EP1276986A1 - Soupape de regulation de fluides - Google Patents

Soupape de regulation de fluides

Info

Publication number
EP1276986A1
EP1276986A1 EP01919220A EP01919220A EP1276986A1 EP 1276986 A1 EP1276986 A1 EP 1276986A1 EP 01919220 A EP01919220 A EP 01919220A EP 01919220 A EP01919220 A EP 01919220A EP 1276986 A1 EP1276986 A1 EP 1276986A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
hydraulic chamber
cavity
solid body
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Withdrawn
Application number
EP01919220A
Other languages
German (de)
English (en)
Inventor
Wolfgang Stoecklein
Dietmar Schmieder
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1276986A1 publication Critical patent/EP1276986A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—Three-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. for compensating clearance or thermal expansion

Definitions

  • valves are used to control liquids in which a valve closing member separates a low pressure area in the valve from a high pressure area, e.g. in fuel injectors, in particular common rail injectors, or pumps of motor vehicles are well known.
  • the valve according to the invention for controlling liquids with the features of claim 1 has the advantage that the system pressure in the hydraulic chamber is variable, its pressure level being dependent on the pressure prevailing in the high pressure range. This means that at high pressure levels in the high pressure range Increasing the system pressure in the hydraulic chamber possible, which supports the actuating piston to open the valve closing member against the high pressure. In this way, a reduced control voltage of the piezoelectric unit is sufficient compared to a valve with a constant system pressure, which is why the valve according to the invention can be equipped with a smaller and less expensive piezoelectric unit.
  • the solution according to the invention is characterized by its structurally simple nature, which allows the variable system pressure in the hydraulic chamber to be defined by easily adjustable geometric variables such as the longitudinal section of the solid body of the refilling device surrounded by gap flow between the high-pressure feed and a branch to the hydraulic chamber ,
  • valve for controlling liquids according to the invention Some embodiments of the valve for controlling liquids according to the invention are shown in the drawing and are explained in more detail in the following description. Show it
  • FIG. 1 shows a schematic, partial representation of a first exemplary embodiment of the invention in a fuel injection valve for internal combustion engines in longitudinal section
  • FIG. 2 shows a diagram with a greatly simplified course of a system pressure in the low-pressure area as a function of the pressure in the high-pressure area
  • FIG. 8 shows a schematic cross section through the embodiment according to FIG. 7,
  • FIG. 1 shows a use of the valve according to the invention in a fuel injection valve 1 for internal combustion engines of motor vehicles.
  • the fuel injection valve 1 is designed as a common rail injector for injecting diesel fuel, the fuel injection being based on the pressure level in a valve control chamber 2, which is associated with connected to a high pressure supply is controlled.
  • a valve member 3 is activated via a piezoelectric unit designed as a piezoelectric actuator 4, which is arranged on the side of the valve member 3 facing away from the valve control chamber and combustion chamber.
  • the piezoelectric actuator 4 is constructed in the usual manner from several layers and has an actuator head 5 on its side facing the valve member 3 and an actuator base 6 on its side facing away from the valve member 3, which is supported on a wall of a valve body 7.
  • valve member 3 which is axially displaceably arranged in a longitudinal bore 10 of the valve body 7, comprises a second piston 11, which actuates a valve closing member 12 and is therefore also referred to as an actuating piston.
  • valve seats 14, 15 formed on the valve body 7, the valve closing member 12 separating a low pressure region 16 with the system pressure p_sys from a high pressure region 17 with a high pressure or rail pressure p_R.
  • the valve seats 14, 15 are formed in a valve chamber 18 formed by the valve body 7, from which a leakage drain channel 19 leads away on the side of the valve seat 14 facing the piezoelectric actuator 4, and the high-pressure side via the second valve seat 15 and an outlet throttle 20 with the Valve control chamber 2 of the high pressure area 17 is connectable.
  • valve control chamber 2 which is only indicated in FIG. 1, a movable valve control piston is arranged, which is not shown in the drawing.
  • the injection behavior of the fuel valve 1 is increased by axial movements of the valve control piston in the valve control chamber 2, which is usually connected to an injection line, which is connected to a high-pressure storage chamber (common rail) common to several fuel injection valves and supplies an injection nozzle with fuel controlled in a manner known per se.
  • a high-pressure storage chamber common rail
  • FIG. 2 shows the dependence of the system pressure p_sys on the rail pressure p_R in an extremely schematic manner.
  • the system pressure p_sys can be assumed as a product of the high pressure p_R and the distance 1_B between the branch 28 to the hydraulic chamber 13 and the end 25B of the solid or pin 25, at which the leakage line 27 opens into the cavity 24, based on the total length of the pin 25.
  • the static system pressure p sys in the hydraulic chamber 13, which represents the coupler pressure can thus be determined in terms of formula:
  • the spring force F_F is on Further parameters for geometrically determining the branch 28 of the line 29 to the hydraulic chamber 13.
  • the maximum permissible system pressure p_sys_max which is shown in FIG. 2, can thus be represented in a simplified manner as follows:
  • the line 26 branching off from the high-pressure region 17 is connected in the present embodiment to a high-pressure inlet 31 from a high-pressure pump 32 to the valve control chamber 2 in the high-pressure region 17.
  • the line 29 leading from the branch 28 to the hydraulic chamber 13 is divided into a first line 29A and a second line 29B, the mouth region of which is formed in the gap 36 or gap 37 as a filling groove 38, 39 ,
  • the filling grooves 38, 39 can be supplied individually or together with the pressure supplied via the pin 25.
