EP2137400A1 - Pressure control valve - Google Patents

Pressure control valve

Info

Publication number
EP2137400A1
EP2137400A1 EP08717877A EP08717877A EP2137400A1 EP 2137400 A1 EP2137400 A1 EP 2137400A1 EP 08717877 A EP08717877 A EP 08717877A EP 08717877 A EP08717877 A EP 08717877A EP 2137400 A1 EP2137400 A1 EP 2137400A1
Authority
EP
European Patent Office
Prior art keywords
pressure
control valve
pressure control
housing
volume
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.)
Granted
Application number
EP08717877A
Other languages
German (de)
French (fr)
Other versions
EP2137400B1 (en
Inventor
Alois Moser
Johann Schardax
Peter Luckeneder
Andreas Poelzl
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 EP2137400A1 publication Critical patent/EP2137400A1/en
Application granted granted Critical
Publication of EP2137400B1 publication Critical patent/EP2137400B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—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
    • 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
    • F02M63/0019—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of electromagnets or fixed armatures
    • 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
    • F02M63/0021—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of mobile armatures
    • 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
    • F02M63/0012—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
    • 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

Definitions

  • the fuel injection system comprises a high-pressure storage space, which is acted upon by a high-pressure feed unit with high-pressure fuel and which supplies fuel injectors with fuel.
  • the high pressure pumping unit is associated with a pressure control valve which is arranged between a high pressure side and a low pressure side and comprises a valve element which can be controlled via an electric actuator.
  • 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 actuator arrangement can be set when the pressure regulating valve is mounted in a receiving body.
  • DE 102 22 895 A1 relates to a high-pressure accumulator for fuel injection systems with integrated pressure control valve.
  • the high-pressure storage space is supplied with high-pressure fuel via a high-pressure delivery unit and in turn supplies fuel injectors with fuel injectors.
  • the fuel injection system comprises a pressure regulating valve, which is arranged between a high-pressure side and a low-pressure side and via which a valve element can be actuated.
  • the pressure control valve is actuated by an electric actuator.
  • the pressure control valve delimits the low-pressure region at the high-pressure reservoir with one end face and is sealed off by a low-pressure-side seal.
  • Pressure control valves are used in a wide variety of applications and, as described above from DE 102 14 084 A1 and DE 102 22 895 A1, are used on fuel injection systems (common rail). These pressure control valves have points of discontinuity and instabilities in the pressure flow chart or in their control range. In particular, the return pressure also has a strong influence on the controllability or the achievable control quality of the pressure regulating valves known from the prior art. Disclosure of the invention
  • the present invention has for its object to provide an improved pressure control valve, which has a greater robustness to the occurrence of instability, in particular by the influence of constant or varying pressures on the low pressure side (return pressure, back pressure).
  • the stability of the pressure regulating valve is improved, in particular with increased backpressure, since, owing to the smaller volume, effective hydraulic forces are reduced which cause the instabilities in hitherto known pressure regulating valves known from the prior art.
  • the volume between the armature and the above-mentioned housing plan area filled with a non-magnetic material is thereby further increased.
  • the filling of the residual air gap between the armature and the above-mentioned housing plan surface of the pressure control valve, in particular of the magnetic coil receiving magnetic core for example, by applying or inserting a film.
  • a coating can also be applied both to the end face of the armature that points to the housing plan surface and to the housing plan surface itself.
  • the inventively proposed pressure control valve is distinguished from known from the prior art pressure control valves, as briefly outlined above, characterized in that on the one hand, the volume between the armature and housing plan surface is reduced, in which the discharged from the high pressure side medium drains and / or on the other hand this already reduced volume between magnet armature and housing plan surface is filled with a non-magnetic material.
  • FIG. 1 shows a pressure / flow characteristic diagram of a pressure regulating valve according to the prior art with an applied counter-pressure of approximately 5 bar
  • Figure 2 shows the pressure / flow characteristics of a pressure regulating valve proposed according to the invention at an applied back pressure between 5 and 6 bar and
  • FIG. 1 shows a pressure / flow characteristic diagram for a pressure regulating valve according to the prior art.
  • FIG. 1 shows a pressure / flow characteristic field 10 in which the pressure, i. H. the system pressure, which is applied to a high-pressure accumulator (common rail) of a high-pressure accumulator injection system, is plotted against the flow of the pressure regulating valve in l / h.
  • the pressure i. H. the system pressure
  • a high-pressure accumulator common rail
  • a high-pressure accumulator injection system for constant pressure control valve currents are different characteristic curves (pressure over flow) 12, each characterized by an area in which there is an instability 14.
  • the instability 14 is characterized in that, for a first operating point A and a second operating point B, a flow value is assigned a plurality of system pressure values, ie. H. an undefined state of the pressure control valve is present.
  • FIG. 2 shows a pressure / flow characteristic map 10, which is recorded for a pressure regulating valve proposed according to the invention.
  • characteristic curves 12 are also shown here, which however, in contrast to the instabilities 14 in the characteristic curves 12 according to FIG. 1, are characterized by continuous curves 16.
  • continuous curves 16 There is a continuous continuous course of the characteristic curves, so that with an applied back pressure of at least 5 bar a value for the system pressure p is essentially assigned a value for a corresponding flow in l / h.
  • FIG. 3 shows a section through the pressure regulating valve proposed according to the invention.
  • a pressure regulating valve 20 shown in section in FIG. 3 comprises a mounting element 74 with external thread secured to a housing 22, for example via a support ring 68.
