EP2633180B1 - Pressure regulating valve - Google Patents
Pressure regulating valve Download PDFInfo
- Publication number
- EP2633180B1 EP2633180B1 EP11757879.9A EP11757879A EP2633180B1 EP 2633180 B1 EP2633180 B1 EP 2633180B1 EP 11757879 A EP11757879 A EP 11757879A EP 2633180 B1 EP2633180 B1 EP 2633180B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- armature
- pressure regulating
- pressure
- regulating valve
- 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.)
- Not-in-force
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/22—Safety or indicating devices for abnormal conditions
-
- 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
- F02M63/0033—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
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- 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
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- 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
- F02M63/005—Pressure relief valves
- F02M63/0052—Pressure relief valves with means for adjusting the opening pressure, e.g. electrically controlled
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- 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
- F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
- F02M63/0073—Pressure balanced 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
- F02M63/0012—Valves
- F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
- F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
-
- 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
- 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
Definitions
- the invention relates to a pressure regulating valve according to the preamble of claim 1.
- the fuel system pressure in the high-pressure accumulator is kept substantially constant by means of a pressure regulating valve.
- the pressure regulating valve opens, when the pressure has fallen below the system pressure, the pressure regulating valve closes. This ensures that the fuel injection into the cylinders of the internal combustion engine takes place under constant conditions. If the fuel pressure in the high-pressure accumulator falls below the vapor pressure of the air dissolved in the fuel, the air is released, so that in addition to the liquid fuel, a gas phase is also contained in the high-pressure accumulator.
- the gas contained in the high-pressure accumulator When starting the internal combustion engine then the gas contained in the high-pressure accumulator must be compressed by the high-pressure pump, so that builds up in the high-pressure accumulator necessary for the operation pressure. Depending on the starting temperature of the internal combustion engine this several engine revolutions are necessary, causing startup delays occur. In order to allow outgassing of the air contained in the high pressure accumulator is provided to put the pressure control valve with the engine off in the open state.
- Out DE 10 2004 002 964 A1 is a pressure regulating valve is known in which when the internal combustion engine, the pressure control valve is open, ie, in that a connection from the high-pressure accumulator to a low-pressure line is released by a closing element.
- the pressure regulating valve has a magnetic actuator, which is energized to close the closing element by an armature, the closing element in a valve seat.
- a spring element is provided which acts counter to the magnetic force of the magnetic actuator and thereby moves the armature and an anchor bolt attached thereto in the opening direction, whereby the closing element lifts from the valve seat and releases a hydraulic return connection between the high pressure accumulator and the low pressure line.
- the hydraulic return connection to the low pressure line takes place from a valve seat downstream valve chamber, are provided from the radially laterally branching holes, which open into a low pressure line in the housing of the high-pressure accumulator.
- DE10 2008 042 801 A1 discloses a pressure control valve with balancing bore in the valve housing.
- the pressure regulating valve according to the invention with the characterizing features of claim 1 has the advantage that the closing element performs a quick opening stroke and remains in a stable position during the open position. This is possible because both sides of the armature are exposed to the same pressure and thus the armature is pressure balanced. As a result, pressure fluctuations in the return line have no effect on the anchor. In addition, an attenuation of the armature is achieved by the arrangement of the armature plate in the armature space during the opening phase.
- the hydraulic return connection is formed by a connecting bolt formed in the anchor bolt between the valve chamber and the armature space, which is preferably designed as a blind hole and a transverse bore pointing away therefrom.
- the hydraulic return connection is realized by at least one guided through the valve housing bore, the connected at one end to the valve space and at the other end to the anchor space.
- the bore can open directly or indirectly into the valve chamber and into the armature space.
- the hydraulic return connection is formed by at least one channel incorporated in the piston guide and / or in the anchor bolt.
- the channel can be formed particularly easily by at least one axially extending groove machined into the piston guide and / or in the anchor bolt.
- axially extending grooves are formed, which form the axially extending channels, wherein between two adjacent grooves in each case a web is executed, which forms with its outer surface a guide surface within the piston guide.
- an outlet throttle which is connected downstream of the armature space, the effect of flow fluctuations between the valve space and the low pressure line can be suppressed and the occurrence of cavitations on the valve seat or on the closing element is reduced.