  • valve closing member 12 In the closed state of the fuel injection valve 1, that is to say when the piezoelectric actuator 4 is not energized, the valve closing member 12 lies against the one assigned to it upper valve seat 14 and is loaded by the spring 30 with the spring preload F_F. Above all, the rail pressure p_R is applied to the valve closing member 12, which presses the valve closing member against the first valve seat 14.
  • valve 1 is therefore the pin 25 of the feed device 23 is used, by means of which the pressure in the hydraulic chamber 13 is also increased accordingly at high rail pressure p_R. In this way, the piezo-side force on the valve closing member 12 is increased at the same voltage on the piezoelectric actuator 4, as shown in Figure 3.
  • FIG. 3 shows the course of the force F_A of the piezoelectric actuator 4 on the valve closing element 12 for a first voltage U1 and for a second lower voltage U2 with a dashed line, with variable system pressure p_sys according to the invention and with a solid line at conventional static system pressure p_sys , It shows that with the variable system pressure p_sys according to the invention, the piezoelectric actuator with one and the same voltage when moving the valve closing member 12 from a position S1 on the first valve seat 14 to a position S2 on the second valve seat 15 exerts a greater force, whereby the increase in force ⁇ F results from the system pressure p_sys in the hydraulic chamber 13 and the diameter AI of the second piston 11.
  • the increase in force .DELTA.F corresponds to a substantially higher voltage which would have to be applied to the piezoelectric actuator, since the gain in force can be, for example, 20% compared to a valve with a constant system pressure.
  • This gained power reserve can be used in the design of the valve, for example, to reduce the size of the piezoelectric actuator.
  • FIG. 5 a section of a further exemplary embodiment of the fuel injection valve is shown, which works in principle like the fuel injection valve described for FIGS. 1 and 4. For reasons of clarity, functionally identical components are identified by the reference numerals used in FIG. 1.
  • the solid body or pin 25 acting like a “pressure divider pin” is here by means of a mechanical adjustment device 32 is axially adjustable in the cavity 24.
  • the pin 25 can be displaced in the cavity 24 by means of the mechanical adjustment device 32, which is implemented in the embodiment according to Figure 5 with adjusting washers 33 at its end 25B facing the leakage line 27 the system pressure p_sys branched off from the pin 25 to the hydraulic chamber 13 is changed since the aspect ratios on the pin 25 shift. If the piezoelectric actuator 4 is energized in the embodiment according to FIG.
  • the change in length leads, as described above, to an increase in the pressure in the hydraulic chamber 13, the pressure build-up in the hydraulic chamber 13 in turn being dependent on various factors, such as a control gradient, the volume of the hydraulic chamber 13 and the scattering of the actuator ceramic depends.
  • pre-injections are often carried out with small injection quantities, which should be dosed as precisely as possible. Since the real pre-injection quantity often does not exactly match the pre-calculated pre-injection quantity due to different tolerance influences, a correction of the pre-injection quantity during the movement of the valve closing member from its first valve seat 14 against the second valve seat 15 can be made in this embodiment in such a way that by varying the system pressure p_sys the injection time or the start of injection is changed.
  • FIG. 6 shows an embodiment variant of the embodiment according to FIG. 5, the mechanical adjusting device 32 for the axial displacement of the pin 25 in the cavity 24 of the feed device 23 being designed with an adjusting screw 34 which can be set externally in a thread 35 by means of a suitable screwdriver is.
  • FIGS. 7 to 13 show further embodiment variants of the invention, with the pin 25 in each case here a positioning device 40 is arranged in the cavity 24.
  • the pin 25 is inserted into the bore of the cavity 24 with a certain amount of play, the exact position of the pin 25 remaining unknown.
  • the radial arrangement of the pin 25 in the cavity 24 has an influence, which should not be underestimated, on the gap flow rate and the exact function of the fuel injection valve.
  • the division ratio between the lengths on the pin 25 with regard to the arrangement of the branch 28 is e.g. with an imbalance of the pin 25 imprecise.
  • the flow rate also varies and can be 2.5 times higher when the pin 25 is completely eccentric than when the pin 25 is arranged exactly in the center.
  • the positioning device 40 according to the invention enables the pin 25 to be arranged in a defined manner. the division ratio is adhered to exactly and the function of the injector is therefore more precise.
  • the pin 25 is arranged eccentrically by at least one spring element in such a way that its longitudinal side is supported on the wall of the cavity 24.
  • the pin 25 can be provided with a groove 41 for this purpose.
  • this groove 41 there is a sheet metal strip 42 made of resilient material as a spring element, which is against the bore wall of the hollow room 24 supports.
  • the spring element 42 produces a force which presses the pin 25 against the wall.
  • the pin 25 is thus defined eccentrically. The flow is now defined solely by the play between pin 25 and the bore.
  • FIG. 9 essentially corresponds to the embodiment according to FIGS. 7 and 8, however the spring element here represents a helical spring 43 which lies in the groove 41 and presses against a ball 44.
  • the positioning device 40 can also be designed as a pressure shoulder 47, 48 or 49, 50 arranged at one end of the pin 25, as shown by the embodiment variants in FIGS. 12 and 13.
  • the pressure shoulders 47, 48 and 49, 50 are each offset by 180 ° to one another and represent bevels which, as in FIG. 12, can be formed on the pin 25 or on the cavity 24 as in FIG. 13.
  • the resulting hydraulic force is used by two bends at the end of the pin 25 which are rotated by 180 °.
  • the fuel flows from the bottom up when a pressure p_l below is greater than a pressure p_0 above. Without the bends, the pen surface would appear Set linear pressure curve from p_l to p_0.
  • FIG. 14 shows such an embodiment variant with two pins 25 and 25 N, wherein two cavities 24, 24 'with lines 26, 26' and leakage lines 27, 27 'which respectively supply high pressure are arranged in series such that a line 29 leading to the hydraulic chamber 13 'from the upstream cavity 24' at the same time forms the line 26 leading from the high pressure region 17, which opens into the downstream cavity 24.

