EP2859216B1 - Pressure control valve - Google Patents

Pressure control valve Download PDF

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Publication number
EP2859216B1
EP2859216B1 EP13721721.2A EP13721721A EP2859216B1 EP 2859216 B1 EP2859216 B1 EP 2859216B1 EP 13721721 A EP13721721 A EP 13721721A EP 2859216 B1 EP2859216 B1 EP 2859216B1
Authority
EP
European Patent Office
Prior art keywords
opening
armature
pressure
armature plate
regulating 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.)
Not-in-force
Application number
EP13721721.2A
Other languages
German (de)
French (fr)
Other versions
EP2859216A1 (en
Inventor
Pierre-Marie Rochas
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2859216A1 publication Critical patent/EP2859216A1/en
Application granted granted Critical
Publication of EP2859216B1 publication Critical patent/EP2859216B1/en
Not-in-force legal-status Critical Current
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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
    • F02M63/007—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
    • F02M63/0014—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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/07—Fuel-injection apparatus having means for avoiding sticking of valve or armature, e.g. preventing hydraulic or magnetic sticking of parts

Definitions

  • the invention relates to a pressure regulating valve according to the preamble of claim 1.
  • a pressure control valve in which at standstill of the internal combustion engine, the pressure control valve is open, that is, that a connection from the high pressure accumulator is released in a low pressure line from a closing element.
  • the pressure regulating valve has a magnetic actuator with a magnetic core and a magnetic tanker, the magnetic actuator being energized to close the closing element, in which a magnetic armature places the closing element in its valve seat.
  • a spring element is provided, which moves the magnet armature in the opening direction against the magnetic force of the magnetic actuator, whereby the closing element lifts off from the valve seat and a hydraulic return connection between the high pressure accumulator and the low pressure line is released.
  • the magnet armature has an armature plate, which is arranged in an armature space formed above the magnetic core.
  • a magnetic coil is accommodated with dimensionally stablemaschineieriten, wherein the Victorier202e have at the magnetic core end face perpendicular in the direction of the armature space.
  • the pressure control valve according to the invention with the characterizing features of the claim has the advantage that a better flow for the pressure compensation is created by the formation of a radial extension of the further implementation in the residual air gap.
  • the further implementation in the residual air gap disk manufacturing technology is easy to manufacture and leads to no significant additional manufacturing costs in the production of the pressure control valve.
  • the pressure compensation channel ensures that pressure fluctuations in the return line have no effect on the armature and that during the opening phase of the closing element, an attenuation of the armature is achieved.
  • the radial extension forms in the residual air gap disk a flow channel which extends substantially from the opening of the pressure equalization channel up to the passage formed on the anchor plate. Conveniently, the radial extension covers the opening, so that the opening of the pressure equalization channel opens into the extension.
  • the radial extension expediently has a slot-shaped form.
  • the slot shape of the radial extension is designed with a substantially constant width, wherein the width of the slot is formed by the diameter of the further implementation.
  • the slot shape of the radial extension is designed with a decreasing width, wherein the width tapers from the diameter of the further passage to the opening at least approximately to the diameter of the opening.
  • the opening of the pressure equalization channel is seconded as close as possible to the bushing.
  • the opening lies on a line that intersects the center of the residual air gap disk and the center of the further feedthrough.
  • FIG. 1 illustrated pressure control valve is inserted into a housing 21 of a high-pressure accumulator chamber 22 of a fuel injection device of an internal combustion engine.
  • the pressure regulating valve has a solenoid actuator 10 and a valve element 11, wherein the solenoid actuator 10 actuates the valve element 11.
  • the solenoid actuator 10 is arranged in a valve housing 12, which has a piston guide 13, a valve piece receptacle 14 and a connection-side receptacle 15.
  • the valve element 11 comprises a valve piston 16 with a closing element 17 in the form of a ball.