- the outlet can also be connected directly downstream of the valve chamber.
- FIGS. 1 . 2 and 3 illustrated pressure control valve 10 is inserted into a housing 11 of a high-pressure accumulator 12 of a fuel injection device by means of a threaded sleeve 13 in a receiving space 14.
- the pressure control valve 10 closes or opens a hydraulic connection from the high pressure accumulator 12 to a low pressure port 15 which is connected to a non-illustrated low pressure line, which leads back to a fuel tank, also not shown.
- the pressure regulating valve 10 has a solenoid actuator 17 and a valve element 18, wherein the solenoid actuator 17 actuates the valve element 18.
- the solenoid actuator 17 and the valve element 18 are arranged in a valve housing 20 which has a piston guide 22, a valve piece receptacle 23 and a connection-side receptacle 24.
- valve element 18 is arranged, which comprises a valve piece 25 and a closing element 29.
- the valve piece 25 limits a valve space 26 via a spacer ring.
- a throttle bore 27 leads through the valve piece 25 and hydraulically connects the valve space 26 to the high-pressure accumulator 12.
- a valve seat 28 is further formed for the closing element 29.
- the valve chamber 26 is arranged downstream of the valve seat 28, wherein the closing element 29 is arranged within the valve chamber 26.
- the terminal-side receptacle 24 of the magnetic actuator 17 is arranged with a magnetic coil 30 and an armature 31, wherein the magnetic coil 30 acts on the armature 31.
- the armature 31 is designed with an anchor plate 32 and an anchor bolt 33, wherein the anchor bolt 33 is fixedly connected to the anchor plate 32 and acts on the closing element 29.
- the anchor bolt 33 is guided axially displaceably in the piston guide 22, wherein the piston guide 22 is guided axially through the valve housing 20.
- the magnetic coil 33 forms with the surrounding housing part of the valve housing 20 a magnetic core with a magnetic core end face 34 against which the armature plate 23 abuts when the magnet coil 30 is energized with an armature surface 36.
- connection piece 40 with a connection flange 41 is furthermore hydraulically tightly inserted by means of a sealing ring 42, the low-pressure connection 15 being designed in the connection flange 41.
- an armature space 44 is formed, in which the armature plate 32 is disposed axially movable.
- the armature space 44 is hydraulically connected in the present embodiment via an outlet throttle 45 with the low pressure port 15.
- Adjoining the armature space 44 is a spring chamber 46, which is incorporated in the magnetic core end face 34 and accommodates a compression spring 47 which acts on the magnet armature 31 in the opening direction of the closing element 29.
- the connecting piece 40 is held on the valve housing 20 by means of an encapsulation 48, which contains electrical plug-in contacts 49 for the magnet coil 30.
- a hydraulic return connection 50 between the valve chamber 26 and the armature space 44 is provided.
- the hydraulic return connection 50 between the valve chamber 26 and the armature space 44 the two opposite end faces of the anchor plate 32 within the armature space 44 and the anchor bolt 33 within the valve chamber 26 are exposed to the same pressure, so that the armature 31 is axially movable substantially pressure-balanced.
- the hydraulic return connection 50 is executed by a blind hole 51 guided through the anchor bolt 33 and a transverse bore 52 facing away from it.
- the blind bore 51 opens at an end face 53 in the armature space 44.
- the transverse bore 52 opens laterally into the valve chamber 26.
- the hydraulic return connection 50 through one through the valve housing 20 realized axially guided bore 55, which opens at one end into the valve chamber 26 and the other end of the magnetic core end face 34 in the armature space 44.
- the bore 55 can also open into the other end of the spring chamber 46, which in turn is hydraulically connected to the armature space 44.
- the valve chamber 26 is connected via the armature space 44 with the return line connected to the return port 15.
- the hydraulic return connection 50 is performed by at least one incorporated in the anchor bolt 33 channel according to FIG. 3 is formed by a machined into the anchor bolt 33, axially extending groove 61.
- the channel is executed by four in the anchor bolt 33 incorporated grooves 63 which extend on the surface of the anchor bolt 33 and thereby produce the hydraulic return connection 50 between the valve chamber 26 via the spring chamber 46 to the armature space 44 through the piston guide 22 and the anchor bolt 33.