  • this mounting element 74 which is fixed on the circumference of the housing 22 of the present invention proposed pressure control valve 20 via the support ring 68 in the axial direction, the pressure control valve 20 in a high-pressure accumulator body 72, which is shown only partially in the illustration of FIG 3, attached. Due to the screw connection between an internal thread in the high-pressure accumulator body 72 at the mounting location, a pressure-tight connection takes place between the pressure regulating valve 20 proposed according to the invention and the interior of the high-pressure accumulator body 72 (common rail). In this system pressures of up to 2000 bar and more prevail.
  • the system pressure p is maintained in the high-pressure storage body 72 by a high-pressure delivery unit (not shown in FIG. 3), such as a high-pressure pump, irrespective of the speed of an internal combustion engine to be supplied with fuel.
  • FIG. 3 shows that an electrical connection 24 for electrical contacting of the pressure regulating valve 20 proposed according to the invention is formed on the housing 22 of the pressure regulating valve 20 proposed according to the invention.
  • proposed pressure control valve 20 is an insert 26. This insert limits the stroke of an anchor plate 34 of an armature assembly 32, which further comprises an anchor bolt 50 extending through an anchor bolt bore 52 of the housing 22 of the present invention proposed pressure control valve 20th extends.
  • the insert 26 is sealed by a first seal 28 against the housing 22 of the present invention proposed pressure control valve 20.
  • the armature plate 34 accommodated on the anchor bolt 50 of the armature assembly 32 has a plan side 36 which assigns an end face 38 of the housing 22 of the pressure control valve 20.
  • the plan side 36 of the armature plate 34 of the armature assembly 32 is acted upon by a compression spring 30 which is received in a bore of the end face 38 of the housing 22 of the pressure control valve 20.
  • a magnetic coil 46 In the housing 22 of the pressure control valve 20 is further a magnetic coil 46, the of an embedding 44 enclosed in the housing 22 of the pressure control valve 20 is embedded.
  • This reduced volume 40 represents a Abgresraum in which the volume discharged from the high-pressure region of the high-pressure accumulator body 72 when opening a valve element 54 occurs and this reduced volume 40 accordingly fills.
  • a reduction of this volume between the armature assembly 32 and the end face 38 of the housing 22 and its filling with the high-pressure side controlled medium medium is possible to enter this volume, but due to the reduced volume 40 and due to the thereby reduced hydraulic Forces to a better stability of the pressure control valve 20, especially at elevated counter pressures leads.
  • the filling of the previously existing air gap between the plan side 36 of the armature plate 34 and the end face 38 of the housing 22 by an a- magnetic material can be achieved by either the plan side 36 of the Anchor plate 34 or the end face 38 of the housing 22, a film or a coating is applied. This coating or film can be applied on the flat side 36 of the anchor plate 34 and / or on the end face 38 of the housing 22.
  • the remaining residual air gap on the closed pressure control valve 20 can thereby assume an extremely low value.
  • the anchor bolt 50 of the armature assembly 32 extends through the armature bolt bore 52 in the housing 22 of the pressure control valve 20 proposed according to the invention.
  • the tip of the armature bolt 52 facing the high-pressure storage body 72 is conical and actuates a valve element 54 which is designed as a ball in the embodiment of the present invention proposed pressure control valve 20 shown in Figure 3.
  • the valve element 54 is placed in its seat 56, which is formed in a seat ring 58.
  • the seat ring 58 is embodied at the end of the housing 22 of the pressure regulating valve 20 proposed according to the invention, which faces the cavity, ie the area of the high-pressure accumulator 52 acted upon by the system pressure p.
  • a channel 60 extends, via which flows from the cavity of the high-pressure accumulator body (common rail) fuel via a filter 62.
  • the high-pressure accumulator body 72 is relieved of pressure when a certain maximum pressure is exceeded, for example during pressure pulsations via the pressure regulating valve 20 according to the sectional illustration in FIG.
  • the valve element 74 is open via the channel 60, the seat 56, the fuel volume diverted in the discharge lines 70 is returned to the tank of the high-pressure storage injection system via a low-pressure return.
  • the return can not be returned directly into the tank, but are fed back to a possibly provided in fuel injection systems prefeed pump, which generates higher back pressures.
  • a disk 64 can be arranged upstream to compensate for manufacturing tolerances. Furthermore, located on the missionsfikiee of the housing 22 of the pressure control valve 20 between the Ab Kunststofftechnisch 70 and the support ring 68 for fixing the mounting member 74, a second seal further.
  • the greater robustness and the avoidance of points of discontinuity and instabilities 14 in the characteristic curve 12 are achieved by the volume previously present at pressure regulating valves 20 between the plane side 36 of the anchor plate 34 of the end face 38 of the housing 22 through the FM volume 42, which is preferably represented by an amagnetic material is reduced. Due to the reduced volume 40, which is then still filled by the diverted medium, a significant reduction of the hydraulic forces, which would otherwise be effective in the volume between the armature plate 34 of the end face 38 of the housing 22. would be achievable, which in turn favors the precision of actuation of the armature assembly 32.
  • the non-magnetic gap 48 which determines the pressure-current characteristic of the pressure regulating valve 20 proposed according to the invention, despite small air gap, the remaining reduced volume 40 between the flat side 36 of the armature plate 34 and the end face 38 of the housing 22 of the pressure control valve 20 filled with the filling volume 42 of non-magnetic material.
  • This filling volume 42 can be realized either in the form of a coating or in the form of the introduction of a film or the like.
