with a damping element which can be moved independently of it and which delimits a damping space. At least one overflow channel for connecting the damping chamber to a further hydraulic chamber is accommodated in the damping element.
- the opening speed of the nozzle needle is determined in DE 102 29 415 by the size of the outlet throttle from the damper chamber. An outlet throttle with a high volume throughput results in faster needle opening. In the fuel injection valve known from the prior art, the opening process of the injection valve member begins before the full injection pressure in the nozzle chamber has been reached.
- the fuel injector according to the invention with the characterizing features of the independent claim has the advantage of improved atomization and concomitantly improved combustion behavior of the fuel in the combustion chamber of an internal combustion engine.
- a later opening of the injection valve member and thus a higher fuel pressure at the beginning of the injection process is achieved by the erfindungs ⁇ trained according Kraftstoffinjektor.
- the higher, higher than the system pressure For example, a common rail lying fuel pressure at the beginning of the injection process leads to a finer and more uniform atomization of the fuel, resulting in a further reduced exhaust emissions.
- the coordination between nozzle needle damping and injection pressure at the beginning of the injection is improved, higher injection pressures are achieved, in particular even with short activation times or short injection pulses. This is guaranteed with an easily manufactured construction.
- a 2/2-way valve is accommodated in the supply line to the compression space.
- the 2/2 -way valve is preferably designed as a ball valve. As soon as the pressure in the compression chamber is increased by the movement of a piston into the compression space, the 2/2-way valve closes. This avoids that fuel from the compression chamber in the supply line and thus passes through the control valve in the return.
- the injector housing can be divided into individual segments, which are stacked one above the other for installation.
- recesses are formed in the end faces of the segments in which at least one channel opens, via which fuel is fed and at least two channels open, via which fuel is discharged.
- the channels are preferably formed as holes in the segments.
- inventively embodied fuel injector in high-pressure storage stars, it can also be used on other pressure-controlled injection systems, for example on pump-nozzle units, pump-line-nozzle units and distributor injection pumps.
- FIG. 1 shows a fuel injector embodied according to the invention
- FIG. 2 shows a detailed view of a further exemplary embodiment.
- FIG. 1 shows a fuel injector designed according to the invention in a first embodiment.
- the fuel injector designed according to the invention will be described with reference to a system with high-pressure accumulator.
- the supply of high-pressure fuel can also be effected, for example, by a pump-nozzle unit, a pump-line-nozzle unit or a distributor injection pump. All systems have in common that the inventively designed fuel injector is provided with a pressure booster.
- a fuel injector 1 is supplied with high-pressure fuel via a high-pressure accumulator 2 shown schematically here.
- the fuel first passes through a supply line 3 into a working space 4 of a pressure booster 5.
- a check valve 6 is accommodated in the supply line 3 to the working space 4.
- the check valve 6 is designed as a ball valve.
- a supply line 7 extends from the work space 4 to a control valve 8 is preferably designed as a 3/2 -way valve and is controlled by a piezoelectric actuator or an electromagnet.
- the control valve can be designed in a manner known per se as a 3/2-servo valve, which is controlled via a 2/2 solenoid valve.
- the fuel flows from the working chamber 4 via the supply line 7 to the control valve 8 and from there into a control line 9, while the return line 50 is disconnected.
- the pressure booster 5 and the control valve 8 are received in a pressure booster body 10.
- a nozzle body 11 connects.
- the pressure booster body 10 and the nozzle body 11 are preferably non-positively connected, for example with a union nut, with the fuel injector 1.
- the injection valve member 13 is preferably a one-piece configured nozzle needle. However, this can also be configured in several parts.
- the injection valve member 13 is enclosed by a nozzle chamber 14, wherein at least a part of the region 13a of the injection valve member is provided with a -Aximalem diameter into the nozzle chamber 14 protrudes.
- the nozzle chamber 14 is hydraulically connected via a connecting line 15 with a compression space 16.
- the compression space 16 is bounded on one side by an end face 17 of a booster piston 18 of the pressure booster 5.