- the four axially extending grooves 63 are arranged distributed uniformly over the circumference of the valve piston 33. Between two adjacent grooves 63, a web 64 is in each case designed, which forms with its outer surface 65 a guide surface within the piston guide 22.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Magnetically Actuated Valves (AREA)
- Fuel-Injection Apparatus (AREA)
- Valve Device For Special Equipments (AREA)
Description
Die Erfindung betrifft ein Druckregelventil nach dem Oberbegriff des Anspruchs 1.The invention relates to a pressure regulating valve according to the preamble of claim 1.
Im Betrieb einer selbstzündenden Verbrennungskraftmaschine mit einem Hochdruckspeicher (Common Rail) wird der Kraftstoff-Systemdruck im Hochdruckspeicher mittels eines Druckregelventils im Wesentlichen konstant gehalten. Sobald der Druck im Hochdruckspeicher den Systemdruck übersteigt, öffnet das Druckregelventil, wenn der Druck wieder unter den Systemdruck gefallen ist, schließt das Druckregelventil. Hierdurch wird gewährleistet, dass die Kraftstoffeinspritzung in die Zylinder der Verbrennungskraftmaschine unter gleichbleibenden Konditionen erfolgt. Sinkt der Kraftstoffdruck im Hochdruckspeicher unter den Dampfdruck der im Kraftstoff gelösten Luft, gast die Luft aus, sodass neben dem flüssigen Kraftstoff auch eine Gasphase im Hochdruckspeicher enthalten ist. Beim Start der Verbrennungskraftmaschine muss dann das im Hochdruckspeicher enthaltene Gas durch die Hochdruckpumpe komprimiert werden, damit sich im Hochdruckspeicher der für den Betrieb notwendige Druck aufbaut. Abhängig von der Starttemperatur der Verbrennungskraftmaschine sind hierzu mehrere Motorumdrehungen notwendig, wodurch Startverzögerungen auftreten. Um ein Ausgasen der im Hochdruckspeicher enthaltenen Luft zu ermöglichen ist vorgesehen, das Druckregelventil bei abgestelltem Motor in geöffneten Zustand zu stellen.During operation of a self-igniting internal combustion engine with a high-pressure accumulator (common rail), the fuel system pressure in the high-pressure accumulator is kept substantially constant by means of a pressure regulating valve. As soon as the pressure in the high-pressure accumulator exceeds the system pressure, the pressure regulating valve opens, when the pressure has fallen below the system pressure, the pressure regulating valve closes. This ensures that the fuel injection into the cylinders of the internal combustion engine takes place under constant conditions. If the fuel pressure in the high-pressure accumulator falls below the vapor pressure of the air dissolved in the fuel, the air is released, so that in addition to the liquid fuel, a gas phase is also contained in the high-pressure accumulator. When starting the internal combustion engine then the gas contained in the high-pressure accumulator must be compressed by the high-pressure pump, so that builds up in the high-pressure accumulator necessary for the operation pressure. Depending on the starting temperature of the internal combustion engine this several engine revolutions are necessary, causing startup delays occur. In order to allow outgassing of the air contained in the high pressure accumulator is provided to put the pressure control valve with the engine off in the open state.
Aus
Das erfindungsgemäße Druckregelventil mit den kennzeichnenden Merkmalen des Anspruchs 1 hat den Vorteil, dass das Schließelement einen schnellen Öffnungshub ausführt und während der geöffneten Position in einer stabilen Lage bleibt. Dies ist dadurch möglicht, weil beide Seiten des Ankers dem gleichen Druck ausgesetzt sind und somit der Anker druckausgeglichen ist. Dadurch haben Druckschwankungen in der Rücklaufleitung keine Auswirkungen auf den Anker. Zusätzlich wird durch die Anordnung der Ankerplatte im Ankerraum während der Öffnungsphase eine Dämpfung des Ankers erreicht.The pressure regulating valve according to the invention with the characterizing features of claim 1 has the advantage that the closing element performs a quick opening stroke and remains in a stable position during the open position. This is possible because both sides of the armature are exposed to the same pressure and thus the armature is pressure balanced. As a result, pressure fluctuations in the return line have no effect on the anchor. In addition, an attenuation of the armature is achieved by the arrangement of the armature plate in the armature space during the opening phase.
