EP2016278B1 - Régulateur de pression avec fonction de circulation de secours et de purge - Google Patents

Régulateur de pression avec fonction de circulation de secours et de purge Download PDF

Info

Publication number
EP2016278B1
EP2016278B1 EP07726779A EP07726779A EP2016278B1 EP 2016278 B1 EP2016278 B1 EP 2016278B1 EP 07726779 A EP07726779 A EP 07726779A EP 07726779 A EP07726779 A EP 07726779A EP 2016278 B1 EP2016278 B1 EP 2016278B1
Authority
EP
European Patent Office
Prior art keywords
pressure
control valve
cavity
closing
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.)
Active
Application number
EP07726779A
Other languages
German (de)
English (en)
Other versions
EP2016278A1 (fr
Inventor
Gerhard Geyer
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 EP2016278A1 publication Critical patent/EP2016278A1/fr
Application granted granted Critical
Publication of EP2016278B1 publication Critical patent/EP2016278B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
    • F02M55/025—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
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M63/0043—Two-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
    • 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
    • F02M63/023—Means for varying pressure in common rails
    • F02M63/0235—Means for varying pressure in common rails by bleeding fuel pressure
    • F02M63/025—Means for varying pressure in common rails by bleeding fuel pressure from the common rail
    • 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
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/46—Details, component parts or accessories not provided for in, or of interest apart from, the apparatus covered by groups F02M69/02 - F02M69/44
    • F02M69/54—Arrangement of fuel pressure regulators