- a step-shaped extension 19 is formed, which defines a control space 21 with an end face 20 pointing in the direction of the compression space 16.
- the step-shaped extension 19 divides the booster piston 18 into a first piston part 22 which faces the compression space 16 and a second piston part 23, which adjoins the stepped extension 19 on the side facing away from the compression space 16.
- the second piston part 23 is enclosed by a spring element 24, which is preferably designed as a spiral spring.
- the spring element 24 is supported with one side against a stop 25, which closes the booster piston 18 and with the other side against a received in the pressure booster annular stop 26.
- An ⁇ 26 is for example a locking ring for holes or a snap ring.
- the control chamber 21 of the pressure booster 5 is connected via a bypass 27 to the control line 9.
- the compression chamber 16 is supplied with fuel via a supply line 28, which also branches off from the control line 9. In the supply line 28, a 2/2-way valve is added, which closes the supply line 28, so ⁇ soon the pressure in the compression chamber 16 is higher than the pressure in the control line 9.
- the 2/2 -Wege- valve 29 is thus designed in the form of a check valve.
- a supply line 30 to a second control chamber 31 also extends from the compression chamber 16.
- the second control chamber 31 is delimited on one side by an end face 32 of a transmission element in the form of a hold-down piston 33.
- a connecting line 34 leads from the control line 9 into a damping chamber 35, in which the hold-down piston is arranged.
- a damping element 37 is further accommodated, which is formed, for example, in the shape of a piston.
- the transfer element 33 is surrounded by a second spring element 39.
- the second spring element 39 is preferably designed as a spiral spring. However, any further compression spring known to the person skilled in the art may also be used as the second spring element 39.
- the second spring element 39 is supported on one side against an end wall of the damping chamber 35 and on the second side against an adjusting ring 41.
- the adjusting ring 41 surrounds the transformer element 33 and rests on a stepped extension of the transformer element facing the damping element.
- the adjusting ring 41 serves to compensate for manufacturing tolerances, so that with each fuel injector 1, which is installed, the same spring force acts on the transmitter element 33 and thus on the damping element 37 on which the transmitter element rests.
- the damping element 37 limits a third control chamber 42.
- the third control chamber 42 is supplied with fuel via an inlet 43, which is connected to the control line 9.
- the damping element 37 is provided on the injection valve member side facing a flat ground end surface 44.
- a plane-ground end face 45 is likewise formed on the injection valve member 13.
- the damping element 37 is independent of the injection valve member 13 movable bar.
- the injection valve member 13 is placed in a seat 46, wherein the flat ground end face 45 of the injection valve member 13 of fuel, via a throttle 48 and the supply line 43 can flow into the control chamber 42, is acted upon.
- the injection valve member 13 and the damping element 37 separate, and the injection valve member 13 is initially moved independently of the damping element 37 in the direction of the at least one injection opening 12.
- the damping element 37 has a bore 58 which opens on the end face 44 and establishes a connection to the damping chamber 35.
- a connecting path 66 in the form of a groove is introduced, which produces a fuel-fillable connection between the bore 58 and an edge region of the damping chamber 35.
- a first throttle element 47 and in the inlet 43 to the third control space 42 the already mentioned (second) throttle element 48 is formed.
- the transmitter element 33 and the damping element 37 are designed as components separated from one another.
- the connection path 66 is designed as a hole perpendicular to the central bore 58.
- the control valve 8 In the idle state, the control valve 8 is in the position shown in Figure 1 and there is no fuel injection in a fuel injector 1 associated combustion chamber 49.
- the injection valve member 13 is in the seat 46 and thus closes the at least one injection port 12. Also lies the flat ground end face 44 of the damping element 37 on the flat-ground end face 45 of the injection valve member 13, so that the bore 58 is closed in the damping element 37.
- the connection from the supply line 3 to the control line 9 is released via the control valve 8.