Vorteilhafte Ausführungsformen sind durch die Maßnahmen der Unteransprüche möglich.Advantageous embodiments are possible by the measures of the subclaims.
Gemäß einer ersten Ausführungsform ist die hydraulische Rücklaufverbindung durch eine im Ankerbolzen ausgebildete Verbindungsbohrung zwischen Ventilraum und Ankerraum ausgeführt, die vorzugsweise als Sacklochbohrung und eine davon abzeigende Querbohrung ausgeführt ist.According to a first embodiment, the hydraulic return connection is formed by a connecting bolt formed in the anchor bolt between the valve chamber and the armature space, which is preferably designed as a blind hole and a transverse bore pointing away therefrom.
Im Stand der Technik benannt ist die hydraulische Rücklaufverbindung durch mindestens eine durch das Ventilgehäuse geführte Bohrung realisiert, die einenends mit dem Ventilraum und anderenends mit dem Ankerraum verbunden ist. Dabei kann die Bohrung mittelbar oder unmittelbar in den Ventilraum und in den Ankerraum münden.Named in the prior art, the hydraulic return connection is realized by at least one guided through the valve housing bore, the connected at one end to the valve space and at the other end to the anchor space. In this case, the bore can open directly or indirectly into the valve chamber and into the armature space.
Gemäß einer zweiten Ausführungsform ist die hydraulische Rücklaufverbindung von mindestens einem in die Kolbenführung und/oder in den Ankerbolzen eingearbeiteten Kanal gebildet. Besonders einfach lässt sich der Kanal von mindestens einer in die Kolbenführung und/oder in den Ankerbolzen eingearbeiteten, axial verlaufenden Nut ausbilden. Zweckmäßig sind in den Ankerbolzen vier gleichmäßig über den Umfang verteilte, axial verlaufende Nuten eingebracht, die die axial verlaufenden Kanäle bilden, wobei zwischen zwei benachbarten Nuten jeweils ein Steg ausgeführt ist, der mit seiner Außenfläche eine Führungsfläche innerhalb der Kolbenführung ausbildet.According to a second embodiment, the hydraulic return connection is formed by at least one channel incorporated in the piston guide and / or in the anchor bolt. The channel can be formed particularly easily by at least one axially extending groove machined into the piston guide and / or in the anchor bolt. Appropriately, in the anchor bolt four evenly distributed over the circumference, axially extending grooves are formed, which form the axially extending channels, wherein between two adjacent grooves in each case a web is executed, which forms with its outer surface a guide surface within the piston guide.
Durch eine Anordnung einer Auslassdrossel, die den Ankerraum nachgeschaltet ist, sind die Auswirkung von Strömungsschwankungen zwischen Ventilraum und Niederdruckleitung unterdrückbar und das Auftreten von Kavitationen am Ventilsitz bzw. am Schließelement wird reduziert. Wahlweise kann der Auslass auch dem Ventilraum direkt nachgeschaltet sein.By arranging an outlet throttle, which is connected downstream of the armature space, the effect of flow fluctuations between the valve space and the low pressure line can be suppressed and the occurrence of cavitations on the valve seat or on the closing element is reduced. Optionally, the outlet can also be connected directly downstream of the valve chamber.
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert.An embodiment of the invention is illustrated in the drawing and explained in more detail in the following description.
Es zeigen:
- Figur 1
- eine Schnittdarstellung durch ein erfindungsgemäßes Druckregelventil gemäß einem ersten Ausführungsbeispiel,
- Figur 2
- eine Schnittdarstellung durch ein bekanntes Druckregelventil
- Figur 3
- eine Schnittdarstellung durch ein erfindungsgemäßes Druckregelventil gemäß einem zweites Ausführungsbeispiel und
- Figur 4
- eine Schnittdarstellung durch das Druckregelventil nach der Linie II-II in
Figur 3 .
