EP1611344A1 - Hubgesteuerter common-rail-injektor mit steller für schwingungsanregung - Google Patents
Hubgesteuerter common-rail-injektor mit steller für schwingungsanregungInfo
- Publication number
- EP1611344A1 EP1611344A1 EP03753328A EP03753328A EP1611344A1 EP 1611344 A1 EP1611344 A1 EP 1611344A1 EP 03753328 A EP03753328 A EP 03753328A EP 03753328 A EP03753328 A EP 03753328A EP 1611344 A1 EP1611344 A1 EP 1611344A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fuel
- pressure
- injector
- actuator
- 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.)
- 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
- 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
- F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
- F02M45/12—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship providing a continuous cyclic delivery with variable 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
- 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
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
-
- 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
- F02M63/06—Use of pressure wave generated by fuel inertia to open injection valves
Definitions
- the pressure which is present at the nozzle of the injector drops when the nozzle needle is opened for an injection process into the combustion chamber of the engine.
- This causes vibration excitation in a connecting line from the injector to the pressure accumulator, the frequency and amplitude of the oscillation being dependent on the flow through said nozzle, the line length and the line cross section, and the pressure in the pressure accumulator.
- the amplitude can be up to 25% of the pressure in the pressure accumulator (rail pressure). Because of the reduced pressure at the nozzle, the injection process begins with a lower pressure than the rail pressure.
- the stroke-controlled injector mentioned is one in which the nozzle needle (also referred to as valve piston) of the injection valve, when the control valve is closed, on the one hand from a pressure in a control chamber at that point facing away from the injection opening. End of the nozzle needle, and on the other hand is acted upon by the rail pressure on a piston surface provided on the nozzle needle in the vicinity of the injection openings of the injection valve.
- the arrangement is such that the nozzle needle is kept closed until, by opening a control valve, the pressure in the control chamber is reduced to such an extent that the force on the piston surface mentioned near the nozzle outweighs the force generated by the control chamber.
- the invention has for its object to provide a way to start the injection only when a vibration excited in the hydraulic system between the pressure accumulator and the injector generates a pressure at the injector that is higher than the above by opening the valve resulting collapsed (i.e. reduced compared to the rail pressure) pressure. It can be advantageous that the injection process only begins when a pressure close to the rail pressure or even higher than this is available for the injection.
- the features of claim 1 achieve the advantage that in preparation for the injection with the injection valve remaining closed, an oscillation is excited in the high-pressure line connecting the injector to the pressure accumulator, but the injection nozzle is still closed. At a suitable later point in time, at which a vibration is then preferably caused by the excited vibration If the pressure in the area of the injector is excessive, the injection valve is opened, as a result of which the injection process into the combustion chamber of the internal combustion engine can take place at high pressure, in any case at a higher pressure than in the prior art described.
- the vibration is excited by removing fuel from the high-pressure accumulator, preferably in the area of the high-pressure line, the injector of which is to be activated.
- the removal of fuel can take place directly from the high-pressure accumulator or from the high-pressure line at a suitable point which, depending on the technical circumstances, can be close to the high-pressure accumulator, close to the injector or at an intermediate location.
- the fuel withdrawal results in a flow of fuel from the. Pressure accumulator directed towards the injector, which may be useful for a particularly strong vibration excitation.
- the fuel is withdrawn through a valve that is separate from the injector.
- the injector can be a conventional injector which is actuated in a known manner to open the injection valve. In other configurations of the invention, the fuel is withdrawn within the injector. This offers the possibility of providing a single valve for the aforementioned fuel extraction for vibration excitation and for opening the stroke-controlled injector, as in two exemplary embodiments described below.
- the quantity per unit of time of the fuel removed from the pressure accumulator before the injection valve is opened and the duration during which this quantity of fuel flows are dimensioned such that the oscillation is excited with a desired amplitude.
- the above explanations also describe a method according to the invention with configurations in which an oscillation is first excited by taking fuel without an injection process and then an injection process can be initiated.
- the storage pressure can be, for example, up to 1600 bar or higher.
- Preferred embodiments shown in the drawings effect the described process by means of hydraulic elements arranged inside the injector, which cause the flow of fuel to start before the injection valve opens and cause the time delay until the injection valve opens.