- the fuel under storage pressure passes via the bypass 27 into the control chamber 21
- the third control chamber 42 is also supplied via the inlet 43 with cherbuchstruck under fuel pressure ,
- the working space 4 the control chamber 21, the compression chamber 16, the second control chamber 31, the damping chamber 35, the third control chamber 42 and the nozzle chamber 14 are acted upon by the pressure prevailing in the high-pressure accumulator 2 pressure level and the booster piston 18 in the pressure booster 5 is in the pressure-balanced Status.
- the pressure booster 5 is deactivated and there is no pressure boosting.
- the booster piston 18 is held by the spring element 24 in the starting position.
- the control valve 8 is switched to its other position.
- the control line 9 is connected to the low-pressure side return 50 and the supply line 7 is closed.
- the compression chamber 16 Since the compression chamber 16 is hydraulically connected via the connecting line 15 to the nozzle chamber 14 and via the supply line 30 to the second control chamber 31, the pressure also increases in the nozzle chamber 14 and in the second control chamber 31.
- the increasing pressure in the second control chamber 31 causes an additional closing force on the injection valve member 13 to be exerted due to the pressure force acting on the end face 32 of the hold-down piston 33.
- the damping chamber empties slowly, controlled by the throttle 47, an increasing opening force on the injection valve member in the nozzle chamber 14 is opposed by a likewise increasing closing force in the second control chamber 31.
- the force acting on the damping piston 37 in the direction of the injection valve member 13 and thus the Ein ⁇ injection valve member 13 in its seat 46 is composed of the pressure force of the fuel in the damping chamber 35, the spring force of the spring element 39 and the Druck ⁇ force of Fuel in the second control chamber 31.
- the cross-sectional area of the hold-down piston in the second control chamber 31 is smaller than the area of the maximum cross-section of the injection valve member in the nozzle chamber 14.
- the opening force on the injection valve member in the nozzle chamber attacks faster than the force acting in the closing direction in the second control Furthermore, the damping chamber slowly empties via the throttle 47, so that, starting at a specific pressure level in the compression chamber, which is above the system pressure level of the high-pressure accumulator 2, the composite of injection valve member 13 and damping element 37 moves away from the at least one injection opening 12 lifts, whereby the injection valve member 13 completely lifts from its seat 46 and so the at least one injection opening 12 releases. As soon as the injection valve member 13 lifts out of its seat 46, fuel is injected into the combustion chamber 49.
- the hold-down piston thus causes mit ⁇ means of its pressurization on the compression space a targeted delay of the lifting of the injection valve member to ensure a sufficiently high, above the system pressure of the high-pressure accumulator pressure build-up in the nozzle chamber, so that even with short drive times immediately applied a pressure-boosted fuel pressure level, as soon an injection port is opened.
- the control valve 8 is again switched to the position shown in FIG. As a result, the connection from the high pressure accumulator 2 is opened in the control line 9. Due to the thereby increasing pressure force on the end face 20 of the stepped extension 19 on the booster piston 18, the booster piston 18 moves supported by the spring force of the compression spring 24 from the compression chamber 16, whereby the volume of the compression chamber 16 is increased and so the pressure in the compression chamber 16 and in the nozzle chamber 14 decreases.
- the closing movement of the injection valve member 13 takes place via the refilling of the control chamber 42 and the throttle 48 adapted thereto.
- the rising fuel pressure on the end face 44 thus causes a fast closing movement of the injection valve member 13 into the seat 46.
- the injection valve member 13 releases from the damping element 37 and releases the sealing surface 44.
- the refilling space 35 is refilled via the bore 58 and the groove 66.
- the closing movement of the damping element 37 is determined primarily by the spring element 39. This leads to a slower closing movement of the damper piston 37 in comparison to the injection valve member 13.
- the injection valve member thus finally dissolves element 37 from the damping element and is placed in its seat 46. As a result, the at least one injection opening 12 is closed and the injection process into the combustion chamber 49 is ended. Via the inlet 43 passes, as already mentioned, fuel under storage pressure in the third control chamber 42. Thus, the damping element 37 is pressure balanced.