  • the measure of the formation of a reduced volume 40 can be taken together with the introduction of a filling volume 42 between the planar side 36 of the anchor plate and the end face 38 of the housing 22, or it can only a reduction of the volume 40 are performed, as well as an introduction of the Filling volume 42 between the plan side 36 of the anchor plate and the end face 38 of the housing 22.
  • the compression spring 30 and the spring which acts on the anchor plate 34 only one of these two springs may be present That is, either only the compression spring 30 or only the armature plate 34 acting on its back, inserted into the insert 26 spring. In Fig. 3 both possible mounting positions are shown.
  • the measures proposed according to the invention the reduction of the volume 40 and the introduction of the filling volume 42 of non-magnetic material can be implemented individually or in combination with solenoid valves which are used to actuate fuel injectors on fuel injection systems, such as high-pressure accumulator injection systems (common-rail systems). Rail) are used.
  • solenoid valves which are used to actuate fuel injectors on fuel injection systems, such as high-pressure accumulator injection systems (common-rail systems). Rail) are used.

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)

Abstract

The invention relates to a pressure control valve (20), particularly for a high-pressure accumulator body (72) of a fuel injection system. The pressure control valve (20) comprises a housing (22), an armature assembly (32) having an armature plate (34) and an armature pin (50). The armature plate (34) and a face (38) of the housing (22) delimit a volume (40) that can be filled with medium taken from the high-pressure accumulator (72). The volume (40) is reduced by a fill volume (42).

Description

Beschreibung description
Titel DruckregelventilTitle Pressure control valve
Stand der TechnikState of the art
DE 102 14 084 Al bezieht sich auf ein einstellbares Druckregelventil für Kraftstoffeinspritzsysteme. Das Kraftstoffeinspritzsystem umfasst einen Hochdruckspeicherraum, der über ein Hochdruckförderaggregat mit unter hohem Druck stehendem Kraftstoff beauf- schlag ist und welcher Kraftstoffinjektoren mit Kraftstoff versorgt. Dem Hochdruckförderaggregat ist ein Druckregelventil zugeordnet, das zwischen einer Hochdruckseite und einer Niederdruckseite angeordnet ist und ein Ventilelement umfasst, welches über einen elektrischen Steller ansteuerbar ist. Das Druckregelventil umfasst eine Gehäusekomponente, die einen verformbaren Bereich enthält, über den bei Montage des Druckregelventils in einem Aufnahmekörper ein Spalt L zwischen Flächen einer elektrisch ansteuerbaren Stelleranordnung einstellbar ist.DE 102 14 084 A1 relates to an adjustable pressure regulating valve for fuel injection systems. The fuel injection system comprises a high-pressure storage space, which is acted upon by a high-pressure feed unit with high-pressure fuel and which supplies fuel injectors with fuel. The high pressure pumping unit is associated with a pressure control valve which is arranged between a high pressure side and a low pressure side and comprises a valve element which can be controlled via an electric actuator. 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 actuator arrangement can be set when the pressure regulating valve is mounted in a receiving body.
DE 102 22 895 Al bezieht sich auf einen Hochdruckspeicher für Kraftstoffeinspritzsysteme mit integriertem Druckregelventil. Der Hochdruckspeicherraum wird über ein Hochdruck- förderaggregat mit unter Hochdruck stehendem Kraftstoff beaufschlagt und versorgt seinerseits Kraftstoffinjektoren mit Kraftstoff. Das Kraftstoffeinspritzsystem umfasst ein Druckregelventil, welches zwischen einer Hochdruckseite und einer Niederdruckseite angeordnet und über welches ein Ventilelement betätigbar ist. Das Druckregelventil wird über einen elektrischen Steller betätigt. Das Druckregelventil begrenzt mit einer Stirnseite den Nieder- druckbereich am Hochdruckspeicherraum und ist über eine niederdruckseitige Abdichtung abgedichtet.DE 102 22 895 A1 relates to a high-pressure accumulator for fuel injection systems with integrated pressure control valve. The high-pressure storage space is supplied with high-pressure fuel via a high-pressure delivery unit and in turn supplies fuel injectors with fuel injectors. The fuel injection system comprises a pressure regulating valve, which is arranged between a high-pressure side and a low-pressure side and via which a valve element can be actuated. The pressure control valve is actuated by an electric actuator. The pressure control valve delimits the low-pressure region at the high-pressure reservoir with one end face and is sealed off by a low-pressure-side seal.
Druckregelventile kommen in den verschiedensten Anwendungen zum Einsatz und werden, wie oben aus DE 102 14 084 Al und DE 102 22 895 Al geschildert, an Kraftstoffeinspritz- Systemen (Common-Rail) eingesetzt. Diese Druckregelventile weisen im Druck- Durchflusskennfeld bzw. in ihrem Regelbereich Unstetigkeitsstellen und Instabilitäten auf. Insbesondere nimmt auch der Rücklaufdruck einen starken Einfluss auf die Regelbarkeit bzw. die erzielbare Regelgüte der aus dem Stand der Technik bekannten Druckregelventile. Offenbarung der ErfindungPressure control valves are used in a wide variety of applications and, as described above from DE 102 14 084 A1 and DE 102 22 895 A1, are used on fuel injection systems (common rail). These pressure control valves have points of discontinuity and instabilities in the pressure flow chart or in their control range. In particular, the return pressure also has a strong influence on the controllability or the achievable control quality of the pressure regulating valves known from the prior art. Disclosure of the invention
Der vorliegenden Erfindung liegt die Aufgabe zugrunde, ein verbessertes Druckregelventil bereitzustellen, welches eine größere Robustheit gegenüber dem Auftreten von Instabilität insbesondere durch den Einfluss konstanter oder variierender Drücke auf der Niederdruckseite (Rücklaufdruck, Gegendruck) aufweist.The present invention has for its object to provide an improved pressure control valve, which has a greater robustness to the occurrence of instability, in particular by the influence of constant or varying pressures on the low pressure side (return pressure, back pressure).