Definitions

  • FIG. 9 is a pressure regulating valve known.
  • the pressure control valve is used on a high-pressure pump, see page 267, Figure 7 of the same publication.
  • the pressure regulating valve comprises a ball valve, which contains a ball-shaped closing body.
  • an armature is received, which is acted upon on the one hand by a compression spring and on the other hand, an electromagnet is arranged opposite.
  • the armature of the pressure control valve is lapped for lubrication and cooling of fuel.
  • the pressure regulating valve If the pressure regulating valve is not actuated, the high pressure applied in the high-pressure storage space or at the outlet of the high-pressure pump is applied via the high-pressure inlet to the pressure regulating valve. Since the electroless electromagnet exerts no force, the high pressure force outweighs the spring force of a compression spring, so that the pressure regulating valve opens and this remains more or less open depending on the amount of fuel delivered.
  • the pressure control valve is activated, d. H. when the electromagnet is energized, the pressure in the high-pressure circuit is increased. For this purpose, a magnetic force is generated in addition to the force exerted by the compression spring.
  • the pressure control valve is closed until there is an equilibrium of forces between the high-pressure force on the one hand and the spring force and the magnetic force on the other hand.
  • the magnetic force of the solenoid is proportional to the drive current I of the solenoid within the pressure control valve.
  • the drive current I can be varied by clocking (pulse width modulation).
  • the pressure control valve is screwed into the high-pressure pump, for example.
  • the air gap L is at the dismantling of the pressure control valve in a receiving body, here for example a high-pressure pump set.
  • DE 102 14 084 A1 refers to an adjustable pressure control valve for fuel injection systems.
  • the fuel injection system comprises a high-pressure storage space, which is acted upon by a high-pressure delivery unit with high-pressure fuel and the fuel injectors supplied with fuel.
  • the high-pressure conveying unit is assigned a pressure regulating valve, which is arranged between a high-pressure side and a low-pressure side and comprises a valve element which can be activated via an electrical point.
  • the pressure regulating valve comprises a housing component, which contains a deformable region, by means of which a gap L between surfaces of an electrically controllable location arrangement can be adjusted during assembly of the pressure regulating valve to a receiving body.
  • a pressure regulating valve In high-pressure injection systems such as, for example, a common rail system for motor vehicles, a pressure regulating valve is used in connection with the two-position concept, which has the task of dynamic pressure reduction in leak-free injectors, such as by means of a piezoelectric actuator controlled fuel injectors in the lower speed and load range the internal combustion engine to allow a very good pressure control at low pressures. This can not be realized in the required quality by alone on the suction side of a high-pressure pumping unit effective regulations. In the case of commercial vehicles, the aforementioned lekage-free injectors have hitherto not been used, which means that the pressure reduction in this application only takes place via the system-inherent leakage of the fuel injectors.
  • a known from the prior art pressure control valve FIG.
  • a fuel injection system according to the preamble of claim 1 is known from WO-03/100247 known.
  • the present invention seeks to provide a pressure control valve for use in high-pressure accumulator injection systems, especially for commercial vehicles, which ensures a Notfahrfunktion.
  • this object is achieved in that the pressure control valve or the high-pressure accumulator body (common rail), a check valve is used, the opening direction is directed from the low pressure side to the high pressure side and which allows a connection of the low pressure side fuel return to the high pressure area of the high pressure accumulator, if by the Cooling in the high pressure accumulator resulting negative pressure of this check valve opens and thus ensures the filling of the high pressure accumulator. This ensures that the high-pressure accumulator is completely filled. Is in the high-pressure accumulator by the high pressure accumulator pressurizing high-pressure pumping unit, such as the high-pressure fuel pump, high pressure, d. H. Built system pressure, the check valve closes the high pressure area against the low pressure side return from.
  • high-pressure pumping unit such as the high-pressure fuel pump, high pressure, d. H.
  • the check valve closes the high pressure area against the low pressure side return from.
  • the non-return valve separating the low-pressure side from the high-pressure side of the high-pressure accumulator can be integrated in the wall of the high-pressure accumulator chamber (common rail) or can also be accommodated in a base plate of the pressure control valve.
  • Decisive for the installation point of the check valve is the fact that through the check valve the high pressure side and the low pressure side of the high-pressure accumulator space in one direction, ie from the low pressure side toward the high pressure side of fuel can flow and thus a constant filling of the cavity of the high pressure fuel accumulator (common Rail) is guaranteed.
  • the direction of action of the electromagnet and the closing spring are interchanged in comparison with the solution known from the prior art.
  • the electromagnet of the pressure regulating valve proposed according to the invention applies a force in the opening direction with respect to a closing element closing the high-pressure accumulator space at one end, while an armature pin which holds the closing element acted upon, acting closing spring acts in relation to the closing element in the closing direction.