  • valve piece 18 is formed with a valve seat 19 for the closing element 17, the closing element 17 acting on the valve seat 19.
  • the valve member 18 defines a spacer ring via a valve chamber 23 into which a throttle bore 25 leads, which connects the valve chamber 23 with the high-pressure accumulator chamber 22 when the closing element 17 is open.
  • the valve chamber 23 continue to open, for example, two lateral hydraulic connections 26 which are connected to a low pressure line 27, which in turn lead to a return system.
  • the magnetic actuator 10 comprises a magnetic core 30 with a magnetic coil 32 and a magnet armature 33, the magnetic coil 32 acting on the armature 33 via the magnetic core 30.
  • the armature 33 has an anchor plate 34 and an anchor bolt 35, wherein the anchor bolt 35 is fixedly connected to the anchor plate 34.
  • the anchor bolt 35 simultaneously forms the valve piston 16, so that the armature 33 acts on the closing element 17 by means of the anchor bolt 35.
  • the anchor bolt 35 is guided axially displaceably in the piston guide 13, wherein the piston guide 13 is guided axially through the valve housing 12.
  • the magnetic core 30 has, facing the armature plate 34, a magnetic core end face 31, which is also called a pole face.
  • An armature surface 36 is formed on the armature plate 34, wherein the armature surface 36 forms the underside or the lower front side of the armature plate 34.
  • a residual air gap disc 50 is arranged between the magnetic core 30 and the anchor plate 34.
  • a spring chamber 28 is further introduced to the magnetic core end face 31, in which a compression spring 29 is arranged, which acts in the opening direction on the magenta tank 33.
  • a cover 40 is used hydraulically tight.
  • the end cover 40 surrounds the armature plate 34 of the armature 33 and forms around the armature plate 34 around an armature space 44 from.
  • the anchor plate 34 is arranged axially movable.
  • the magnetic coil 30 is for electrical contacting with a first dimensionally stablemaschineierloch 41 a and a second dimensionally stablemaschineierloch 41b carried out, which lead out substantially perpendicularly from the magnetic core end face 34 and are each surrounded by an insulating sleeve 42a, 42b.
  • the armature plate 32 has a first passage 43a for the continuation of the first contact pin 41a and a second passage 43b for the continuation of the second contact pin 41b.
  • the passages 43a, 43b are designed such that a gap 45a, 45b is formed between the insulating sleeves 42a and 42b and the passages 43a, 43b. The function of the gap 45a, 45b will be discussed later.
  • the contacting pins 41a, 41b are guided by means of the insulating sleeves 42a, 42b into an electrically insulating encapsulation 46 arranged above the end cap 40, where the contacting pins 41a, 41b are electrically contacted. For tight reception of the contact pins 41a, 41b, these are enclosed on the end faces of the insulating sleeves 42a, 42b each with an O-ring 47 in the end cover 40.
  • valve space 23 and the armature space 44 are hydraulically connected to each other via a pressure equalization channel 60.
  • the pressure equalization channel 60 opens at the magnetic core end face 31 with an opening 61 into the armature space 44.
  • the gaps 45a, 45b formed on the armature plate 34 pass between the insulating sleeves 42a and 42b and the passages 43a, 43b as a passage used by fuel for pressure equalization.
  • at least the passages 43b located in the vicinity of the opening 61 may have a larger diameter or a widening.
  • a transverse flow channel 56 is formed, which ensures a hydraulic connection between the opening 61 and the gap 45b. It is not necessary that the radial extension 54 extends to the spring chamber space 28.
  • the shortest possible radial extent of the flow channel 56 is achieved if the opening 61 of the pressure compensation channel 60 to be arranged in the vicinity of one of the passages 43 b.
  • the easiest way to choose the position is by the opening 61 in accordance with FIGS. 2 and 3 is aligned on a line 48 which intersects the center of the residual air gap disc 50 and the center of the further passage 53b.
  • the proximity of the opening 61 to the insulating sleeve 42a, 42b is limited, however, because the pressure equalizing channel 60 can not be passed through an annular magnetic coil receptacle 38 in which the magnetic coil 32 is molded with an insulating compound.
  • the extension 54 is formed by a slot shape with a constant width, wherein the width of the slot is formed by the diameter of the further passage 53b.
  • the extension 54 is formed by a slot shape with a decreasing width to the opening 61, which tapers from the diameter of the further passage 53b to the opening 61 substantially to the diameter of the opening 61.

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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)

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.

