EP1137876A1 - Soupape permettant de commander le passage de liquides - Google Patents

Soupape permettant de commander le passage de liquides

Info

Publication number
EP1137876A1
EP1137876A1 EP00978944A EP00978944A EP1137876A1 EP 1137876 A1 EP1137876 A1 EP 1137876A1 EP 00978944 A EP00978944 A EP 00978944A EP 00978944 A EP00978944 A EP 00978944A EP 1137876 A1 EP1137876 A1 EP 1137876A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
solid body
pressure chamber
chamber
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Withdrawn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
EP00978944A
Other languages
German (de)
English (en)
Inventor
Rudolf Heinz
Wolfgang Stoecklein
Klaus-Peter Schmoll
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 EP1137876A1 publication Critical patent/EP1137876A1/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Withdrawn legal-status Critical Current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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/004—Actuating devices; Operating means; Releasing devices actuated by piezoelectric means
    • F16K31/007—Piezoelectric stacks

Definitions

  • the invention is based on a valve for controlling liquids according to the type defined in claim 1.
  • 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. at
  • EP 0 477 400 AI also describes such a valve, which can be actuated via a piezoelectric actuator and has an arrangement for a displacement transformer of the piezoelectric actuator acting in the stroke direction, in which the deflection of the actuator is transmitted via a hydraulic chamber, which acts as a hydraulic ratio or coupling and tolerance compensation element works.
  • Hydraulic chamber closes between two delimiting them Pistons, of which one piston is designed with a smaller diameter and is connected to a valve element to be actuated, and the other piston is designed with a larger diameter and is connected to the piezoelectric actuator, a common compensation volume.
  • the hydraulic chamber is clamped between the two pistons in such a way that the actuating piston makes a stroke that is enlarged by the transmission ratio of the piston diameter when the larger piston is moved by a certain distance by the piezoelectric actuator.
  • the valve member, the pistons and the piezoelectric actuator lie on a common axis. Tolerances based on temperature gradients or different coefficients of thermal expansion of the materials used and any setting effects can be compensated for via the compensating volume of the hydraulic chamber, without a change in the position of the valve element to be controlled thereby occurring.
  • the hydraulic system in the low-pressure range in particular the hydraulic coupler, requires a system pressure which drops due to leakage if there is no sufficient refill with hydraulic fluid.
  • Common-rail injectors of the leakage gap are chosen to be relatively large in order to be able to maintain the system pressure in the low-pressure range even at extremely low temperatures, at which the viscosity of diesel fuel increases until it becomes greasy.
  • a large amount of liquid reaches the low-pressure region via the gap around the lick stick, the excess amount of liquid having to be drained off via a pressure-maintaining valve. In this way there is an undesirably high leakage loss of the valve, due to which the efficiency of the overall system decreases sharply.
  • the invention has for its object to provide a valve for controlling liquids, in which one
  • Leakage amount from a high pressure area into a low pressure area of the valve is at least approximately constant in the event of temperature changes.
  • the valve according to the invention for controlling liquids with the features of claim 1 has the advantage that the gap between the solid body and the valve body can be designed to be relatively large, so that a sufficient volume throughput is ensured even at very low temperatures of the flowing liquid.
  • the solid With increasing temperature and decreasing viscosity of the liquid flowing through the gap, the solid expands more than the material of the valve body due to its greater coefficient of thermal expansion, so that the gap is reduced with increasing temperature and thus advantageously the same volume throughput at medium and high temperatures how to set in the low temperature range.
  • valve according to the invention Since with the valve according to the invention an increase in the leakage rate in the low-pressure range as a result of rising temperatures is avoided, there is also no need to drain the large quantities of excess liquid through a pressure relief valve, which is why the efficiency of the overall system is not impaired.
  • Figure 1 is a schematic, sectional view of a first embodiment of the invention in a fuel injection valve for internal combustion engines in longitudinal section, and
  • Figure 2 is a schematic, partial representation of a further embodiment of the invention in a fuel injection valve for internal combustion engines.
  • 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 here as a common rail injector for injecting diesel fuel, the fuel injection being controlled via the pressure level m in a valve control chamber 12 which is connected to a high pressure supply.
  • the start of injection, the injection duration and the injection quantity are set via force relationships in the fuel injection valve 1, a valve member 2 being controlled via an actuator designed as a piezoelectric unit with a piezoelectric actuator 3, which is arranged on the side of the valve member 2 facing away from the valve control chamber and combustion chamber.
  • the piezoelectric actuator 3 is usually made up of several layers and has on its side facing the valve member 2 an actuator head 4 and on its side facing away from the valve member an actuator foot 5 which is supported on a wall of a valve body 9.
  • a first piston 7 of the valve member 2 is in contact with the actuator head 4 via a support 6, and its diameter is stepped.
  • the valve member 2 is arranged in a bore 8 of the valve body 9 designed as a longitudinal bore and is axially displaceable and comprises, in addition to the first piston 7, a second piston 10 which actuates a valve closing member 13.
  • the pistons 7 and 10 of the valve member 2 are coupled to one another by means of a hydraulic transmission, which is designed as a hydraulic chamber 11.
  • the hydraulic chamber 11 encloses between the two pistons 7 and 10 delimiting it, of which the second piston 10 is designed with a smaller diameter than the first piston 7, a common compensation volume via which the deflection of the piezoelectric actuator 3 is transmitted.
  • the hydraulic chamber 11 is between the
  • valve member 10 of the valve member 2 makes a stroke enlarged by the transmission ratio of the piston diameter when the larger first piston 7 is moved by the piezoelectric actuator 3 by a certain distance.
  • the pistons 7 and 10 and the piezoelectric actuator 3 lie one behind the other on a common axis.
  • the spherical valve closing member 13 interacts with valve seats 14, 15 formed on the valve body 9, the valve closing member 13 separating a low pressure region 16 with a system pressure from a high pressure region 17 with a high pressure or rail pressure.
  • a first valve pressure chamber 20 adjoins the piezo-side end of the bore 8, which is delimited on the one hand by the valve body 9 and on the other hand by a sealing element 22 connected to the first piston 7 of the valve member 2 and the valve body 9.