  • a negative pressure is created in the latter, as a result of which the valve opens and a subsequent flow of fuel from the low-pressure region into the high-pressure reservoir body results. This ensures a complete filling of the high-pressure accumulator body during system restart and thus a faster start possible.
  • FIG. 1 is to be taken from a known from the prior art pressure control valve in which an electromagnet acts in the closing direction with respect to a closing element and a acting on the armature of the pressure control valve pressure spring acts in the opening direction with respect to the closing element.
  • FIG. 1 shows a pressure regulating valve 10, which has a magnetic coil 26 which can be supplied with current via an electrical connection 12 with a plug connection.
  • the pressure regulating valve 10 as shown in FIG. 1 comprises a housing 14, which is sealed by a sealing ring 16 against the electrical connection 12.
  • a compression spring 18 is received, which encloses an anchor bolt 20 and an anchor plate 22 is acted upon in the opening direction.
  • the armature plate 22 opposite is located on the plug 12, a stop 24.
  • the housing 14 of the pressure control valve 10 as shown in FIG FIG. 1 the already mentioned solenoid 26 is received.
  • An end face 28 of the anchor plate 22 and an end face 30 of the housing 14 are facing each other, wherein the distance between these two end faces 28, 30 defines the stroke of the anchor bolt 20 when the solenoid 26 is energized.
  • the anchor bolt 20 is slidable in an anchor hole 32 of the housing 14 of the pressure regulating valve 10.
  • the housing 14 of the pressure regulating valve 10 is screwed by means of a thread 52 with a high-pressure accumulator 34.
  • low pressure holes 36 are formed on both sides of a cavity, which open into a return line 38, flows back through the low pressure side fuel into a tank of a motor vehicle.
  • a seat ring 42 is disposed within a receptacle 44.
  • a seat 50 is formed for a closing element 48, which in the illustration according to FIG. 1 is formed spherical.
  • a tubular cavity 46 is formed in which fuel under system pressure is stored.
  • the system pressure of the fuel is built up via a high-pressure delivery unit acting on the high-pressure accumulator 34, such as, for example, a high-pressure pump, which in the illustration in FIG. 1 is not reproduced, but is connected to the high-pressure accumulator 34.
  • a high-pressure delivery unit acting on the high-pressure accumulator 34 such as, for example, a high-pressure pump, which in the illustration in FIG. 1 is not reproduced, but is connected to the high-pressure accumulator 34.
  • FIG. 2 shows in a schematic manner the effective directions of the electromagnet and the compression spring according to the embodiment FIG. 1 ,
  • the representation according to FIG. 3 is a block diagram of a pressure control valve can be removed, in which the effective directions of the electromagnet and the valve spring in comparison to the representation according to FIG. 2 are reversed.
  • FIG. 3 shown schematic diagram acts the solenoid 26 as shown in FIG. 1 in a second direction of action 72, ie with respect to the closing element 48 in the opening direction.
  • the compression spring 18 acts in the closing direction with respect to the closing element 48, so that when the magnetic coil 26 becomes de-energized (see FIG FIG. 1 ) Uncontrolled outflow of stored in the cavity 46 of the high pressure accumulator 34 fuel volume is suppressed in the low pressure holes 36 and thus in the return line 38 to the tank of the vehicle. A refilling of the cavity 46 as shown in FIG FIG. 3 However, this is not possible with the thematic basic structure presented there.
  • FIG. 4 is a schematic diagram of the inventively proposed pressure control valve can be seen.
  • FIG. 4 shows that in the solenoid 26 of a pressure regulator valve 80 described in more detail below has an electromagnet 26 which acts in the second direction of action 72, ie in relation to the closing element 48 in the opening direction.
  • a closing force is applied by a closing spring described in more detail below, in the illustration according to FIG. 4 extends in the second direction of action 70, that is, the closing element 48 is acted upon in the closing direction and thus in the seat in the seat ring 42.
  • the solenoid 26 is thus ensured that the stockpiled in the cavity 46 of the high-pressure accumulator 34, under system pressure fuel volume does not uncontrollably flows back into the low pressure holes 36 and thus in the return line 38 to the tank of the vehicle.
  • a check valve 74 is integrated between the cavity 46 of the high pressure accumulator 34 and the low pressure side - indicated here by the low pressure bores 36 - .
  • the check valve has an opening direction which is directed from the low-pressure region to the high-pressure region, ie to the cavity 46 in the high-pressure accumulator 34. Accordingly, the check valve 74 is closed when pressure is applied to the cavity 46 of the high-pressure accumulator 34 in the direction of the low pressure, whereas upon cooling of the high-pressure accumulator 34 and stored in the cavity 46 fuel volume and resulting from the associated decrease in volume of the fuel vacuum - when the Internal combustion engine - allows inflow of fuel from the low pressure side via the check valve 74 into the cavity 46.
  • FIG. 5 is a section through the inventively proposed pressure control valve with reversed direction of action of a closing spring and an electromagnet to refer in more detail.
  • FIG. 5 illustrated pressure control valve 80 is screwed via the thread 52 with the tubular high-pressure accumulator 34 (common rail).
  • the magnetic coil 26 is received, the electrical connections 12 are each enclosed by sealing rings 82.