- the damping element 37 is provided by the spring force of the spring element 39 designed as a compression spring together with the hold-down piston with the flat-ground end face 44 on the flat-ground end face 45 of the injection valve member Ein ⁇ .
- the bore 58 in the damping element 37th closed, so that no fuel from the third control chamber 42 can flow into the damping chamber 35.
- the 2/2-way valve 29 opens, thus releasing the supply line 28 so that fuel under storage pressure can flow from the control line 9 into the compression space 16 , Coming from the compression space 16, fuel under storage pressure reaches the second control chamber 31 via the supply line 30.
- the hold-down piston 33 is also pressure-balanced. As soon as the control valve 8 is again actuated in order to start a new injection process and the pressure in the compression chamber 16 increases, the pressure in the second control chamber 31, which is likewise increasing as a result, and the pressure force on the end surface 32 of the hold-down piston increase again ensures that the injection valve member only lifts off from its seat 46 when a sufficiently large pressure difference has formed on the Nie ⁇ derhaltekolben 33 between the damping chamber 35 and the control chamber 31.
- the hold-down piston 33 always ensures a connection of each region of the damping region with the connecting line 34, so that the throttle 47 determines Geschwin ⁇ speed.
- FIG. 2 shows the nozzle body of a further fuel injector designed according to the invention.
- the nozzle body 11 is divided into individual segments. The advantage of the division into individual segments is that in each case only holes are formed in the individual segments or depressions are milled.
- the nozzle body 11 is divided into a valve segment 51, a throttle segment 52, a piston guide segment 53, a needle guide segment 54 and an injection segment 55. Above the nozzle body joins on the side of the valve segment 51 of the pressure booster body 10.
- Integrated in the pressure booster body is, in addition to the compression chamber 16, also the second control chamber 31 and the piston guide of the diameter-reduced region of the hold-down piston.
- the piston guide may be integrated in an intermediate plate between the valve segment and the pressure booster body, so that the intermediate plate the compression chamber up to the Wegs ⁇ line 30, which in the embodiment shown in Figure 2 as to demand control of the pressure build or ., the pressure reduction in the second control chamber serving throttle element 64 is configured, on the second control chamber 31 side facing.
- the 2/2-way valve 29 is partially disposed in the valve segment 51 and with its seat for the ball bearing 29 in the throttle segment 52.
- a branch region 77 located in the valve segment 51 is a branch region 77, which produces a connection of the control line 9 in the pressure booster body to a following in the throttle segment subsequent Zu ⁇ 43 and to another fuel path leading to the damping chamber 35 and represents a continuation of the control line 9.
- valve segment 51 is a piece of the connecting line 15 to the nozzle chamber 14. Furthermore, a first groove 56 is formed in the pressure booster body 10 via which a connecting line 34 arranged in the valve segment is connected to the damping chamber 35, this connecting line 34 in turn via a second groove 59 in the Kolben Resultss- segment 53, which is located on the side facing away from the valve segment 51 side of the throttle segment 52 is connected to the continuation of the control line 9.
- the throttle segment 52 are the majority of the damping chamber 35 and bores for the inlet 43 to the third control chamber 42, the continuation of the control line 9, the supply line 28 to the compression space 16, the connecting line 34 to the damping chamber 35 and the connecting line 15 to the nozzle chamber 14th educated.
- the throttle elements 47 and 48 are designed for damping pressure pulsations or for controlling the speed of filling or emptying of the damping chamber.
- a bore 57 is formed, in which the damping element 37 is guided.
- the piston guide segment 53 holes for the inlet 43 to the third control chamber 42 and a third groove 60 and the third control chamber 42 and a second groove 59 through which the continuation of the control line 9 with the supply line 28th and the connection line 34 is connected.
- a bore 61 is formed, in which the injection valve member 13 is guided. The bore 61 opens stu ⁇ fenförmig in the nozzle chamber 14.
- a bore for the connecting line 15 is received in the nozzle chamber 14, which opens in the ste ⁇ .
- the injection segment 55 of the nozzle chamber 14 is formed together with the Einspritzöffhungen 12.