  • the sealing element 22 is designed as a bellows-like membrane and prevents the piezoelectric actuator 3 from coming into contact with the fuel contained in the first valve pressure chamber 20.
  • the first valve pressure chamber 20 is connected to a second valve pressure chamber 21 leading to the valve control chamber 12 of the high pressure region 17, in which the valve seats 14, 15 are formed.
  • a leakage discharge channel 29 leads away, in the leakage discharge channel 29 a throttle 23 is arranged as a damping element for the adjustment movement of the valve closing member 13.
  • a spring 27 assigned to the lower valve seat 15 is provided in the second valve pressure chamber 21 and holds the valve closing member 13 on the upper valve seat 14 when the valve control chamber 12 is relieved.
  • valve control chamber 12 which is only indicated in FIG. 1, a movable valve control piston is arranged, which is not shown in the drawing.
  • An injection nozzle of the fuel injection valve 1 is controlled in a manner known per se by axial movements of the valve control piston in the valve control chamber 12.
  • valve control chamber 12 usually also opens ne
  • Injection line that supplies the injector with diesel fuel.
  • the injection line is connected to a common high-pressure storage space (common rail) for multiple fuels.
  • the channel-like cavity 18 of the filling device 19 has a spring-loaded pressure relief valve 25 that regulates the system pressure of the first valve pressure chamber 20 and is equipped with a damping process designed as a throttle 24.
  • a solid body 26 Arranged in the channel-like cavity 18 on the high-pressure side of the pressure relief valve 25 is a solid body 26 designed as a cylindrical pin, which delimits a gap 28 with the valve body 9 surrounding it.
  • the cylindrical pin 26 is made of a material whose coefficient of thermal expansion is significantly higher than that of the surrounding valve body 9, which is usually made of steel. Materials which consist essentially of aluminum or copper are particularly suitable for the cylindrical pin 26. With such a choice of material, an increase in the viscosity of the volumetric flow flowing around the cylindrical pin 26 of the filling device 19 is greatly limited with increasing temperature, an almost constant volumetric flow being able to be achieved with changes in temperature with an optimal choice of material.
  • the fuel injection valve 1 according to FIG. 1 operates in the manner described below.
  • valve closing member 13 When the fuel injector 1 is closed, i.e. when the piezoelectric actuator 3 is not energized, the valve closing member 13 is held in contact with the upper valve seat 14 assigned to it, so that no fuel can get from the high pressure region 17 into the second valve pressure chamber 21 and escape through the leakage drain channel 29.
  • the first piston 7 serving as an actuating piston penetrates with temperature increases. Hung in the compensation volume of the hydraulic chamber 11 and withdraws from it when the temperature drops, without this having an effect on the closed and open position of the valve member 2 and the fuel valve 1 as a whole.
  • the piezoelectric actuator 3 For an injection through the fuel injection valve 1, the piezoelectric actuator 3 is energized, causing it to suddenly expand axially. With such a rapid actuation of the piezoelectric actuator 3, it is supported on the valve body 9 and moves the second piston 10 with the valve closing member 13 from its upper valve seat 14 into a central position between the two valve seats 14 and 15 the volume of the first valve pressure chamber 20 is reduced by means of the membrane 22, as a result of which the system pressure in the first valve pressure chamber 20 increases accordingly. This pressure increase cannot be reduced immediately by the pressure relief valve 25, since the throttle 24 briefly builds up the system pressure. As a result, a hydraulic counterforce acts on the diaphragm 22 against the actuating movement of the valve member 2. The actuating movement is thus damped and the valve closing member 13 is stabilized in its central position.
  • the closing member 13 can be moved into its closed position on the lower valve seat 15, as a result of which no more fuel can penetrate from the valve control chamber 12 into the second valve pressure chamber 21.
  • the fuel injection is then ended. If the energization of the piezoelectric actuator 3 is subsequently interrupted, the valve member moves back into its central position and fuel is injected. Fuel can penetrate into the second valve pressure chamber 21 through the lower valve seat 15, the throttle 23 in the leakage outlet channel 29 in turn damping the actuating movement of the valve member 2.
  • a rail pressure of 200 to 1800 bar can prevail in the high pressure range, while the system pressure in the low pressure range can be, for example, 30 bar and the fuel returned to a tank via the leakage discharge channel 22 can have a low pressure of, for example, 1 bar.
  • the gap 28 can be dimensioned so large that even at extremely low temperatures with a diesel fuel that tends to stain, the provision of the system pressure in the low-pressure region 16 is ensured. With increasing temperatures, the gap 28 by the
  • FIG. 2 a second embodiment of the fuel injection valve is shown, which works in principle like the fuel injection valve described for FIG. 1.
  • functionally identical components are identified by the reference numerals used in FIG. 1.
  • the fuel injection valve 1 shown here differs in that the channel-like cavity 18 instead of the first valve pressure chamber 20, which here has a leakage line 30 leading to a tank, is now on the side of the low pressure region 16 facing Filling device 19 opens a gap 31 surrounding the first piston 7, an annular groove 32 being provided in the mouth region.
  • This embodiment has the advantage that only an extremely small volume is displaced from the system pressure range, so that the continuous leakage of the system in the valve according to the invention is reduced to a minimum, but with a continuous flow through the hydraulic chamber 11 and thus em purging of possibly m this air entering is guaranteed.
  • the hydraulic chamber 11 can advantageously be refilled with high pressure, so that refilling as quickly as possible after a possible leakage through the gap 31 or a gap 32 surrounding the second piston 10 is achieved.
  • the low-pressure side is designed
  • channel-like cavity 18 leads from the solid body or cylindrical pin 28 of the filling device 19 to the gap 32 surrounding the second piston 10.
  • the embodiment of the solid body 26 with a large thermal expansion capacity and the dimensioning of the gap 28 also ensures here that the provision of the system pressure is still ensured even at a minimal high pressure and very low fuel temperatures. If the fuel temperature rises, for example due to an increased return flow at high load and a correspondingly high delivery of thermal energy from the high pressure pump to the power material, the gap 28 narrows due to the expansion of the cylindrical pin 26 in such a way that the viscosity-related increase in the volume flow flowing around the cylindrical pin 26 is at least partially limited.
  • the invention can of course not only be used in the common rail injectors described here as a preferred area of application, but generally in fuel injectors or in other environments, such as e.g. be realized with pumps.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Temperature-Responsive Valves (AREA)