Erfindungsgemäß wird vorgeschlagen, ein Volumen zwischen einem Magnetanker und einer Gehäuseplanfläche, welche sich mit dem von der Hochdruckseite abgesteuerten Medium, wie zum Beispiel Kraftstoff, füllt, zu verkleinern. Dadurch wird die Stabilität des Druckre- gelventiles insbesondere bei erhöhtem Gegendruck verbessert, da aufgrund des geringeren Volumens wirksame hydraulische Kräfte reduziert sind, die bei bisher eingesetzten aus dem Stand der Technik bekannten Druckregelventilen die Instabilitäten verursachen. Um das Volumen, welches die Druck- Stromkennlinie eines Druckregelventiles beeinflusst und in das abgesteuerte Menge eintritt und in welchem hydraulische Kräfte auftreten, zu verringern und trotz geringem Restluftspalt so wie bisher gestalten zu können, wird das Volumen zwischen dem Magnetanker und der oben stehend erwähnten Gehäuseplanfläche mit einem nicht-magnetischen Material aufgefüllt. Die Robustheit gegen das Auftreten von Instabilitä- ten wird dadurch weiter erhöht.According to the invention, it is proposed to reduce a volume between a magnet armature and a housing plan surface which fills with the medium which has been diverted from the high-pressure side, for example fuel. As a result, the stability of the pressure regulating valve is improved, in particular with increased backpressure, since, owing to the smaller volume, effective hydraulic forces are reduced which cause the instabilities in hitherto known pressure regulating valves known from the prior art. In order to reduce the volume, which affects the pressure-current characteristic of a pressure control valve and enters the diverted amount and in which hydraulic forces occur, and to be able to design as before despite a small residual air gap, the volume between the armature and the above-mentioned housing plan area filled with a non-magnetic material. The robustness against the occurrence of instabilities is thereby further increased.
Das Ausfüllen des Restluftspaltes zwischen dem Magnetanker und der oben stehend bereits erwähnten Gehäuseplanfläche des Druckregelventiles, insbesondere des die Magnetspule aufnehmenden Magnetkernes erfolgt zum Beispiel durch Aufbringen oder Einlegen einer Folie. Daneben kann auch eine Beschichtung sowohl auf der der Gehäuseplanfläche zuweisenden Stirnseite des Ankers als auch auf der Gehäuseplanfläche selbst aufgebracht werden. Der erfindungsgemäß vorgeschlagenen Lösung folgend wird eine Entkopplung zwischen dem Volumen um die Ankerplatte der Ankerbaugruppe des Druckregelventiles und dem Volumen, in dem das Medium, wie zum Beispiel unter Systemdruck stehender Kraftstoff, aus dem Hochdruckbereich abgesteuert wird, hergestellt.The filling of the residual air gap between the armature and the above-mentioned housing plan surface of the pressure control valve, in particular of the magnetic coil receiving magnetic core, for example, by applying or inserting a film. In addition, a coating can also be applied both to the end face of the armature that points to the housing plan surface and to the housing plan surface itself. Following the solution proposed according to the invention, a decoupling between the volume around the armature plate of the armature assembly of the pressure control valve and the volume in which the medium, for example fuel under system pressure, is removed from the high-pressure region, is produced.
Das erfindungsgemäß vorgeschlagene Druckregelventil zeichnet sich gegenüber aus dem Stand der Technik bekannten Druckregelventilen, wie oben stehend kurz skizziert, dadurch aus, dass einerseits das Volumen zwischen Magnetanker und Gehäuseplanfläche verkleinert ist, in das das von der Hochdruckseite her abgesteuerte Medium abströmt und/oder andererseits dieses bereits verkleinerte Volumen zwischen Magnetanker und Gehäuseplanfläche mit einem nicht-magnetischen Material verfüllt ist. Dies bedeutet, dass im Idealfall das ver- kleinerte Volumen zwischen Gehäuseplanfläche und Planseite des Magnetankers bei geschlossenem Ventil zu Null wird, so dass Instabilitäten erheblich reduziert werden können.The inventively proposed pressure control valve is distinguished from known from the prior art pressure control valves, as briefly outlined above, characterized in that on the one hand, the volume between the armature and housing plan surface is reduced, in which the discharged from the high pressure side medium drains and / or on the other hand this already reduced volume between magnet armature and housing plan surface is filled with a non-magnetic material. This means that in the ideal case the reduced volume between housing plan face and plan side of the armature with the valve closed to zero, so that instabilities can be significantly reduced.
Kurze Beschreibung der ZeichnungenBrief description of the drawings
Anhand der Zeichnungen wird die Erfindung nachstehend eingehender beschrieben.With reference to the drawings, the invention will be described in more detail below.
Es zeigt:It shows:
Figur 1 ein Druck-/Durchflusskennfeld eines Druckregelventils gemäß dem Stand der Technik bei einem anliegenden Gegendruck von etwa 5 bar,FIG. 1 shows a pressure / flow characteristic diagram of a pressure regulating valve according to the prior art with an applied counter-pressure of approximately 5 bar,
Figur 2 das Druck-/Durchflusskennfeld eines erfindungsgemäß vorgeschlagenen Druckregelventils bei einem anliegenden Gegendruck zwischen 5 und 6 bar undFigure 2 shows the pressure / flow characteristics of a pressure regulating valve proposed according to the invention at an applied back pressure between 5 and 6 bar and
Figur 3 einen Schnitt durch das erfindungsgemäß vorgeschlagene Druckregelventil.3 shows a section through the inventively proposed pressure control valve.