- the holes in the individual segments 51, 52, 53, 54 and 55 which each form a line, are arranged flush over one another.
- pegs not shown in greater detail can be formed, which engage in corresponding recesses (not illustrated in greater detail) on the adjacent segment.
- the pins and the recess each have the same cross section.
- the connection of the individual segments 51, 52, 53, 54, 55 is preferably non-positive.
- a union nut which cooperates with a mounted on the pressure booster body 10 external thread.
- the second spring element 39 has the function of holding the injection valve and as a biasing element for the piston assembly of low retaining piston, damping element and injection valve member.
- the maximum allowable stroke of the injection valve member 13 can be limited via the stroke 76 of the hold-down piston or via the stroke 75 of the damping element.
- the size of the pressurized surfaces perpendicular to the ⁇ ffhungsplatz the injection valve member on hold-down piston 33, the damping element 37 and the injection valve member 13 itself determine together with the self-adjusting fuel pressure levels in Dämp Stahlngsraum 35, the second control chamber 31 and the nozzle chamber 14, the ⁇ ffhungs the injection valve member.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE200410048322 DE102004048322A1 (en) | 2004-10-05 | 2004-10-05 | fuel injector |
PCT/EP2005/054465 WO2006051009A1 (en) | 2004-10-05 | 2005-09-08 | Fuel injector |
Publications (1)
Publication Number | Publication Date |
---|---|
EP1799993A1 true EP1799993A1 (en) | 2007-06-27 |
Family
ID=35432391
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05789635A Withdrawn EP1799993A1 (en) | 2004-10-05 | 2005-09-08 | Fuel injector |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP1799993A1 (en) |
DE (1) | DE102004048322A1 (en) |
WO (1) | WO2006051009A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4415962B2 (en) * | 2006-03-17 | 2010-02-17 | 株式会社デンソー | Injector |
SE529810C2 (en) | 2006-04-10 | 2007-11-27 | Scania Cv Ab | Injection means for an internal combustion engine |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5241935A (en) * | 1988-02-03 | 1993-09-07 | Servojet Electronic Systems, Ltd. | Accumulator fuel injection system |
US6161770A (en) * | 1994-06-06 | 2000-12-19 | Sturman; Oded E. | Hydraulically driven springless fuel injector |
GB9714647D0 (en) * | 1997-07-12 | 1997-09-17 | Lucas Ind Plc | Injector |
DE19941688C2 (en) * | 1999-09-01 | 2001-08-09 | Siemens Ag | Injection device for an internal combustion engine with direct injection |
DE10119602A1 (en) * | 2001-04-21 | 2002-10-24 | Bosch Gmbh Robert | Fuel injection unit consists of fuel pump with piston and chamber, control valve, closure spring, stop, shaft part, connecting hole and smaller and larger diameter shaft parts |
DE10158951A1 (en) * | 2001-12-03 | 2003-06-12 | Daimler Chrysler Ag | Fuel Injection system for IC engine, operates with pressure conversion, has connection from control chamber and admission chamber to return line passing via common valve connection |
DE10229415A1 (en) | 2002-06-29 | 2004-01-29 | Robert Bosch Gmbh | Device for damping the needle stroke on pressure-controlled fuel injectors |
DE10315489B3 (en) * | 2003-04-04 | 2004-08-26 | Robert Bosch Gmbh | Fuel injector for use in internal combustion engine has integrated damping piston and has pressure increasing system connected to fuel pressure reservoir |
-
2004
- 2004-10-05 DE DE200410048322 patent/DE102004048322A1/en not_active Withdrawn
-
2005
- 2005-09-08 WO PCT/EP2005/054465 patent/WO2006051009A1/en active Application Filing
- 2005-09-08 EP EP05789635A patent/EP1799993A1/en not_active Withdrawn
Non-Patent Citations (1)
Title |
---|
See references of WO2006051009A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2006051009A1 (en) | 2006-05-18 |
DE102004048322A1 (en) | 2006-04-06 |
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