- FIG. 1
- a sectional view through an inventive pressure control valve according to a first embodiment,
- FIG. 2
- a sectional view through a known pressure control valve
- FIG. 3
- a sectional view through an inventive pressure control valve according to a second embodiment and
- FIG. 4
- a sectional view through the pressure control valve along the line II-II in
FIG. 3 ,
Das in den
Das Druckregelventil 10 weist einen Magnetaktor 17 und ein Ventilelement 18 auf, wobei der Magnetaktor 17 das Ventilelement 18 betätigt. Der Magnetaktor 17 und das Ventilelement 18 sind in einem Ventilgehäuse 20 angeordnet, das eine Kolbenführung 22, eine Ventilstückaufnahme 23 und eine anschlussseitige Aufnahme 24 aufweist.The
In der Ventilstückaufnahme 23 ist das Ventilelement 18 angeordnet, das ein Ventilstück 25 und ein Schließelement 29 umfasst. Das Ventilstück 25 begrenzt über einen Distanzring einen Ventilraum 26. Durch das Ventilstück 25 führt eine Drosselbohrung 27, die den Ventilraum 26 mit dem Hochdruckspeicher 12 hydraulisch verbindet. Im Ventilstück 25 ist weiterhin ein Ventilsitz 28 für das Schließelement 29 ausgebildet. Der Ventilraum 26 ist dem Ventilsitz 28 nachgeordnet, wobei das Schließelement 29 innerhalb des Ventilraums 26 angeordnet ist.In the
In der anschlussseitigen Aufnahme 24 ist der Magnetaktor 17 mit einer Magnetspule 30 und einem Anker 31 angeordnet, wobei die Magnetspule 30 auf den Anker 31 einwirkt. Der Anker 31 ist mit einer Ankerplatte 32 und einem Ankerbolzen 33 ausgeführt, wobei der Ankerbolzen 33 mit der Ankerplatte 32 fest verbunden ist und auf das Schließelement 29 einwirkt. Der Ankerbolzen 33 ist in der Kolbenführung 22 axial verschiebbar geführt, wobei die Kolbenführung 22 durch das Ventilgehäuse 20 axial hindurchgeführt ist.In the terminal-
Die Magnetspule 33 bildet mit dem umgebenden Gehäuseteil des Ventilgehäuses 20 einen Magnetkern mit einer Magnetkernstirnfläche 34, an welcher die Ankerplatte 23 bei bestromter Magnetspule 30 mit einer Ankerfläche 36 anliegt.The
In der anschlussseitigen Aufnahme 24 ist weiterhin ein Anschlussstück 40 mit einem Anschlussflansch 41 mittels eines Dichtrings 42 hydraulisch dicht eingesetzt, wobei im Anschlussflansch 41 der Niederdruckanschluss 15 ausgeführt ist. Zwischen Anschlussstück 40 und der Magnetkernstirnfläche 34 ist ein Ankerraum 44 ausgebildet, in dem die Ankerplatte 32 axial bewegbar angeordnet ist. Der Ankerraum 44 ist beim vorliegenden Ausführungsbeispiel über eine Ablaufdrossel 45 mit dem Niederdruckanschluss 15 hydraulisch verbunden. Es ist aber auch denkbar, den Ventilraum 26 mit dem Niederdruckanschluss 15 zu verbinden. An den Ankerraum 44 grenzt ein Federraum 46 an, der in der Magnetkernstirnfläche 34 eingearbeitet ist und eine Druckfeder 47 aufnimmt, welche in Öffnungsrichtung des Schließelements 29 auf den Magentanker 31 wirkt. Das Anschlussstück 40 ist mittels einer Umspritzung 48, die elektrische Steckkontakte 49 für die Magnetspule 30 enthält, am Ventilgehäuse 20 gehalten.In the connection-
Zur druckausgeglichen Anordnung des Ankers 31 innerhalb des Ankerraums 44 und des Ventilraums 26 ist eine hydraulische Rücklaufverbindung 50 zwischen dem Ventilraum 26 sowie dem Ankerraum 44 vorgesehen. Durch die hydraulischen Rücklaufverbindung 50 zwischen dem Ventilraum 26 und dem Ankerraum 44 sind die beide gegenüberliegende Stirnseiten der Ankerplatte 32 innerhalb des Ankerraums 44 und der Ankerbolzen 33 innerhalb des Ventilraums 26 dem gleichen Druck ausgesetzt, so dass der Anker 31 im Wesentlichen druckausgeglichen axial bewegbar ist.For pressure-balanced arrangement of the
Gemäß dem Ausführungsbeispiel in
Bei einem weiteren erfindungsgemäßen Ausführungsbeispiel wird die hydraulische Rücklaufverbindung 50 von mindestens einem in den Ankerbolzen 33 eingearbeiteten Kanal ausgeführt, der gemäß
Claims (9)
- Pressure regulating valve for opening and closing an outlet of a high-pressure accumulator (12) for an injection device for an internal combustion engine, having a valve element (18) which can be actuated by a solenoid actuator (17), which solenoid actuator acts by way of an armature (31) on a closing element (29) which closes or opens up a hydraulic connection from the high-pressure accumulator (12) to a valve chamber (26), wherein the armature (31) has an armature plate (32) and an armature pin (33) which is guided in axially movable fashion in a valve housing (20), wherein the armature plate (32) is arranged in movable fashion in an armature chamber (44), wherein the valve chamber (26) is hydraulically connected to a low-pressure port (15), and wherein the armature chamber (44) is hydraulically connected via a return connection (50) to the valve chamber (26), characterized in that the return connection (50) is formed by a connecting bore between the valve chamber (26) and armature chamber (44), said connecting bore being formed in the armature pin (33).