- the time sequence described, in particular the delay time is determined by structural properties of the injector designed according to the invention in cooperation with the vibration properties of the line and the pressure of the pressure accumulator.
- FIG. 1 shows a simplified longitudinal section of a first exemplary embodiment of an injector with a stroke-controlled nozzle needle and a displaceably arranged actuator, the pressure in the control chamber of the nozzle needle also acting on one end of the actuator;
- FIG. 2 shows a second exemplary embodiment of an injector, likewise with an actuator and a stroke-controlled nozzle needle, the actuator being assigned an actuator control chamber which is structurally and functionally separate from the control chamber of the nozzle needle;
- FIG. 3 shows a schematic illustration of an arrangement with a separate valve for vibration excitation
- Fig. 1 shows an injector 1 with its parts necessary for understanding the invention.
- the drawing is also simplified to the extent that it is not apparent how the injector is composed of individual parts.
- An injector 1 has a housing 3 which has two bores 5 and 7 of different diameters arranged linearly one behind the other, the diameter of the bore 7 being somewhat larger than that of the bore 5.
- a valve piston which is essentially of constant diameter over its entire length 9 closes with a lower frustoconical region 11 the passage of fuel which is fed to a channel 12 of the injector from a pressure accumulator (CR) 13 via a high pressure line 14 connecting the injector to the pressure accumulator.
- the channel 12 is connected, inter alia, to a space 15 in the lower region of the injector 1, from where the fuel reaches outlet openings 17 when the injection valve (i.e. valve piston 9) is open.
- the valve piston 9 has in its upper end region a diagonally running bore 21 which opens into an annular groove 22 on both sides.
- a bore 23 leads from the line 21 in the longitudinal direction of the valve piston 9, with the inclusion of a constriction serving as an inlet throttle Z2, to an upper end face 25 of the valve piston.
- the two holes 5 and 7 are approximately the same length.
- a hydraulic element is slidably arranged, which partly acts as a switch, but at the same time is also part of a delay device, as will be explained.
- This hydraulic element is referred to here as an actuator 35 or actuating element and is formed by an essentially tubular part.
- the actuator 35 has a radial bore 37 which extends from the outside to the inside of the tubular part and opens into the annular groove 22 there. On the outside, the bore 37 is in fluid communication with an annular groove 39 arranged in the housing 3, regardless of the respective displacement position of the actuator 35 within its bore 7.
- the groove 39 is in turn connected to the channel 12.
- the actuator 35 there is another channel 43, one end of which is also connected to the groove 39.
- the other end of the channel 43 is connected to the upper end face 45 of the actuator 35 via an inlet throttle Z1.
- the parts arranged within the housing 3 are not particularly secured with respect to rotation and can therefore assume any rotational positions.
- an annular sealing bead 47 is provided on the end wall 46 on an end wall 46 for closing the channel 43 ,
- the actuator is acted upon in an upward direction by a compression spring 51 arranged below the actuator 35 and assumes its upper end position, unless a pressure in the control chamber 41 counteracts this. In the position shown, the actuator 35 assumes its lowest position, in which it strikes in a shoulder formed between the bores 5 and 7.
- the control chamber 41 is connected in a known manner via an outlet throttle A to an electromagnetically operated valve 52, which is not shown completely in the drawing, and when it is actuated, a spherical closure element 53 is raised, which closes the path for fluid from the control chamber 41 via the outlet throttle A. releases a leakage channel 55 which, together with a further leakage channel 56 opening into the space occupied by the spring 51, opens into a main leakage channel 57, from which the fuel is ultimately returned to the fuel tank of the internal combustion engine.
- the leakage channel 56 has no other function than to discharge fuel which has entered the space occupied by the spring 51 through unavoidable sealing gaps.
- a spring biasing the valve piston 9 into its closed position in the idle state is not shown to simplify the drawing.