Stand der TechnikState of the art

Aus EP 2333298 A1 ist ein Druckregelventil bekannt, bei dem bei Stillstand der Verbrennungskraftmaschine das Druckregelventil geöffnet ist, d.h., dass eine Verbindung vom Hochdruckspeicher in eine Niederdruckleitung von einem Schließelement freigegeben wird. Dazu weist das Druckregelventil einen Magnetaktor mit einem Magnetkern und einem Magentanker auf, wobei der Magnetaktor zum Schließen des Schließelements bestromt wird, in dem ein Magnetanker das Schließelement in seinen Ventilsitz stellt. Zum Öffnen des Schließelements ist ein Federelement vorgesehen, das entgegen der Magnetkraft des Magnetaktors den Magnetanker in Öffnungsrichtung bewegt, wodurch das Schließelement von dem Ventilsitz abhebt und eine hydraulische Rücklaufverbindung zwischen dem Hochdruckspeicher und der Niederdruckleitung freigegeben wird. Der Magnetanker weist eine Ankerplatte auf, die in einem oberhalb des Magnetkerns ausgebildeten Ankerraum angeordnet ist. Im Magnetkern ist eine Magnetspule mit formstabilen Kontaktierstiften aufgenommen, wobei die Kontaktierstifte an der Magnetkernstirnfläche senkrecht in Richtung des Ankerraums weisen. Zur Weiterführung der Kontaktierstifte in einem oberhalb des Ankerraums liegenden Abschlussdeckel sind in der Ankerplatte Durchführungen für die Kontaktierstifte ausgebildet.Out EP 2333298 A1 a pressure control valve is known in which at standstill of the internal combustion engine, the pressure control valve is open, that is, that a connection from the high pressure accumulator is released in a low pressure line from a closing element. For this purpose, the pressure regulating valve has a magnetic actuator with a magnetic core and a magnetic tanker, the magnetic actuator being energized to close the closing element, in which a magnetic armature places the closing element in its valve seat. To open the closing element, a spring element is provided, which moves the magnet armature in the opening direction against the magnetic force of the magnetic actuator, whereby the closing element lifts off from the valve seat and a hydraulic return connection between the high pressure accumulator and the low pressure line is released. The magnet armature has an armature plate, which is arranged in an armature space formed above the magnetic core. In the magnetic core, a magnetic coil is accommodated with dimensionally stable Kontaktierstiften, wherein the Kontaktierstifte have at the magnetic core end face perpendicular in the direction of the armature space. To continue the Kontaktierstifte lying in a lying above the anchor space end cover feedthroughs for the Kontaktierstifte formed in the anchor plate.

Im Stand der Technik wird vorgeschlagen, den Ankerraum über einen durch das Ventilgehäuse geführte Druckausgleichskanal hydraulisch mit einem an Niederdruck angebundenen Ventilraum zu verbinden. Damit die beide Stirnseiten der Ankerplatte des Magnetankers dem gleichen Druck ausgesetzt sind, ist fluchtend zum Druckausgleichskanal in der Ankerplatte zusätzlich eine Bohrung mit einer eingesetzten Hülse eingebracht, über welche der Druckausgleichskanal an die der Ankerfläche gegenüberliegenden Stirnseite der Ankerplatte weitergeführt wird.In the prior art it is proposed to hydraulically connect the armature space via a pressure compensation channel guided through the valve housing to a valve space connected to low pressure. Thus, the two faces of the armature plate of the magnet armature are exposed to the same pressure, a bore with an inserted sleeve is in alignment with the pressure equalization channel in the anchor plate additionally introduced, via which the pressure equalization channel is continued to the armature surface opposite end face of the anchor plate.

Offenbarung der ErfindungDisclosure of the invention

Das erfindungsgemäße Druckregelventil mit den kennzeichnenden Merkmalen des Anspruchs hat den Vorteil, dass durch die Ausbildung einer radialen Erweiterung an der weiteren Durchführung in der Restluftspaltscheibe eine bessere Durchströmung für den Druckausgleich geschaffen wird. Die weitere Durchführung in der Restluftspaltscheibe ist fertigungstechnisch einfach herstellbar und führt zu keinen wesentlichen zusätzlichen Fertigungskosten bei der Herstellung des Druckregelventils. Der Druckausgleichskanal bewirkt, dass Druckschwankungen in der Rücklaufleitung keine Auswirkungen auf den Magnetanker haben und dass während der Öffnungsphase des Schließelements eine Dämpfung des Magnetankers erreicht wird.The pressure control valve according to the invention with the characterizing features of the claim has the advantage that a better flow for the pressure compensation is created by the formation of a radial extension of the further implementation in the residual air gap. The further implementation in the residual air gap disk manufacturing technology is easy to manufacture and leads to no significant additional manufacturing costs in the production of the pressure control valve. The pressure compensation channel ensures that pressure fluctuations in the return line have no effect on the armature and that during the opening phase of the closing element, an attenuation of the armature is achieved.