- Pressure regulating valve according to Claim 1, characterized in that the connecting bore is formed by a blind bore (51) and by a transverse bore (52) which branches off from said blind bore.
- Pressure regulating valve according to Claim 1, characterized in that the return connection (50) is formed by at least one duct that is worked into the armature pin (33).
- Pressure regulating valve according to Claim 3, characterized in that the duct is formed by at least one axially running groove (61) that is worked into the armature pin (33).
- Pressure regulating valve according to Claim 4, characterized in that four axially running grooves (64) are formed in the armature pin (33) so as to be distributed uniformly over the circumference.
- Pressure regulating valve according to Claim 5, characterized in that, between two adjacent grooves (63), there is formed in each case one web (64) which, by way of its outer surface (65), forms a guide surface within the piston guide (22).
- Pressure regulating valve according to one of the preceding claims, characterized in that the low-pressure port (15) is connected to the armature chamber (44).
- Pressure regulating valve according to Claim 7, characterized in that an outlet throttle (45) is positioned downstream of the armature chamber (44), and in that the outlet throttle (45) is formed in a connector flange (41) of a connector piece (40).
- Pressure regulating valve according to Claim 6, characterized in that the low-pressure port (15) is connected directly to the valve chamber (26).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102010043097A DE102010043097A1 (en) | 2010-10-29 | 2010-10-29 | Pressure control valve |
PCT/EP2011/066316 WO2012055639A2 (en) | 2010-10-29 | 2011-09-20 | Pressure regulating valve |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2633180A2 EP2633180A2 (en) | 2013-09-04 |
EP2633180B1 true EP2633180B1 (en) | 2015-05-27 |
Family
ID=44653337
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP11757879.9A Not-in-force EP2633180B1 (en) | 2010-10-29 | 2011-09-20 | Pressure regulating valve |
Country Status (6)
Country | Link |
---|---|
US (1) | US20130214186A1 (en) |
EP (1) | EP2633180B1 (en) |
JP (1) | JP5882344B2 (en) |
CN (1) | CN103180601B (en) |
DE (1) | DE102010043097A1 (en) |
WO (1) | WO2012055639A2 (en) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2973076A1 (en) * | 2011-03-25 | 2012-09-28 | Bosch Gmbh Robert | PRESSURE REGULATOR, DIESEL INJECTION DEVICE COMPRISING SUCH A REGULATOR, DIESEL ENGINE COMPRISING SUCH AN INJECTION DEVICE AND VEHICLE COMPRISING SUCH AN ENGINE |
FR2988140B1 (en) * | 2012-03-15 | 2016-02-05 | Bosch Gmbh Robert | HIGH PRESSURE FUEL PRESSURE CONTROL VALVE OF INTERNAL COMBUSTION ENGINE FUEL |
DE102012209226A1 (en) | 2012-05-31 | 2013-12-05 | Robert Bosch Gmbh | Pressure control valve |
DE102013219418A1 (en) * | 2013-06-21 | 2014-12-24 | Robert Bosch Gmbh | Pressure control valve |
DE102013211937A1 (en) * | 2013-06-24 | 2014-12-24 | Robert Bosch Gmbh | Pressure control valve with deflection cap |
DE102013222483A1 (en) | 2013-11-06 | 2015-05-07 | Robert Bosch Gmbh | Pressure control valve |
DE102013224395A1 (en) * | 2013-11-28 | 2015-05-28 | Robert Bosch Gmbh | magnetic valve |