Abstract

L'invention concerne une soupape permettant de commander le passage de liquides. Un organe de fermeture de soupape (13) sépare une zone basse pression (16) située dans la soupape (1) et une zone haute pression (17). Cette soupape comprend une unité de remplissage (19) servant à compenser des pertes de la zone basse pression (16) par prélèvement de liquide hydraulique dans la zone haute pression (17). Cette unité de remplissage (19) est formée dans un corps de soupape (9) comportant une cavité (18) en forme de canal, dans laquelle un solide (26) est placé de sorte qu'un espace (28) soit créé entre ledit solide (26) et le corps de soupape (9). Le matériau du solide (26) présente un coefficient de dilatation thermique supérieur à celui du corps de soupape (9) de sorte que l'augmentation, liée à la viscosité, du courant volumétrique circulant autour du solide (26) soit au moins partiellement limitée lorsque la température augmente.
EP00978944A 1999-09-30 2000-09-19 Soupape permettant de commander le passage de liquides Withdrawn EP1137876A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19946830 1999-09-30
DE19946830A DE19946830A1 (de) 1999-09-30 1999-09-30 Ventil zum Steuern von Flüssigkeiten
PCT/DE2000/003241 WO2001023747A1 (fr) 1999-09-30 2000-09-19 Soupape permettant de commander le passage de liquides