Vorteilhafte Weiterbildungen des Druckregelventils sind durch die Merkmale der Unteransprüche möglich.Advantageous developments of the pressure control valve are possible by the features of the subclaims.

Die radiale Erweiterung bildet in der Restluftspaltscheibe einen Strömungskanal, welcher sich im Wesentlichen von der Öffnung des Druckausgleichskanals bis hin zu der an der Ankerplatte ausgebildeten Durchführung erstreckt. Zweckmäßigerweise überdeckt die radiale Erweiterung die Öffnung, so dass die Öffnung des Druckausgleichskanals in die Erweiterung mündet.The radial extension forms in the residual air gap disk a flow channel which extends substantially from the opening of the pressure equalization channel up to the passage formed on the anchor plate. Conveniently, the radial extension covers the opening, so that the opening of the pressure equalization channel opens into the extension.

Die radiale Erweiterung weist zweckmäßigerweise eine langlochförmige Form auf. Gemäß einer ersten Ausführungsform ist die Langlochform der radialen Erweiterung mit einer im Wesentlichen gleichbleibenden Breite ausgeführt, wobei die Breite des Langlochs vom Durchmesser der weiteren Durchführung gebildet ist. Gemäß einer zweiten Ausführungsform ist die Langlochform der radialen Erweiterung mit einer abnehmenden Breite ausgeführt, wobei sich die Breite vom Durchmesser der weiteren Durchführung bis zur Öffnung hin zumindest annähernd auf den Durchmesser der Öffnung verjüngt.The radial extension expediently has a slot-shaped form. According to a first embodiment, the slot shape of the radial extension is designed with a substantially constant width, wherein the width of the slot is formed by the diameter of the further implementation. According to a second embodiment, the slot shape of the radial extension is designed with a decreasing width, wherein the width tapers from the diameter of the further passage to the opening at least approximately to the diameter of the opening.

Um den Strömungskanal so kurz wie möglich auszuführen, wird die Öffnung des Druckausgleichskanals so nahe wie möglich an der Durchführung abgeordnet. Zweckmäßigerweise liegt die Öffnung auf einer Linie, die das Zentrum der Restluftspaltscheibe und das Zentrum der weiteren Durchführung schneidet.To make the flow channel as short as possible, the opening of the pressure equalization channel is seconded as close as possible to the bushing. Conveniently, the opening lies on a line that intersects the center of the residual air gap disk and the center of the further feedthrough.

Ausführungsbeispieleembodiments

Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert.Embodiments of the invention are illustrated in the drawings and explained in more detail in the following description.

Es zeigen:

Figur 1
eine Schnittdarstellung durch ein Druckregelventil,
Figur 2
eine Draufsicht auf eine Restluftspaltscheibe gemäß einer ersten Ausführungsform und
Figur 3
eine Draufsicht auf eine Restluftspaltscheibe gemäß einer zweiten Ausführungsform.
Show it:
FIG. 1
a sectional view through a pressure control valve,
FIG. 2
a plan view of a residual air gap disc according to a first embodiment and
FIG. 3
a plan view of a residual air gap disc according to a second embodiment.

Das in Figur 1 dargestellte Druckregelventil ist in ein Gehäuse 21 eines Hochdruckspeicherraumes 22 einer Kraftstoffeinspritzeinrichtung einer Verbrennungskraftmaschine eingesetzt.This in FIG. 1 illustrated pressure control valve is inserted into a housing 21 of a high-pressure accumulator chamber 22 of a fuel injection device of an internal combustion engine.

Das Druckregelventil weist einen Magnetaktor 10 und ein Ventilelement 11 auf, wobei der Magnetaktor 10 das Ventilelement 11 betätigt. Das Magnetaktor 10 ist in einem Ventilgehäuse 12 angeordnet, das eine Kolbenführung 13, eine Ventilstückaufnahme 14 und eine anschlussseitige Aufnahme 15 aufweist. Das Ventilelement 11 umfasst einen Ventilkolben 16 mit einem Schließelement 17 in Form einer Kugel.The pressure regulating valve has a solenoid actuator 10 and a valve element 11, wherein the solenoid actuator 10 actuates the valve element 11. The solenoid actuator 10 is arranged in a valve housing 12, which has a piston guide 13, a valve piece receptacle 14 and a connection-side receptacle 15. The valve element 11 comprises a valve piston 16 with a closing element 17 in the form of a ball.