DE102014225323A1 (en) | 2014-12-09 | 2016-06-09 | Robert Bosch Gmbh | Shift or pressure control valve for a fuel injection system |
Family Cites Families (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3927932A1 (en) * | 1989-08-24 | 1991-02-28 | Bosch Gmbh Robert | ELECTROMAGNETICALLY ACTUABLE FUEL INJECTION VALVE |
DE4137786C2 (en) * | 1991-11-16 | 1999-03-25 | Bosch Gmbh Robert | Electromagnetically actuated injection valve |
DE4342398C1 (en) * | 1993-12-13 | 1995-04-20 | Daimler Benz Ag | Pressure-compensated solenoid valve |
JP3742996B2 (en) * | 1996-03-25 | 2006-02-08 | 株式会社デンソー | Fuel supply device |
FR2783890B1 (en) * | 1998-09-29 | 2000-12-01 | Eaton Corp | PRESSURE REGULATING SOLENOID VALVE |
JP2001082283A (en) * | 1999-09-20 | 2001-03-27 | Hitachi Ltd | Solenoid fuel injection valve |
US6454191B1 (en) * | 2000-01-10 | 2002-09-24 | Delphi Technologies, Inc. | Electromagnetic fuel injector dampening device |
DE10039077A1 (en) * | 2000-08-10 | 2002-02-21 | Bosch Gmbh Robert | Fuel injection valve esp. of IC engines with solenoid coil and armature and return spring also valve needle for operating valve closing body which together with valve seat surface forms sealed seat |
DE10131201A1 (en) * | 2001-06-28 | 2003-01-16 | Bosch Gmbh Robert | Solenoid valve for controlling an injection valve of an internal combustion engine |
DE102004002964A1 (en) | 2004-01-21 | 2005-08-11 | Robert Bosch Gmbh | Pressure control valve for a high-pressure accumulator of an internal combustion engine |
JP2006299855A (en) * | 2005-04-18 | 2006-11-02 | Denso Corp | Fluid control valve |
JP4483829B2 (en) * | 2005-07-29 | 2010-06-16 | 株式会社デンソー | Electromagnetic actuator |
US7717400B2 (en) * | 2007-04-19 | 2010-05-18 | Aisan Kogyo Kabushiki Kaisha | Fluid pressure regulating device |
JP2009103050A (en) * | 2007-10-23 | 2009-05-14 | Denso Corp | Electromagnetic drive device |
DE102008041362A1 (en) * | 2008-08-20 | 2010-02-25 | Robert Bosch Gmbh | Fuel supplying device for internal combustion engine in motor vehicle, has dosing valve and pressure control valve comprising closing members, which are connected together in rigid manner and are movable on corresponding movement axis |
JP2011132941A (en) * | 2009-11-26 | 2011-07-07 | Nippon Soken Inc | Pressure control valve |
-
2010
- 2010-10-29 DE DE102010043097A patent/DE102010043097A1/en not_active Withdrawn
-
2011
- 2011-09-20 CN CN201180051798.7A patent/CN103180601B/en not_active Expired - Fee Related
- 2011-09-20 JP JP2013535332A patent/JP5882344B2/en not_active Expired - Fee Related
- 2011-09-20 US US13/881,403 patent/US20130214186A1/en not_active Abandoned
- 2011-09-20 EP EP11757879.9A patent/EP2633180B1/en not_active Not-in-force
- 2011-09-20 WO PCT/EP2011/066316 patent/WO2012055639A2/en active Application Filing
Also Published As
Publication number | Publication date |
---|---|
JP5882344B2 (en) | 2016-03-09 |
JP2013540947A (en) | 2013-11-07 |
CN103180601B (en) | 2016-02-24 |
WO2012055639A3 (en) | 2012-06-21 |
CN103180601A (en) | 2013-06-26 |
DE102010043097A1 (en) | 2012-05-03 |
US20130214186A1 (en) | 2013-08-22 |
EP2633180A2 (en) | 2013-09-04 |
WO2012055639A2 (en) | 2012-05-03 |
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