Figur 1 zeigt ein Druck-/Durchflusskennfeld für ein Druckregelventil gemäß dem Stand der Technik.FIG. 1 shows a pressure / flow characteristic diagram for a pressure regulating valve according to the prior art.
Aus der Darstellung gemäß Figur 1 geht ein Druck-/Durchflusskennfeld 10 hervor, in dem der Druck, d. h. der Systemdruck, mit welchem ein Hochdruckspeicher (Common-Rail) eines Hochdruckspeichereinspritzsystems beaufschlagt ist, über dem Durchfluss des Druckregelventiles in l/h aufgetragen ist. Für konstante Druckregelventilströme stellen sich unterschiedliche Kennlinienverläufe (Druck über Durchfluss) 12 ein, die jeweils durch einen Bereich gekennzeichnet sind, in dem eine Instabilität 14 vorliegt. Die Instabilität 14 ist dadurch charakterisiert, dass für einen ersten Betriebspunkt A sowie einen zweiten Betriebspunkt B einem Durchflusswert mehrere Systemdruckwerte zugeordnet sind, d. h. ein Undefinierter Zustand des Druckregelventiles vorliegt.The illustration according to FIG. 1 shows a pressure / flow characteristic field 10 in which the pressure, i. H. the system pressure, which is applied to a high-pressure accumulator (common rail) of a high-pressure accumulator injection system, is plotted against the flow of the pressure regulating valve in l / h. For constant pressure control valve currents are different characteristic curves (pressure over flow) 12, each characterized by an area in which there is an instability 14. The instability 14 is characterized in that, for a first operating point A and a second operating point B, a flow value is assigned a plurality of system pressure values, ie. H. an undefined state of the pressure control valve is present.
Ausführungsformenembodiments
Der Darstellung gemäß Figur 2 ist ein Druck-/Durchflusskennfeld 10 zu entnehmen, welches für ein erfindungsgemäß vorgeschlagenes Druckregelventil aufgenommen ist. Analog zur Darstellung gemäß Figur 1 sind auch hier Kennlinienverläufe 12 dargestellt, die sich jedoch im Gegensatz zu den Instabilitäten 14 in den Kennlinienverläufen 12 gemäß Figur 1 durch stetige Verläufe 16 auszeichnen. Es existiert ein kontinuierlicher stetiger Verlauf der Kennlinien, so dass bei einem anliegenden Gegendruck von mindestens 5 bar einem Wert für den Systemdruck p im Wesentlichen ein Wert für einen entsprechenden Durchfluss in l/h zugeordnet wird. Dies bedeutet, dass die Durchflussmenge für jeden Systemdruck entsprechend den Kennlinienverläufen 12 exakt definiert ist, d. h. das erfindungsgemäß vorgeschlagene Druckregelventil wesentlich stabiler zu stellen ist als das aus dem Stand der Technik bekannte Druckregelventil, dessen Instabilitäten auf den Kennlinienverläufen 12 aus Figur 1 hervorgehen.The illustration according to FIG. 2 shows a pressure / flow characteristic map 10, which is recorded for a pressure regulating valve proposed according to the invention. Analogous to the representation according to FIG. 1, characteristic curves 12 are also shown here, which however, in contrast to the instabilities 14 in the characteristic curves 12 according to FIG. 1, are characterized by continuous curves 16. There is a continuous continuous course of the characteristic curves, so that with an applied back pressure of at least 5 bar a value for the system pressure p is essentially assigned a value for a corresponding flow in l / h. This means that the flow rate for each system pressure corresponding to the characteristic curves 12 is exactly defined, ie the pressure control valve proposed by the invention is much more stable to set than the known from the prior art pressure control valve, the instabilities of the characteristic curves 12 of Figure 1 emerge.
Figur 3 zeigt einen Schnitt durch das erfindungsgemäß vorgeschlagene Druckregelventil.FIG. 3 shows a section through the pressure regulating valve proposed according to the invention.
Ein in Figur 3 im Schnitt dargestelltes Druckregelventil 20 umfasst ein an einem Gehäuse 22 zum Beispiel über einen Abstützring 68 gesichertes Montageelement 74 mit Außengewinde. Mittels dieses Montageelementes 74, welches am Umfang des Gehäuses 22 des erfindungsgemäß vorgeschlagenen Druckregelventiles 20 über den Abstützring 68 in axialer Richtung fixiert ist, wird das Druckregelventil 20 in einem Hochdruckspeicherkörper 72, der in der Darstellung gemäß Figur 3 nur teilweise dargestellt ist, befestigt. Aufgrund der Verschrau- bung zwischen einem Innengewinde im Hochdruckspeicherkörper 72 an der Montagestelle erfolgt eine druckdichte Verbindung zwischen dem erfindungsgemäß vorgeschlagenen Druckregelventil 20 und dem Inneren des Hochdruckspeicherkörpers 72 (Common-Rail). In diesem herrschen Systemdrücke von bis zu 2000 bar und mehr. Der Systemdruck p wird im Hochdruckspeicherkörper 72 durch ein in Figur 3 nicht dargestelltes Hochdruckförderaggregat, wie zum Beispiel über eine Hochdruckpumpe, unabhängig von der Drehzahl einer mit Kraftstoff zu versorgenden Verbrennungskraftmaschine aufrechterhalten.A pressure regulating valve 20 shown in section in FIG. 3 comprises a mounting element 74 with external thread secured to a housing 22, for example via a support ring 68. By means of this mounting element 74, which is fixed on the circumference of the housing 22 of the present invention proposed pressure control valve 20 via the support ring 68 in the axial direction, the pressure control valve 20 in a high-pressure accumulator body 72, which is shown only partially in the illustration of FIG 3, attached. Due to the screw connection between an internal thread in the high-pressure accumulator body 72 at the mounting location, a pressure-tight connection takes place between the pressure regulating valve 20 proposed according to the invention and the interior of the high-pressure accumulator body 72 (common rail). In this system pressures of up to 2000 bar and more prevail. The system pressure p is maintained in the high-pressure storage body 72 by a high-pressure delivery unit (not shown in FIG. 3), such as a high-pressure pump, irrespective of the speed of an internal combustion engine to be supplied with fuel.