In der Ventilstückaufnahme 14 ist ein Ventilstück 18 mit einem Ventilsitz 19 für das Schließelement 17 ausgebildet, wobei das Schließelement 17 auf den Ventilsitz 19 einwirkt. Das Ventilstück 18 begrenzt über einen Distanzring einen Ventilraum 23, in den eine Drosselbohrung 25 führt, die den Ventilraum 23 mit dem Hochdruckspeicherraum 22 bei geöffnetem Schließelement 17 verbindet. In den Ventilraum 23 münden weiterhin beispielsweise zwei seitliche hydraulische Verbindungen 26, die mit einer Niederdruckleitung 27 verbunden sind, die wiederum in ein Rücklaufsystem führen.In the valve piece receptacle 14, a valve piece 18 is formed with a valve seat 19 for the closing element 17, the closing element 17 acting on the valve seat 19. The valve member 18 defines a spacer ring via a valve chamber 23 into which a throttle bore 25 leads, which connects the valve chamber 23 with the high-pressure accumulator chamber 22 when the closing element 17 is open. In the valve chamber 23 continue to open, for example, two lateral hydraulic connections 26 which are connected to a low pressure line 27, which in turn lead to a return system.

Der Magnetaktor 10 umfasst einen Magnetkern 30 mit einer Magnetspule 32 und einen Magnetanker 33, wobei die Magnetspule 32 auf den Magnetanker 33 über den Magnetkern 30 einwirkt. Der Magnetanker 33 weist eine Ankerplatte 34 und einem Ankerbolzen 35 auf, wobei der Ankerbolzen 35 mit der Ankerplatte 34 fest verbunden ist. Der Ankerbolzen 35 bildet gleichzeitig den Ventilkolben 16, so dass der Magnetanker 33 mittels des Ankerbolzens 35 auf das Schließelement 17 einwirkt. Die Ankerbolzen 35 ist in der Kolbenführung 13 axial verschiebbar geführt, wobei die Kolbenführung 13 durch das Ventilgehäuse 12 axial hindurchgeführt ist.The magnetic actuator 10 comprises a magnetic core 30 with a magnetic coil 32 and a magnet armature 33, the magnetic coil 32 acting on the armature 33 via the magnetic core 30. The armature 33 has an anchor plate 34 and an anchor bolt 35, wherein the anchor bolt 35 is fixedly connected to the anchor plate 34. The anchor bolt 35 simultaneously forms the valve piston 16, so that the armature 33 acts on the closing element 17 by means of the anchor bolt 35. The anchor bolt 35 is guided axially displaceably in the piston guide 13, wherein the piston guide 13 is guided axially through the valve housing 12.

Der Magnetkern 30 weist zur Ankerplatte 34 weisend eine Magnetkernstirnfläche 31 auf, die auch Polfläche genannt wird. An der Ankerplatte 34 ist eine Ankerfläche 36 ausgebildet, wobei die Ankerfläche 36 die Unterseite bzw. die untere Stirnseite der Ankerplatte 34 bildet. Zwischen dem Magnetkern 30 und der Ankerplatte 34 ist eine Restluftspaltscheibe 50 angeordnet. In das Ventilgehäuse 12 ist an der Magnetkernstirnfläche 31 weiterhin ein Federraum 28 eingebracht, in dem eine Druckfeder 29 angeordnet ist, die in Öffnungsrichtung auf den Magentanker 33 einwirkt.The magnetic core 30 has, facing the armature plate 34, a magnetic core end face 31, which is also called a pole face. An armature surface 36 is formed on the armature plate 34, wherein the armature surface 36 forms the underside or the lower front side of the armature plate 34. Between the magnetic core 30 and the anchor plate 34, a residual air gap disc 50 is arranged. In the valve housing 12, a spring chamber 28 is further introduced to the magnetic core end face 31, in which a compression spring 29 is arranged, which acts in the opening direction on the magenta tank 33.