  • the housing 14 of the pressure control valve 80 with reverse direction of action are also an anchor bolt plate 86 enclosing anchor bolt receptacle 98 and a closing spring 84 enclosing closing spring receptacle 100.
  • the anchor bolt receptacle 98 and the closing spring receptacle 100 are separated by a gap 92.
  • a gap spacing 94 between the mutually facing end sides of the anchor bolt receptacle 98 and the closing spring receptacle 100 is indicated by reference numeral 94.
  • the flattening 90 is the in FIG. 5 spherical closure member 48 opposite.
  • the housing 14 of the pressure control valve 80 with reverse direction of action as shown in FIG FIG. 5 is also disposed within the receptacle 44 of the seat ring 42, in which the seat 50 is formed by the ball-shaped closure member 48.
  • a high pressure side of the seat ring 42 is identified by reference drawing 102, a low pressure side of the seat ring 42, which assigns the cavity 40 in the housing 14, is identified by reference numeral 104.
  • Both the closing spring receptacle 100 and partially enclosed by the anchor bolt receptacle 98 closing spring 84 is biased by a biasing member 96.
  • This biasing member 96, on which one end of the closing spring 84 is supported, acting on the anchor bolt plate 86 of the anchor bolt 20, acting in the second direction of action 70 spring force which is applied by the closing spring 84, can be adjusted.
  • the other end of the closing spring 84 is supported on the anchor bolt plate 86 of the anchor bolt 20.
  • FIG. 5 In the illustration according to FIG. 5 is the check valve 74 in the wall of the tubular high pressure accumulator 34 (common rail).
  • the check valve 74 has a ball-shaped closing element 108, which is acted upon by a spring 106.
  • the spring 106 may, as in FIG. 5 shown to be fixed by a pressed-in ring, so that the spring 106 has to apply only small spring forces.
  • Figure 5.1 a variant of the proposed solution according to the invention is shown, in which the components of the valve 74, designed as a check valve, between the high pressure region and low pressure region, the spherical closure member 108 and fixed by a ring spring 106 are integrally formed in the seat ring 42 and also a filling possibility of Provide cavity 46.
  • the check valve 74 in the wall of the high-pressure accumulator 34 (common rail), the fuel flow is prevented by the pressurized system cavity 46 of the high pressure accumulator 34 in the direction of a low pressure side cavity 112, as shown in the illustration FIG. 5 Spherically shaped closing element 108 is pressed into its seat 110 in the wall of the high pressure accumulator 34.
  • the non-return valve 74 it is achieved with the non-return valve 74 that when the fuel is cooled and the internal combustion engine is shut off via the low-pressure side cavity 112, the cavity 46, which in this case is not subjected to system pressure, is filled via the check valve 74 from the low-pressure side cavity 112.
  • the check valve 74 is opened by adjusting itself in the cavity 46 of the high pressure accumulator 34 upon cooling of the fuel contained therein negative pressure, whereby a filling of the cavity 46 of the high pressure accumulator 34 via the low pressure side cavity 112 is possible.
  • the check valve 74 Will start the Internal combustion engine in the cavity 46 constructed by the over the internal combustion engine when spinning driven high-pressure pump system pressure, the check valve 74, the cavity 46 is separated from the low-pressure side cavity 112 in that the here spherical closure element 108 of the check valve 74 in its seat 110 in the wall of the high-pressure accumulator 34 (common rail) is pressed.
  • the check valve 74 is formed in the wall of the high pressure accumulator 34 (common rail).
  • the check valve 74 it is also possible in the FIG. 5 illustrated check valve 74 also in the base plate 42 of the pressure control valve 80 to accommodate with reverse direction of action.
  • the check valve 74 alone is decisive that is separated by this system pressure leading cavity 46 of the high pressure accumulator 34 of the low pressure side of the pressure control valve 80 with reverse direction of action such that an opening direction of the check valve 74 results from the low pressure side to the high pressure side.
  • FIG. 5 illustrated pressure control valve 80 with reverse direction of action is advantageously used in motor vehicle or commercial vehicle applications, in which leak-free fuel injectors, which are controlled for example by means of a piezoelectric actuator, are used. If the solenoid 26 of the in FIG. 5 shown pressure control valve 80 de-energized, which may occur, for example, by a cable waste, it is ensured via the closing spring 84, which acts in the second direction of action 70 on the spherical closure member 48, that he not stored in the cavity 46 over the fuel opened closure member 48 in the low pressure side cavity 40 in the housing 14 and from there via the low pressure bores 36 in the in FIG. 1 illustrated low-pressure side return 38 flows. This ensures at a cable waste that stored in the cavity 46 under system pressure fuel is stored, so that an emergency drive function of the equipped with a high-pressure accumulator injection system with the present invention proposed pressure control valve 80 is maintained.
  • the anchor bolt 20 is acted upon by the closing spring 84 in the second direction of action 70, so that the closing element 48 remains in its seat 50 in the seat ring 42. Furthermore, it is ensured by the either in the wall of the high-pressure accumulator 34 (common rail) check valve 74 or recessed into a base plate of the pressure control valve 80 with reverse direction of action valve 74 that in the case of Stromlos becoming the solenoid 26 fuel in the cavity 46 of the high-pressure accumulator 34 (common rail) can flow from the low pressure region 112 when the fuel volume z. B. reduced by cooling and thus creates a negative pressure in the high pressure storage volume.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Safety Valves (AREA)