- valve element 53 With the internal combustion engine running, fuel is supplied to the channel 12 at high pressure. First, the valve element 53 is closed. The fuel passes through the grooves 39 and 22 and the channels 23 and 43 to the upper end of the valve piston 9 and the actuator 35 and moves the parts mentioned, insofar as they are not already in their lower end position, down to their respective stops. To simplify the description, it is assumed that this position of the parts relative to one another is present when the control chamber 41 is completely filled before the first injection process considered here. To initiate an injection process, the closure element 53 of the control valve 52 is opened. With conventional injectors, the injection valve would now be opened almost immediately and an injection would be initiated.
- the closing process of the injection valve is caused by the valve part 53 blocking the path for fuel from the control chamber 41 via the throttle A. Then, fuel passes under pressure into the control chamber via channels 37, 23 and 43 and increases the pressure there until the injection valve closes.
- the passage of time is predetermined by design features, in particular dimensions of the individual parts.
- the annular sealing bead 47 is only one possibility of several to reduce the inflow of fuel from the channel 12 into the control chamber 41 when the actuator 35 has assumed a predetermined upper position.
- the solution described here is probably the simplest.
- the channel 43 formed by bores there could also be a suitably dimensioned longitudinal groove in the housing 3, which is connected to the groove 39 and whose upper end is closed by the outer surfaces of the actuator when an upper switch-off position is reached, which is not excluded that the actuator can move upwards beyond this position.
- the actuator 35 need not be in contact or in the immediate vicinity of the injection valve piston 9.
- the actuator 35 could instead be arranged as an essentially cylindrical part in another bore within the housing 3, but the space above this actuator must be in communication with the control chamber of the injection valve 9.
- the exemplary embodiment shown is preferred in terms of space requirements, simple, precise manufacture and the ability to absorb high pressures. The statements just made also largely apply to the further exemplary embodiment described with reference to FIG. 2.
- the further exemplary embodiment of a device according to the invention shown in FIG. 2 differs with regard to the mechanical parts insofar as they are shown in FIG. 1, mainly in the following way:
- FIG. 2 Another device is provided which generates an upward force on the actuator 85 of FIG. 2.
- the actuator 85 is extended downward in a radially inner region relative to the radially outer region to such an extent that the annular space 88 visible in FIG. 2, into which the channel 81 opens, always remains closed in a radially inward direction.
- line 113 is always connected to channel 12, e.g. in that the groove 39 is long enough.
- the actuator 85 is braked either by the stop 95 or by switching the valve 110.
- groove 39 is shorter than shown in Fig. 2; the leakage is then reduced, that is to say less fuel is drawn from the high-pressure accumulator to excite vibrations.
- the movement of the actuator 85 has no influence whatsoever on the flow of fuel into and out of the control chamber 97 of the valve piston 9.
- the function in the arrangement according to FIG. 2 is controlled by three different positions of a 3/3-way valve 110.
- the valve 110 is electromagnetically driven in an embodiment that is not shown in detail.
- the control rooms 97 and 98 are spatially separated from one another. In the position shown, the control chambers 97 and 98 are connected to one another and at the same pressure by the valve 110, the pressure of the control chamber 97 being so high that the injection valve is closed. Both control rooms 97 and 98 are practically closed. In this position, the ends of the throttle AD facing away from the control spaces are for the control space of the injection valve and the throttle AS are for the control space. connected to each other.
- the control device moves the 3/3-way valve 110 into its switching position lying on the far right in FIG. 2. In this position, the path for the fuel within the control chamber 97 of the injection valve needle is now also released into the leakage channel via the throttle AD, and the injection valve opens as a result of this pressure drop in the control chamber 97.
- the constructional predetermined time sequences in connection with the vibration-determining dimensions of the line system between the pressure accumulator and the injector are dimensioned such that the removal of fuel from the pressure accumulator caused by the movement of the actuator excites a sufficiently strong oscillation that starting at the injector, runs back to the pressure accumulator as a dilution wave and is reflected in the accumulator (which may be regarded as a closed volume), is reflected as a pressure wave and returns to the injector as a pressure wave.
- the pressure wave can also be interpreted in such a way that the dilution wave arriving at the pressure accumulator results in a particularly violent outflow of fuel from the pressure accumulator, this violent inflow of fuel arriving as a pressure wave at the injector.