In der anschlussseitigen Aufnahme 15 ist ein Abschlussdeckel 40 hydraulisch dicht eingesetzt. Der Abschlussdeckel 40 umgibt die Ankerplatte 34 des Magnetankers 33 und bildet um die Ankerplatte 34 herum einen Ankerraum 44 aus. Im Ankerraum 44 ist die Ankerplatte 34 axial bewegbar angeordnet.In the connection-side receptacle 15 a cover 40 is used hydraulically tight. The end cover 40 surrounds the armature plate 34 of the armature 33 and forms around the armature plate 34 around an armature space 44 from. In the armature space 44, the anchor plate 34 is arranged axially movable.

Die Magnetspule 30 ist zur elektrischen Kontaktierung mit einem ersten formstabilen Kontaktierstift 41a und einem zweiten formstabilen Kontaktierstift 41b ausgeführt, die im Wesentlichen senkrecht aus der Magnetkernstirnfläche 34 herausführen und jeweils von einer Isolierhülse 42a, 42b umgeben sind.The magnetic coil 30 is for electrical contacting with a first dimensionally stable Kontaktierstift 41 a and a second dimensionally stable Kontaktierstift 41b carried out, which lead out substantially perpendicularly from the magnetic core end face 34 and are each surrounded by an insulating sleeve 42a, 42b.

Die Ankerplatte 32 weist zur Weiterführung des ersten Kontaktierstifts 41a eine erste Durchführung 43a und zur Weiterführung des zweiten Kontaktierstifts 41b eine zweite Durchführung 43b auf. Die Durchführungen 43a, 43b sind so ausgeführt, dass zwischen den Isolierhülsen 42a und 42b und den Durchführungen 43a, 43b jeweils ein Spalt 45a, 45b ausgebildet ist. Auf die Funktion des Spaltes 45a, 45b wird später eingegangen. Die Kontaktierstifte 41a, 41b sind mittels der Isolierhülsen 42a, 42b in ein über dem Abschlussdeckel 40 angeordnetes, elektrisch isolierendes Umspritzung 46 geführt, wo die Kontaktierstifte 41a, 41b elektrisch kontaktiert werden. Zur dichten Aufnahme der Kontaktstifte 41a, 41b sind diese an den Stirnseiten der Isolierhülsen 42a, 42b jeweils mit einem O-Ring 47 im Abschlussdeckel 40 umschlossen.The armature plate 32 has a first passage 43a for the continuation of the first contact pin 41a and a second passage 43b for the continuation of the second contact pin 41b. The passages 43a, 43b are designed such that a gap 45a, 45b is formed between the insulating sleeves 42a and 42b and the passages 43a, 43b. The function of the gap 45a, 45b will be discussed later. The contacting pins 41a, 41b are guided by means of the insulating sleeves 42a, 42b into an electrically insulating encapsulation 46 arranged above the end cap 40, where the contacting pins 41a, 41b are electrically contacted. For tight reception of the contact pins 41a, 41b, these are enclosed on the end faces of the insulating sleeves 42a, 42b each with an O-ring 47 in the end cover 40.

Zur Ausbildung eines druckausgeglichenen Druckregelventils sind der Ventilraum 23 und der Ankerraum 44 über einen Druckausgleichskanal 60 miteinander hydraulisch verbunden. Der Druckausgleichskanal 60 mündet dabei an der Magnetkernstirnfläche 31 mit einer Öffnung 61 in den Ankerraum 44.To form a pressure-balanced pressure control valve, the valve space 23 and the armature space 44 are hydraulically connected to each other via a pressure equalization channel 60. The pressure equalization channel 60 opens at the magnetic core end face 31 with an opening 61 into the armature space 44.

Damit der Druckausgleich im Ankerraum 44 sowohl an der Unterseite der Ankerplatte 43 als auch an der Oberseite der Ankerplatte 34 wirkt, werden die an der Ankerplatte 34 ausgebildeten Spalte 45a, 45b zwischen den Isolierhülsen 42a und 42b und den Durchführungen 43a, 43b als Durchlass zum Durchströmen von Kraftstoff für den Druckausgleich genutzt. Zur Vergrößerung des Strömungsquerschnitts für den Durchlass kann dabei mindestens die in der Nähe der Öffnung 61 liegende Durchführungen 43b einen größeren Durchmesser oder eine Aufweitung aufweisen.In order for the pressure equalization in the armature space 44 to act both on the underside of the armature plate 43 and on the upper side of the armature plate 34, the gaps 45a, 45b formed on the armature plate 34 pass between the insulating sleeves 42a and 42b and the passages 43a, 43b as a passage used by fuel for pressure equalization. In order to increase the flow cross section for the passage, at least the passages 43b located in the vicinity of the opening 61 may have a larger diameter or a widening.