Claims (9)

  1. Système d'injection de carburant pour moteurs à combustion interne, comprenant un accumulateur haute pression (34), qui présente une cavité (46) à la pression du système et l'accumulateur de pression (34) étant associé à une soupape de régulation de pression (80) à commande électromagnétique, avec laquelle la cavité (46) peut être connectée à un côté basse pression (36, 38, 40, 112) de l'accumulateur haute pression (34), caractérisé en ce qu'entre la cavité (46) et le côté basse pression (36, 38 40, 112) de l'accumulateur haute pression (34) est disposée une soupape (74) permettant le remplissage de l'accumulateur haute pression (34) du côté basse pression vers le côté à la pression du système.
  2. Système d'injection de carburant selon la revendication 1, caractérisé en ce qu'une bobine magnétique (26) de la soupape de régulation de pression (80) produit une force agissant dans la direction de l'ouverture (72) par rapport à un élément de fermeture (48).
  3. Système d'injection de carburant selon la revendication 1, caractérisé en ce qu'un ressort de fermeture (84) de la soupape de régulation de pression (80) produit une force agissant dans la direction de fermeture (70) par rapport à l'élément de fermeture (48).
  4. Système d'injection de carburant selon la revendication 3, caractérisé en ce que la force agissant dans la direction de fermeture (70) est ajustée par le ressort de fermeture (48) par le biais d'un élément de précontrainte (96) vissé dans le boîtier (14).
  5. Système d'injection de carburant selon la revendication 1, caractérisé en ce que la soupape (74) est réalisée sous forme de soupape de non retour.
  6. Système d'injection de carburant selon la revendication 1, caractérisé en ce que la soupape (74) est soit incorporée dans la paroi de l'accumulateur haute pression (34), soit est réalisée dans une plaque de base (42) de la soupape de régulation de pression (80).
  7. Système d'injection de carburant selon la revendication 3, caractérisé en ce que le ressort de fermeture (84) est entouré par un logement de boulon d'ancrage (98), qui est espacé d'un certain intervalle d'espacement (94) d'un logement (100) du ressort de fermeture.
  8. Système d'injection de carburant selon la revendication 7, caractérisé en ce que l'intervalle d'espacement (94) définit entre le logement de boulon d'ancrage (98) et le logement (100) du ressort de fermeture une course de levage d'un boulon d'ancrage (20) dans le boîtier (14) de la soupape de régulation de pression (80).
  9. Système d'injection de carburant selon la revendication 1, caractérisé en ce que la cavité (46) de l'accumulateur haute pression (34), lorsque le moteur à combustion interne est arrêté et que la dépression dans la cavité (46) diminue en raison du refroidissement du carburant, est équilibrée par le biais de la soupape (74) du côté basse pression (36, 38, 40, 112) et la cavité (46) est toujours remplie.
EP07726779A 2006-05-04 2007-03-12 Régulateur de pression avec fonction de circulation de secours et de purge Active EP2016278B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006020692A DE102006020692A1 (de) 2006-05-04 2006-05-04 Druckregelventil mit Notfahr- und Belüftungsfunktion
PCT/EP2007/052264 WO2007128606A1 (fr) 2006-05-04 2007-03-12 RÉgulateur de pression avec fonction de circulation de secours et de purge

Publications (2)

Publication Number Publication Date
EP2016278A1 EP2016278A1 (fr) 2009-01-21
EP2016278B1 true EP2016278B1 (fr) 2009-11-04

Family

ID=38069857

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07726779A Active EP2016278B1 (fr) 2006-05-04 2007-03-12 Régulateur de pression avec fonction de circulation de secours et de purge