Aus Figur 3 geht hervor, dass am Gehäuse 22 des erfindungsgemäß vorgeschlagenen Druckregelventiles 20 ein elektrischer Anschluss 24 zur elektrischen Kontaktierung des erfindungsgemäß vorgeschlagenen Druckregelventiles 20 ausgebildet ist. Im Gehäuse 22 des erfindungsgemäß vorgeschlagenen Druckregelventiles 20 befindet sich ein Einsatz 26. Dieser Einsatz begrenzt den Hub einer Ankerplatte 34 einer Ankerbaugruppe 32, die des Weiteren einen Ankerbolzen 50 umfasst, der sich durch eine Ankerbolzenbohrung 52 des Ge- häuses 22 des erfindungsgemäß vorgeschlagenen Druckregelventiles 20 erstreckt.FIG. 3 shows that an electrical connection 24 for electrical contacting of the pressure regulating valve 20 proposed according to the invention is formed on the housing 22 of the pressure regulating valve 20 proposed according to the invention. In the housing 22 of the present invention proposed pressure control valve 20 is an insert 26. This insert limits the stroke of an anchor plate 34 of an armature assembly 32, which further comprises an anchor bolt 50 extending through an anchor bolt bore 52 of the housing 22 of the present invention proposed pressure control valve 20th extends.
Der Einsatz 26 ist über eine erste Dichtung 28 gegen das Gehäuse 22 des erfindungsgemäß vorgeschlagenen Druckregelventiles 20 abgedichtet. Die am Ankerbolzen 50 der Ankerbaugruppe 32 aufgenommene Ankerplatte 34 weist eine Planseite 36 auf, die einer Stirnseite 38 des Gehäuses 22 des Druckregelventiles 20 zuweist. Die Planseite 36 der Ankerplatte 34 der Ankerbaugruppe 32 ist durch eine Druckfeder 30 beaufschlagt, die in einer Bohrung der in der Stirnseite 38 des Gehäuses 22 des Druckregelventiles 20 aufgenommen ist. Im Gehäuse 22 des Druckregelventiles 20 befindet sich des weiteren eine Magnetspule 46, die von einer Einbettung 44 umschlossen, in das Gehäuse 22 des Druckregelventiles 20 eingebettet ist. Das in Figur 3 im Schnitt dargestellte Druckregelventil zeichnet sich dadurch aus, dass es sich bei einem Volumen, welches einerseits durch die Planseite 36 der Ankerplatte 34 und andererseits durch die Stirnseite 38 des Gehäuses 22 begrenzt ist, um ein verringertes Vo- lumen 40 handelt. Dieses verringerte Volumen 40 stellt einen Absteuerraum dar, in dem das aus dem Hochdruckbereich des Hochdruckspeicherkörpers 72 bei Öffnen eines Ventilelementes 54 abgesteuerte Volumen eintritt und dieses verringerte Volumen 40 demzufolge befüllt. Durch eine Verkleinerung dieses Volumens zwischen der Ankerbaugruppe 32 und der Stirnseite 38 des Gehäuses 22 und dessen Befüllung mit dem von der Hochdruckseite abgesteuerten Medium ist zwar ein Eintritt von Medium in dieses Volumen möglich, was jedoch aufgrund des verringerten Volumens 40 und aufgrund der dadurch verringerten hydraulischen Kräfte zu einer besseren Stabilität des Druckregelventiles 20, insbesondere bei erhöhten Gegendrücken, führt. Dies geht aus den jeweils stetige Verläufen 16 aufweisenden Kennlinien 12 des Druck-/Durchflusskennfeldes 10 gemäß Figur 2 besonders deutlich her- vor. Um einen nicht-magnetischen Spalt 48, welcher die Druck- Stromkennlinie des erfindungsgemäß vorgeschlagenen Druckregelventiles 20 bestimmt, trotz sehr geringem Luftspalt, hinreichend groß gestalten zu können, wird das verringerte Volumen 40 zwischen der Ankerplatte 34 und der Stirnseite 38 des Gehäuses 22 mit einem Füllvolumen 42 bevorzugt aus einem nicht-magnetischen Material aufgefüllt. Dadurch wird eine weitere Steigerung der Robustheit gegen das Auftreten von Instabilitäten 14 - wie anhand der Kennlinienverläufe 12 gemäß Figur 1 gezeigt - erreicht. Bei geschlossenem Druckregelventil 20 bleibt im Idealfall kein Luftspalt, der gesamte nicht-magnetische Spalt 48 wird durch nicht-magnetisches Material, d. h. das Füllvolumen 42, ausgefüllt. In der Praxis verbleibt jedoch aufgrund von Fertigungstoleranzen auch im geschlossenen Zustand des Druckregelventiles 20 ein kleiner Luftspalt, der jedoch im Vergleich zu dem Luftspalt, der bei Druckregelventilen gemäß des Standes der Technik das Volumen bildet, welches durch den abgesteuerten Kraftstoff ausgefüllt ist, erheblich reduziert ist.The insert 26 is sealed by a first seal 28 against the housing 22 of the present invention proposed pressure control valve 20. The armature plate 34 accommodated on the anchor bolt 50 of the armature assembly 32 has a plan side 36 which assigns an end face 38 of the housing 22 of the pressure control valve 20. The plan side 36 of the armature plate 34 of the armature assembly 32 is acted upon by a compression spring 30 which is received in a bore of the end face 38 of the housing 22 of the pressure control valve 20. In the housing 22 of the pressure control valve 20 is further a magnetic coil 46, the of an embedding 44 enclosed in the housing 22 of the pressure control valve 20 is embedded. The pressure regulating valve shown in