- the arrangement is such that, depending on the desired injection process, the injection valve is fully open for a longer or shorter time before the pressure wave arrives from the pressure accumulator, so that in this case the injection begins at a lower pressure and is then amplified when the pressure wave arrives ; or that in another case the injection valve is only opened shortly before the pressure wave arrives, so that practically the injection begins immediately with the high pressure.
- the upper end of the channel 43 is closed by the sealing bead 47 in the upper end position of the actuator 35, but is open in other positions of the actuator, a 2/2-way valve is formed. This has the effect that, depending on the position of the actuator 35, either the two channels 43 and 23 or only the channel 23 are connected to the channel in which the throttle A is arranged. As described, this last-mentioned channel is opened and closed by the movable valve part 53.
- the desired behavior of the function of the injection valve in relation to the pressure profile within the connecting line to the pressure accumulator is achieved by appropriately actuating the 3/3-way valve 110.
- An upward slower movement of the actuator can be achieved by switching back and forth between the shown position of the valve 110 and the adjacent position. If the actuator 85 reaches the top with the injector open so that the flow of fuel through the actuator is interrupted, this creates a pressure increase (dynamic pressure), which can cause a further increase in the pressure at the injection openings and therefore an increase in the injection rate.
- the 3/3-way valve also takes over the function of the control valve 52 of FIG. 1, in which the movable valve part 53 is located.
- FIG. 2 thus shows an arrangement which is characterized in that an actuator (85) or hydraulically adjustable switching element is arranged in the injector and can be moved between two end positions, that an actuator control chamber (98) is assigned to the actuator (85) which is separated from a control chamber (97) assigned to the valve piston (9), and that the two control rooms can either be shut off by a valve arrangement (110) or can be connected to a low pressure area, or the actuator control room is connected to the low pressure area and the valve piston control chamber is shut off, channels being provided in the region of the actuator and the valve piston in order to conduct fuel under pressure into the assigned control chamber.
- an actuator (85) or hydraulically adjustable switching element is arranged in the injector and can be moved between two end positions, that an actuator control chamber (98) is assigned to the actuator (85) which is separated from a control chamber (97) assigned to the valve piston (9), and that the two control rooms can either be shut off by a valve arrangement (110) or can be connected to a low pressure area, or the actuator control room is connected to the low pressure area and the valve
- FIG. 3 shows in simplified form an arrangement with the pressure accumulator 13 intended for fuel, which is filled with fuel under pressure (for example 1600 bar) from a fuel tank via pumps (not shown) and which is connected to a conventional stroke-controlled injector 201 via the high-pressure line 14.
- fuel under pressure for example 1600 bar
- pumps not shown
- high-pressure line 14 In an internal combustion engine for passenger cars, for example, there are several engine cylinders and therefore a corresponding number of injectors and high-pressure lines.
- Each injector has a leakage line leading to a collection leakage line 205 and from there to the fuel tank.
- an electrically controllable valve 210 is connected between the high-pressure line and the leakage collecting line in the area of the high-pressure line 14, in the example near the end that is connected to the injector 201.
- the valve 210 allows fuel to be discharged from the high-pressure accumulator i ⁇ to the low-pressure region, as a result of which vibration in the high-pressure line is excited, as explained above, before the injector starts an injection.
- the injector is electrically controlled to initiate an injection process. It is expediently activated and that of valve 210 by means of an activation device 220 in the desired chronological order.
- the following methods and variants are carried out by means of the arrangement according to FIG. 3: Fuel is drawn from the pressure accumulator in order to excite an oscillation of the pressure at the stroke-controlled injector without starting an injection.
- the fuel is taken from the pressure accumulator.
- the fuel is taken from the high-pressure line.
- the fuel is taken from the high-pressure line at a point such that a flow of fuel is caused in the direction of the injector.
- the fuel is drawn from the high pressure line near the injector.
- the fuel is removed from the pressure accumulator and the high-pressure line in the interior of the stroke-controlled injector or more generally from the stroke-controlled injection device without starting an injection process.
- the high-pressure line is always filled with fuel during the operation of the injection devices or the associated internal combustion engines.
- 4a to 4d are representations over time (horizontal axis).
- 4a is 400 the path of the actuator 35 starting from the rest position of FIG. 1.
- the increase begins with the opening of the valve 52.