Country Status (6)

Country Link
US (1) US20090199820A1 (fr)
EP (1) EP2016278B1 (fr)
JP (1) JP2009535562A (fr)
AT (1) ATE447669T1 (fr)
DE (2) DE102006020692A1 (fr)
WO (1) WO2007128606A1 (fr)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2951783A1 (fr) * 2009-10-22 2011-04-29 Bosch Gmbh Robert Regulateur de pression pour dispositif d'injection diesel comportant des moyens assurant un fonctionnement en mode degrade, moteur thermique comportant un tel dispositif d'injection et vehicule
DE102009047649A1 (de) * 2009-12-08 2011-06-09 Robert Bosch Gmbh Druckregelventil zur Regelung des Drucks in einem Hochdruck-Kraftstoffspeicher einer Brennkraftmaschine
DE102010001252A1 (de) * 2010-01-27 2011-07-28 Robert Bosch GmbH, 70469 Kraftstoffeinspritzsystem mit integriertem Hochdruckspeicher an einem Zylinderkopf
JP5780581B2 (ja) * 2010-12-28 2015-09-16 ボッシュ株式会社 コモンレール式燃料噴射制御装置用圧力制御弁
DE102011075059A1 (de) * 2011-05-02 2012-11-08 Robert Bosch Gmbh Brennstoffverteiler
FR2982327B1 (fr) * 2011-11-07 2013-11-29 Delphi Tech Holding Sarl Ensemble de bouchon pour vanne haute pression
DE102011090010B4 (de) 2011-12-28 2019-07-25 Continental Automotive Gmbh Druckregelventil
CN104093968B (zh) * 2012-02-07 2016-10-12 甘瑟-许德罗玛格股份公司 燃料喷射阀和用于喷射燃料的装置
JP5838919B2 (ja) * 2012-06-18 2016-01-06 株式会社日本自動車部品総合研究所 圧力制御装置
FR2999658A1 (fr) * 2012-12-18 2014-06-20 Delphi Technologies Holding Vanne haute pression
JP6201504B2 (ja) * 2013-08-09 2017-09-27 株式会社デンソー 燃料噴射装置
US10539104B2 (en) * 2017-09-20 2020-01-21 Stanadyne Llc Three stage proportional control valve

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2841174A (en) * 1954-12-14 1958-07-01 Charles F Frye Valve
US3289694A (en) * 1963-03-27 1966-12-06 Deltrol Corp Ball check valve with particular cage means
FR2093250A5 (fr) * 1970-06-08 1972-01-28 Peugeot
DE19645243C2 (de) * 1996-11-02 1998-10-29 Orange Gmbh Druckspeicher-Einspritzvorrichtung
US6435210B1 (en) * 1998-03-31 2002-08-20 Continental Teves Ag & Co. Ohg Electromagnetic valve
DE10016242B4 (de) * 2000-03-31 2006-04-13 Siemens Ag Druckregelventil mit integrierter Sicherheitsfunktion
JP2002004975A (ja) * 2000-06-21 2002-01-09 Toyota Motor Corp 高圧燃料供給装置
JP2002115622A (ja) * 2000-10-12 2002-04-19 Toyota Motor Corp 高圧燃料供給装置
DE10138756A1 (de) * 2001-08-07 2003-02-20 Bosch Gmbh Robert Kraftstoffhochdruckspeicher
DE10214084A1 (de) * 2002-03-28 2003-10-30 Bosch Gmbh Robert Einstellbares Druckregelventil für Kraftstoffeinspritzsysteme
DE10222895A1 (de) * 2002-05-23 2003-12-11 Bosch Gmbh Robert Hochdruckspeicher für Kraftstoffeinspritzsysteme mit integriertem Druckregelventil
DE10246594A1 (de) * 2002-10-05 2004-04-15 Robert Bosch Gmbh Steuerbarer Druckspeicher für Kraftfahrzeuge
DE102004037557A1 (de) * 2004-08-03 2006-03-16 Robert Bosch Gmbh Kraftstoffeinspritzsystem
JP4114654B2 (ja) * 2004-09-29 2008-07-09 株式会社デンソー コモンレール式燃料噴射装置