section in FIG. 3 is distinguished by the fact that, for a volume bounded on the one hand by the plane side 36 of the anchor plate 34 and on the other hand by the end face 38 of the housing 22, this is a reduced volume 40. This reduced volume 40 represents a Absteuerraum in which the volume discharged from the high-pressure region of the high-pressure accumulator body 72 when opening a valve element 54 occurs and this reduced volume 40 accordingly fills. Although a reduction of this volume between the armature assembly 32 and the end face 38 of the housing 22 and its filling with the high-pressure side controlled medium medium is possible to enter this volume, but due to the reduced volume 40 and due to the thereby reduced hydraulic Forces to a better stability of the pressure control valve 20, especially at elevated counter pressures leads. This is particularly clear from the respective continuous curves 16 having characteristic curves 12 of the pressure / flow characteristic map 10 according to FIG. In order to be able to design a non-magnetic gap 48, which determines the pressure-current characteristic of the inventively proposed pressure control valve 20, despite very small air gap, sufficiently large, the reduced volume 40 between the armature plate 34 and the end face 38 of the housing 22 with a filling volume 42 preferably filled from a non-magnetic material. As a result, a further increase in the robustness against the occurrence of instabilities 14 is achieved, as shown by the characteristic curves 12 according to FIG. When the pressure regulating valve 20 is closed, ideally no air gap remains; the entire non-magnetic gap 48 is filled by non-magnetic material, ie the filling volume 42. In practice, however, a small air gap remains due to manufacturing tolerances even in the closed state of the pressure control valve 20, which, however, compared to the air gap, which forms the volume, which is filled by the discarded fuel is significantly reduced in pressure control valves according to the prior art ,
Wie in Figur 3 angedeutet, kann das Ausfüllen des bisher vorhandenen Luftspaltes zwischen der Planseite 36 der Ankerplatte 34 und der Stirnseite 38 des Gehäuses 22 durch ein a- magnetisches Material, d. h. dem Füllvolumen 42, dadurch erreicht werden, dass entweder auf die Planseite 36 der Ankerplatte 34 oder die Stirnseite 38 des Gehäuses 22 eine Folie oder eine Beschichtung aufgebracht wird. Diese Beschichtung bzw. Folie kann auf der Planseite 36 der Ankerplatte 34 und/oder auf der Stirnseite 38 des Gehäuses 22 aufgebracht werden. Der verbleibende Restluftspalt am geschlossenen Druckregelventil 20 kann dadurch einen äußerst geringen Wert annehmen. Wie aus der Darstellung gemäß Figur 3 weiter hervorgeht, erstreckt sich der Ankerbolzen 50 der Ankerbaugruppe 32 durch die Ankerbolzenbohrung 52 im Gehäuse 22 des erfindungsgemäß vorgeschlagenen Druckregelventiles 20. Die dem Hochdruckspeicherkörper 72 zuweisende Spitze des Ankerbolzens 52 ist konisch ausgebildet und betätigt ein Ventilele- ment 54, welches in der in Figur 3 dargestellten Ausführungsform des erfindungsgemäß vorgeschlagenen Druckregelventiles 20 als Kugel ausgebildet ist. Über den Ankerbolzen 50 wird das in dieser Ausführungsform kugelförmig ausgebildete Ventilelement 54 in seinen Sitz 56 gestellt, der in einem Sitzring 58 ausgebildet ist. Der Sitzring 58 ist an dem Ende des Gehäuses 22 des erfindungsgemäß vorgeschlagenen Druckregelventiles 20 ausgeführt, wel- ches dem Hohlraum, d. h. dem mit Systemdruck p beaufschlagten Bereich des Hochdruckspeichers 52, gegenüberliegt. Durch den Sitzring 58 erstreckt sich ein Kanal 60, über den aus dem Hohlraum des Hochdruckspeicherkörpers (Common-Rail) Kraftstoff über ein Filtersieb 62 zuströmt. Je nachdem, welcher Systemdruck p im inneren des Hochdruckspeicherkörpers 72 herrscht, wird bei Überschreiten eines bestimmten Höchstdruckes, so zum Beispiel bei Druckpulsationen über das Druckregelventil 20 gemäß der Schnittdarstellung in Figur 3, der Hochdruckspeicherkörper 72 druckentlastet. Bei geöffnetem Ventilelement 74 über den Kanal 60, den Sitz 56, in Absteuerleitungen 70 abgesteuertes Kraftstoffvolumen wird über einen niederdruckseitigen Rücklauf wieder dem Tank des Hochdruckspeicherein- spritzsystems zugeführt. Bei anderen Ausführungsformen von Kraftstoffeinspritzsystemen kann der Rücklauf auch nicht direkt in den Tank zurückgeleitet werden, sondern nach einer in Kraftstoffeinspritzsystemen gegebenenfalls vorgesehenen Vorförderpumpe wieder eingespeist werden, welche höhere Gegendrücke erzeugt.As indicated in Figure 3, the filling of the previously existing air gap between the plan side 36 of the armature plate 34 and the end face 38 of the housing 22 by an a- magnetic material, ie the filling volume 42, can be achieved by either the plan side 36 of the Anchor plate 34 or the end face 38 of the housing 22, a film or a coating is applied. This coating or film can be applied on the flat side 36 of the anchor plate 34 and / or on the end face 38 of the housing 22. The remaining residual air gap on the closed pressure control valve 20 can thereby assume an extremely low value. 