- FIG. 4b is the corresponding pressure curve 403 in the control chamber 41. Even if the pressure drops to p1 the valve piston 9 remains closed (curve 402 in FIG. 4a).
- the oscillation in the high pressure line is now excited (pressure reduced compared to the rail pressure, curve 404 in Fig. 4c and reaches the rail pressure again at time T / 2 (half oscillation period).
- the channel 43 is closed, the pressure of the control chamber continues to decrease off to p2 and the valve piston is opened (curve 402). It is open during the maximum pressure at the injector.
- the injection rate is shown by curve 405 in FIG. 4d.
- FIG. 4a also shows by curve 401 that the opening of the valve piston can be adjusted by the arrangement according to FIG. 2; in the example, an actuation earlier than FIG. 1 is shown; later actuation is also possible.
- 5a and 5b are representations over time (horizontal axis).
- Curve 500 shows the path of actuator 85 of FIG. 2, and curve 501 shows the opening of the valve piston at a relatively low pressure, predetermined by a sequence of actuation of valve 110 selected in this example. Curve points to the maximum of the curve a pressure increase when the actuator 85 is closed.
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 |
---|---|---|---|
DE2003113419 DE10313419A1 (de) | 2003-03-25 | 2003-03-25 | Hubgesteuerter Common-Rail-Injektor mit Steller für Schwingungsanregung |
PCT/DE2003/003235 WO2004085834A1 (de) | 2003-03-25 | 2003-09-29 | Hubgesteuerter common-rail-injektor mit steller für schwingungsanregung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1611344A1 true EP1611344A1 (de) | 2006-01-04 |
EP1611344B1 EP1611344B1 (de) | 2006-12-13 |
Family
ID=33038759
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP03753328A Expired - Lifetime EP1611344B1 (de) | 2003-03-25 | 2003-09-29 | Hubgesteuerter common-rail-injektor mit steller für schwingungsanregung |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP1611344B1 (de) |
DE (2) | DE10313419A1 (de) |
WO (1) | WO2004085834A1 (de) |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2009322A1 (de) * | 1969-05-07 | 1971-01-28 | Technische Hochschule Otto von Guericke Magdeburg, χ 3010 Magdeburg | Hydraulische Druckstoß-Einspritzvorrichtung, insbesondere für Brennkraftmaschinen |
DE4106015A1 (de) * | 1991-02-26 | 1992-08-27 | Ficht Gmbh | Druckstoss-kraftstoffeinspritzung fuer verbrennungsmotoren |
US5509391A (en) * | 1994-10-03 | 1996-04-23 | Caterpillar Inc. | Helmoltz isolation spool valve assembly adapted for a hydraulically-actuated fuel injection system |
WO1999047802A1 (de) * | 1998-03-16 | 1999-09-23 | Siemens Aktiengesellschaft | Verfahren zum bestimmen der einspritzzeit bei einer direkteinspritzenden brennkraftmaschine |
DE10056166A1 (de) * | 2000-11-13 | 2002-05-23 | Bosch Gmbh Robert | Hochdrucksammelraum mit integriertem Druckübersetzungselement |
DE10105031A1 (de) * | 2001-02-05 | 2002-08-14 | Bosch Gmbh Robert | Vorrichtung zur Dämpfung von Druckpulsationen in Hochdruckeinspritzsystemen |
DE10145862A1 (de) * | 2001-09-18 | 2003-04-03 | Bosch Gmbh Robert | Verfahren zum Einspritzen von Kraftstoff sowie Ventil zum Steuern von Flüssigkeiten |
-
2003
- 2003-03-25 DE DE2003113419 patent/DE10313419A1/de not_active Ceased
- 2003-09-29 DE DE50305998T patent/DE50305998D1/de not_active Expired - Fee Related
- 2003-09-29 WO PCT/DE2003/003235 patent/WO2004085834A1/de not_active Application Discontinuation
- 2003-09-29 EP EP03753328A patent/EP1611344B1/de not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO2004085834A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2004085834A1 (de) | 2004-10-07 |
EP1611344B1 (de) | 2006-12-13 |
DE50305998D1 (de) | 2007-01-25 |
DE10313419A1 (de) | 2004-11-04 |
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