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

L'invention concerne une soupape de régulation de fluides, qui comprend une unité piézo-électrique (4) actionnant une tige de soupape (3), à laquelle une tige de fermeture de soupape (12) est affectée, qui sépare une zone de haute pression (17) d'une zone de basse pression (16) à pression de système. La tige de soupape (3) comporte au moins un premier piston (9) et un second piston (11), entre lesquels se trouve une chambre hydraulique (13). Un système de remplissage (23), pouvant être relié à la zone de haute pression (17), permet de compenser les pertes de fuites. Ledit système comprend au moins une cavité de type canal (24), dans laquelle est disposé un corps solide (25). Un espace est maintenu tout autour dudit corps, de sorte qu'une conduite (26) déviée de la zone de haute pression (17) se jette dans ladite cavité (24) au niveau d'une extrémité (25A) dudit corps solide (25), de même qu'une conduite de fuite (27) au niveau de l'extrémité opposée (25B) du corps solide, et de sorte qu'une conduite (29) menant à la chambre hydraulique (13) est déviée le long de l'extension longitudinale du corps solide (25), la pression de système (p sys) dans la chambre hydraulique (13) étant réglable par détermination géométrique de la déviation (28).
EP01919220A 2000-04-20 2001-03-20 Soupape de regulation de fluides Withdrawn EP1276986A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10019766A DE10019766A1 (de) 2000-04-20 2000-04-20 Ventil zum Steuern von Flüssigkeiten
DE10019766 2000-04-20
PCT/DE2001/001056 WO2001081755A1 (fr) 2000-04-20 2001-03-20 Soupape de regulation de fluides