Korrespondierend zu den Durchführungen 43a, 43b in der Ankerplatte 44 weist gemäß Figur 2 und 3 die zwischen dem Magnetkern 30 und der Ankerplatte 43 angeordnete Restluftspaltscheibe 50 weitere Durchführungen 53a, 53b zur Durchführung der Isolierhülsen 42a, 42b auf. Zur Strömungsoptimierung ist an einer der beiden weiteren Durchführung 53b, die in der Nähe der Öffnung 61 liegt, eine sich in Richtung der Öffnung 61 erstreckende radiale Erweiterung 54 ausgebildet. Die radiale Erweiterung 54 hat dadurch in der radialen Ebene liegend eine langlochförmige Form, der die Öffnung 61 überdeckt, so dass die Öffnung 61 in die Erweiterung 54 mündet. Dadurch bildet sich von der Öffnung 61 bis zum Spalt 45a an der Durchführung 43b, der im Wesentlichen den Durchlass für den Kraftstoff bildet, ein quer verlaufender Strömungskanal 56 aus, der eine hydraulische Verbindung zwischen der Öffnung 61 und dem Spalt 45b gewährleistet. Es ist dabei nicht notwendig, dass die radiale Erweiterung 54 bis zum Federraumraum 28 reicht.Corresponding to the bushings 43a, 43b in the anchor plate 44 has according to FIGS. 2 and 3 the arranged between the magnetic core 30 and the armature plate 43 residual air gap disc 50 further passages 53a, 53b for the implementation of the insulating sleeves 42a, 42b. For flow optimization, a radial extension 54 extending in the direction of the opening 61 is provided on one of the two further passages 53b, which lies in the vicinity of the opening 61 educated. The radial extension 54 thereby has lying in the radial plane of a slot-like shape, which covers the opening 61, so that the opening 61 opens into the extension 54. As a result, from the opening 61 to the gap 45a on the passage 43b, which essentially forms the passage for the fuel, a transverse flow channel 56 is formed, which ensures a hydraulic connection between the opening 61 and the gap 45b. It is not necessary that the radial extension 54 extends to the spring chamber space 28.

Eine möglichst kurze radiale Ausdehnung des Strömungskanals 56 wird erzielt, wenn die Öffnung 61 des Druckausgleichskanals 60 in der Nähe einer der Durchführungen 43b anzuordnen. Am einfachsten wird die Position dadurch gewählt, indem die Öffnung 61 gemäß Figur 2 und 3 fluchtend auf einer Linie 48 liegt, die das Zentrum der Restluftspaltscheibe 50 und das Zentrum der weiteren Durchführung 53b schneidet. Die Nähe der Öffnung 61 zur Isolierhülse 42a, 42b ist jedoch begrenzt, weil der Druckausgleichskanal 60 nicht durch eine ringförmige Magnetspulenaufnahme 38 geführt werden kann, in der die Magnetspule 32 mit einer Isoliermasse eingegossen ist.The shortest possible radial extent of the flow channel 56 is achieved if the opening 61 of the pressure compensation channel 60 to be arranged in the vicinity of one of the passages 43 b. The easiest way to choose the position is by the opening 61 in accordance with FIGS. 2 and 3 is aligned on a line 48 which intersects the center of the residual air gap disc 50 and the center of the further passage 53b. The proximity of the opening 61 to the insulating sleeve 42a, 42b is limited, however, because the pressure equalizing channel 60 can not be passed through an annular magnetic coil receptacle 38 in which the magnetic coil 32 is molded with an insulating compound.

Bei der Ausführungsform gemäß Figur 2 wird die Erweiterung 54 von einer Langlochform mit einer gleichbleibenden Breite gebildet, wobei die Breite des Langlochs vom Durchmesser der weiteren Durchführung 53b gebildet wird.In the embodiment according to FIG. 2 The extension 54 is formed by a slot shape with a constant width, wherein the width of the slot is formed by the diameter of the further passage 53b.

Bei der Ausführungsform in Figur 3 wird die Erweiterung 54 von einer Langlochform mit einer zur Öffnung 61 hin abnehmenden Breite gebildet, die sich vom Durchmesser der weiteren Durchführung 53b bis zur Öffnung 61 hin im Wesentlichen auf den Durchmesser der Öffnung 61 verjüngt.In the embodiment in FIG. 3 the extension 54 is formed by a slot shape with a decreasing width to the opening 61, which tapers from the diameter of the further passage 53b to the opening 61 substantially to the diameter of the opening 61.