Publications (1)

Publication Number Publication Date
EP1137876A1 true EP1137876A1 (fr) 2001-10-04

Family

ID=7923812

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00978944A Withdrawn EP1137876A1 (fr) 1999-09-30 2000-09-19 Soupape permettant de commander le passage de liquides

Country Status (7)

Country Link
US (1) US6547213B1 (fr)
EP (1) EP1137876A1 (fr)
JP (1) JP2003510510A (fr)
CZ (1) CZ20011876A3 (fr)
DE (1) DE19946830A1 (fr)
HU (1) HUP0104426A3 (fr)
WO (1) WO2001023747A1 (fr)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2349545A (en) * 1999-04-26 2000-11-01 Nokia Mobile Phones Ltd Terminal for providing an application using a browser
DE19949528A1 (de) * 1999-10-14 2001-04-19 Bosch Gmbh Robert Doppelschaltendes Steuerventil für einen Injektor eines Kraftstoffeinspritzsystems für Brennkraftmaschinen mit hydraulischer Verstärkung des Aktors
DE10003863B4 (de) * 2000-01-28 2004-11-18 Robert Bosch Gmbh Einspritzdüse
DE10019767A1 (de) * 2000-04-20 2001-10-31 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE10019764B4 (de) * 2000-04-20 2004-09-23 Robert Bosch Gmbh Ventil zum Steuern von Flüssigkeiten
DE10019765B4 (de) * 2000-04-20 2004-12-09 Robert Bosch Gmbh 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
EP1445472B1 (fr) * 2003-02-04 2008-04-09 Siemens VDO Automotive S.p.A. Dispositif de dosage avec joint dynamique
DE102006009659A1 (de) * 2005-07-25 2007-02-01 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung für eine Brennkraftmaschine mit Kraftstoff-Direkteinspritzung
DE202006008930U1 (de) 2006-06-07 2006-08-24 Vermes Technik Gmbh & Co. Kg Volumetrisch arbeitendes Dosierventil
US9091321B2 (en) 2013-09-25 2015-07-28 Honeywell International Inc. Fluid dampers having temperature-dependent viscosity compensation and auxiliary power unit inlet systems employing the same
CN108506130B (zh) * 2018-04-18 2024-06-11 莆田市博泰动力设备有限公司 减少高压共轨燃油动态泄漏的喷油器

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US3719322A (en) * 1971-04-08 1973-03-06 Vernay Laboratories Thermally responsive valve assembly
US4560871A (en) * 1983-12-22 1985-12-24 Marquest Medical Products, Inc. Actuator for control valves and related systems
DE3660781D1 (en) 1985-02-19 1988-10-27 Nippon Denso Co Control valve for controlling fluid passage
JP2636379B2 (ja) * 1988-11-07 1997-07-30 トヨタ自動車株式会社 燃料噴射装置
DE59010904D1 (de) * 1990-09-25 2000-05-31 Siemens Ag Anordnung für einen in Hubrichtung wirkenden adaptiven, mechanischen Toleranzausgleich für den Wegtransformator eines piezoelektrischen Aktors
DE4308297A1 (fr) * 1992-03-20 1993-09-23 Rexroth Mannesmann Gmbh
DE4412948C2 (de) * 1994-04-14 1998-07-23 Siemens Ag Elektrohydraulische Absperrvorrichtung
DE19709794A1 (de) * 1997-03-10 1998-09-17 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
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DE19807903C2 (de) 1998-02-25 2001-11-29 Siemens Ag Vorrichtung und Verfahren zur Kraftübertragung

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Also Published As

Publication number Publication date
CZ20011876A3 (cs) 2002-03-13
WO2001023747A1 (fr) 2001-04-05
HUP0104426A2 (hu) 2002-03-28
HUP0104426A3 (en) 2002-04-29
JP2003510510A (ja) 2003-03-18
DE19946830A1 (de) 2001-05-03
US6547213B1 (en) 2003-04-15

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