Publications (1)

Publication Number Publication Date
EP1276986A1 true EP1276986A1 (fr) 2003-01-22

Family

ID=7639567

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01919220A Withdrawn EP1276986A1 (fr) 2000-04-20 2001-03-20 Soupape de regulation de fluides

Country Status (6)

Country Link
US (1) US6655605B2 (fr)
EP (1) EP1276986A1 (fr)
JP (1) JP2003532003A (fr)
CZ (1) CZ20014519A3 (fr)
DE (1) DE10019766A1 (fr)
WO (1) WO2001081755A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10043625C2 (de) * 2000-09-05 2003-03-27 Bosch Gmbh Robert Hydraulisch übersetztes Ventil
DE10048933A1 (de) * 2000-10-04 2002-05-02 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
FR2819021B1 (fr) * 2000-12-28 2005-03-04 Denso Corp Soupape de commande hydraulique et injecteur de carburant utilisant une telle soupape
DE10157419A1 (de) * 2001-11-23 2003-06-12 Bosch Gmbh Robert Leckagereduzierte Druckversorgung für Kraftstoffinjektoren
DE10217594A1 (de) * 2002-04-19 2003-11-06 Bosch Gmbh Robert Brennstoffeinspritzventil
DE102004027824A1 (de) * 2004-06-08 2006-01-05 Robert Bosch Gmbh Kraftstoffinjektor mit variabler Aktorübersetzung
DE102009002840A1 (de) * 2009-05-06 2010-11-11 Robert Bosch Gmbh Vorrichtung zum Einspritzen von Kraftstoff
CN107152545A (zh) * 2017-07-10 2017-09-12 中国船舶重工集团公司第七0三研究所 一种油压曲线可分段调节的机械式调压阀
DE102018204586B4 (de) 2018-03-26 2024-05-23 Hawe Hydraulik Se Hydraulikwegeschieberventil mit Leckagebeeinflussung
AT521678B1 (de) 2018-10-08 2020-04-15 Avl List Gmbh Längenverstellbare Pleuelstange mit masseoptimiertem Steuerschieber

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4560871A (en) * 1983-12-22 1985-12-24 Marquest Medical Products, Inc. Actuator for control valves and related systems
EP0477400B1 (fr) * 1990-09-25 2000-04-26 Siemens Aktiengesellschaft Dispositif compensateur de tolérance dans la direction de mouvement du transformateur de déplacement d'un dispositif d'actionnement piézoélectrique
DE4332119B4 (de) * 1993-09-22 2006-04-20 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
US5779149A (en) * 1996-07-02 1998-07-14 Siemens Automotive Corporation Piezoelectric controlled common rail injector with hydraulic amplification of piezoelectric stroke
DE19709794A1 (de) * 1997-03-10 1998-09-17 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE19746143A1 (de) * 1997-10-18 1999-04-22 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
US5875764A (en) * 1998-05-13 1999-03-02 Siemens Aktiengesellschaft Apparatus and method for valve control
DE19844996A1 (de) * 1998-09-30 2000-04-13 Siemens Ag Vorrichtung und Verfahren zur Dosierung von Fluid
DE19860678A1 (de) 1998-12-29 2000-07-06 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE19946828C1 (de) * 1999-09-30 2001-07-12 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0181755A1 *

Also Published As

Publication number Publication date
CZ20014519A3 (cs) 2003-03-12
WO2001081755A1 (fr) 2001-11-01
DE10019766A1 (de) 2001-10-31
US20020139946A1 (en) 2002-10-03
US6655605B2 (en) 2003-12-02
JP2003532003A (ja) 2003-10-28

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