Claims (6)

  1. Pressure regulating valve for a high-pressure accumulator (22), in particular for an injection device of an internal combustion engine, having a magnetic actuator (10) which has a magnet core (30) with contact pins (41a, 41b) and a magnet armature (33) with an armature plate (34), wherein the contact pins (41a, 41b) project out of a magnet core face surface (31) and extend through leadthroughs (43a, 43b) formed in the armature plate (34), wherein the armature plate (34) is arranged movably in an armature chamber (44) which is hydraulically connected via a pressure equalization duct (60) to a valve chamber (23) which is connected to low pressure, wherein the pressure equalization duct (60) has, on the magnet core face surface (31), an opening (61) via which the pressure equalization duct (60) issues into the armature chamber (44), wherein a passage for the fuel is provided, for pressure equalization, from one face side of the armature plate (34) to the other face side of the armature plate (34), said passage being formed by at least one of the leadthroughs (43a, 43b) in the armature plate (34), and wherein a residual air gap disk (50) is arranged between the magnet core (30) and armature plate (43), said residual air gap disk (50) having further leadthroughs (53a, 53b), which correspond to the leadthroughs (43a, 43b), for the contact pins (41a, 41b), characterized in that that further leadthrough (53b) in the residual air gap disk (50) which is situated in the vicinity of the opening (61) has a radial extension (54) extending in the direction of the opening (61).
  2. Pressure regulating valve according to Claim 1, characterized in that the radial extension (54) forms a flow duct (56) which extends substantially from the opening (61) to the leadthrough (43b) formed on the armature plate (34).
  3. Pressure regulating valve according to Claim 1 or 2, characterized in that the radial extension (54) covers the opening (61), such that the opening (61) issues into the extension (54).
  4. Pressure regulating valve according to Claim 3, characterized in that the radial extension (54) has a slot-shaped form with a substantially uniform width, wherein the width of the slot form is formed by the diameter of the further leadthrough (53b).
  5. Pressure regulating valve according to Claim 3, characterized in that the radial extension (54) has a slot-shaped form with a decreasing width, wherein, in the direction of the opening (61), the width decreases from the diameter of the further leadthrough (53b) to at least approximately the diameter of the opening (61).
  6. Pressure regulating valve according to one of Claims 1 to 5, characterized in that the opening (61) lies on a line (48) which intersects the center of the residual air gap disk (50) and the center of the further leadthrough (53b).
EP13721721.2A 2012-06-08 2013-05-07 Pressure control valve Not-in-force EP2859216B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1255351A FR2991727B1 (en) 2012-06-08 2012-06-08 HIGH PRESSURE FUEL ACCUMULATOR PRESSURE CONTROL VALVE
PCT/EP2013/059518 WO2013182366A1 (en) 2012-06-08 2013-05-07 Pressure control valve

Publications (2)

Publication Number Publication Date
EP2859216A1 EP2859216A1 (en) 2015-04-15
EP2859216B1 true EP2859216B1 (en) 2017-02-01

Family

ID=46963836

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13721721.2A Not-in-force EP2859216B1 (en) 2012-06-08 2013-05-07 Pressure control valve

Country Status (7)

Country Link
US (1) US9410522B2 (en)
EP (1) EP2859216B1 (en)
JP (1) JP5989955B2 (en)
CN (1) CN104334868B (en)
FR (1) FR2991727B1 (en)
IN (1) IN2014DN10005A (en)
WO (1) WO2013182366A1 (en)

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WO2023133034A1 (en) * 2022-01-05 2023-07-13 Cummins Inc. Fuel injector, needle seal, and fuel injector system

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Publication number Publication date
IN2014DN10005A (en) 2015-08-14
JP2015522742A (en) 2015-08-06
WO2013182366A1 (en) 2013-12-12
CN104334868B (en) 2017-03-22
FR2991727B1 (en) 2014-07-04
JP5989955B2 (en) 2016-09-07
FR2991727A1 (en) 2013-12-13
US9410522B2 (en) 2016-08-09
CN104334868A (en) 2015-02-04
EP2859216A1 (en) 2015-04-15
US20150152827A1 (en) 2015-06-04

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