Also Published As

Publication number Publication date
ATE447669T1 (de) 2009-11-15
EP2016278A1 (fr) 2009-01-21
US20090199820A1 (en) 2009-08-13
DE102006020692A1 (de) 2007-11-08
DE502007001915D1 (de) 2009-12-17
WO2007128606A1 (fr) 2007-11-15
JP2009535562A (ja) 2009-10-01

Similar Documents

Publication Publication Date Title
EP2016278B1 (fr) Régulateur de pression avec fonction de circulation de secours et de purge
EP2238338B1 (fr) Système d'injection de combustible d'un moteur à combustion interne
DE19612413B4 (de) Druckfluid-Versorgungssystem, insbesondere für ein Kraftstoff-Einspritzsystem
EP2137400B1 (fr) Soupape de réglage de la pression
DE19630938C2 (de) Kraftstoffzuleitung mit einem Volumenstromregelventil und Volumenstromregelventil
EP1654456A1 (fr) Dispositif d'injection de carburant pour moteur a combustion interne
WO1988000292A1 (fr) Dispositif d'injection de carburant pour moteurs a combustion interne
EP3036430B1 (fr) Dispositif pour pompe à haute pression pour véhicule automobile
EP1799999B1 (fr) Systeme de carburant pour un moteur a combustion interne
WO2002073028A2 (fr) Soupape a siege/coulisse comportant une tige de compensation de pression
DE102010039051A1 (de) Einspritzvorrichtung
DE102016212671B4 (de) Ansteuerverfahren zum Ansteuern eines Einlassventils einer Kraftstoffhochdruckpumpe und Kraftstoffeinspritzsystem
DE102006020634B4 (de) Einspritzinjektor für Brennkraftmaschinen
DE102012221157A1 (de) Druckregelventil für einen Hochdruckspeicher eines Verbrennungsmotors
DE102007026834A1 (de) Elektromagnetisches Regelventil und Einspritzanlage für eine Brennkraftmaschine
EP2659127B1 (fr) Conjoncteur-disjoncteur pour un système d'injection de carburant d'un moteur à combustion interne
WO2002090766A1 (fr) Systeme d'injection a accumulateur (rampe commune) pour moteurs a combustion interne
DE102004020941B9 (de) Druckregelanordnung
DE102015226248A1 (de) Elektromagnetisch betätigbares Einlassventil und Hochdruckpumpe mit Einlassventil
DE102014221660A1 (de) Verfahren zur Regelung der Fördermenge einer Hochdruckpumpe sowie Hochdruckpumpe
DE19952511B4 (de) Common-Rail-Injektor
EP3177859A1 (fr) Soupape de régulation de pression à capteur de pression intégré
WO2006013151A1 (fr) Procede et dispositif pour la reduction de pression de rampe dans un systeme d'injection a rampe d'alimentation commune
DE102012218384A1 (de) Speichereinspritzsystem
DE102016203516A1 (de) Elektromagnetisch betätigbares Einlassventil und Hochdruckpumpe mit Einlassventil

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20081204

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK RS

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

DAX Request for extension of the european patent (deleted)
GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 502007001915

Country of ref document: DE

Date of ref document: 20091217

Kind code of ref document: P

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
LTIE Lt: invalidation of european patent or patent extension

Effective date: 20091104

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091104

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100215

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091104

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100304

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091104

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100304

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091104

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091104

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091104

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091104

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091104

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091104

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091104

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091104

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100204

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091104

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091104

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

BERE Be: lapsed

Owner name: ROBERT BOSCH G.M.B.H.

Effective date: 20100331

26N No opposition filed

Effective date: 20100805

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100331

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100205

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091104

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20110312

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20100331

Year of fee payment: 4

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110331

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110312

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100312

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100505

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091104

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091104

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 447669

Country of ref document: AT

Kind code of ref document: T

Effective date: 20120312

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120312

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20140319

Year of fee payment: 8

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20151130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150331

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20200526

Year of fee payment: 14

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502007001915

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20211001