3, the anchor bolt 50 of the armature assembly 32 extends through the armature bolt bore 52 in the housing 22 of the pressure control valve 20 proposed according to the invention. The tip of the armature bolt 52 facing the high-pressure storage body 72 is conical and actuates a valve element 54 which is designed as a ball in the embodiment of the present invention proposed pressure control valve 20 shown in Figure 3. About the anchor bolt 50, the ball-shaped in this embodiment, the valve element 54 is placed in its seat 56, which is formed in a seat ring 58. The seat ring 58 is embodied at the end of the housing 22 of the pressure regulating valve 20 proposed according to the invention, which faces the cavity, ie the area of the high-pressure accumulator 52 acted upon by the system pressure p. Through the seat ring 58, a channel 60 extends, via which flows from the cavity of the high-pressure accumulator body (common rail) fuel via a filter 62. Depending on which system pressure p prevails in the interior of the high-pressure accumulator body 72, the high-pressure accumulator body 72 is relieved of pressure when a certain maximum pressure is exceeded, for example during pressure pulsations via the pressure regulating valve 20 according to the sectional illustration in FIG. When the valve element 74 is open via the channel 60, the seat 56, the fuel volume diverted in the discharge lines 70 is returned to the tank of the high-pressure storage injection system via a low-pressure return. In other embodiments of fuel injection systems, the return can not be returned directly into the tank, but are fed back to a possibly provided in fuel injection systems prefeed pump, which generates higher back pressures.
Aus der Darstellung gemäß Figur 3 geht des weiteren hervor, dass zwischen dem Sitzring 58, in dem der Sitz 56 für das hier kugelförmig ausgebildete Ventilelement 54 ausgebildet ist, eine Scheibe 64 vorgeschaltet sein kann, um Fertigungstoleranzen auszugleichen. Des weiteren befindet sich an der Umfangsfiäche des Gehäuses 22 des Druckregelventiles 20 zwischen der Absteuerleitung 70 und dem Abstützring 68 zur Fixierung des Montageelementes 74 eine weitere zweite Dichtung.From the illustration according to FIG. 3, it can also be seen that between the seat ring 58, in which the seat 56 is formed for the valve element 54 of spherical design here, a disk 64 can be arranged upstream to compensate for manufacturing tolerances. Furthermore, located on the Umfangsfiäche of the housing 22 of the pressure control valve 20 between the Absteuerleitung 70 and the support ring 68 for fixing the mounting member 74, a second seal further.
Bei dem erfindungsgemäß vorgeschlagenen Druckregelventil 20 wird die größere Robustheit und das Vermeiden von Unstetigkeitsstellen und Instabilitäten 14 im Kennlinienverlauf 12 dadurch erreicht, dass das bisher an Druckregelventilen 20 vorhandene Volumen zwischen der Planseite 36 der Ankerplatte 34 der Stirnseite 38 des Gehäuses 22 durch das FM- volumen 42, welches bevorzugt durch ein amagnetisches Material dargestellt wird, reduziert wird. Aufgrund des verringerten Volumens 40, welches dann noch durch das abgesteuerte Medium ausgefüllt wird, ist eine erhebliche Verringerung der hydraulischen Kräfte, die andernfalls im Volumen zwischen der Ankerplatte 34 der Stirnseite 38 des Gehäuses 22 wirk- sam werden würden erzielbar, was wiederum die Präzision der Betätigung der Ankerbau- gruppe 32 begünstigt. Um den nicht-magnetischen Spalt 48, welcher die Druck- Stromkennlinie des erfϊndungsgemäß vorgeschlagenen Druckregelventiles 20 bestimmt, trotz kleinem Luftspalt hinreichend groß gestalten zu können, wird das verbliebene verrin- gerte Volumen 40 zwischen der Planseite 36 der Ankerplatte 34 und der Stirnseite 38 des Gehäuses 22 des Druckregelventiles 20 mit dem Füllvolumen 42 aus amagnetischem Material aufgefüllt. Dieses Füllvolumen 42 kann entweder in Form einer Beschichtung oder in Form des Einbringens einer Folie oder dergleichen realisiert sein. Wenn das erfindungsgemäß vorgeschlagene Druckregelventil 20 geschlossen ist, besteht zwischen der Stirnseite 38 des Gehäuses 22 und der Planseite 36 der Ankerplatte 34 ein verbleibender nichtmagnetischer Spalt, der durch das Füllvolumen 42 so reduziert ist, dass hydraulische Kräfte nicht zu den in Zusammenhang mit Figur 1 dargestellten Instabilitäten 14 am Druckregelventil 20 führen können. Befindet sich das erfindungsgemäß vorgeschlagene Druckregelventil 20 gemäß Figur 3 in seiner offenen Position, so ist die Ankerbaugruppe 32 aus Ankerbol- zen 50 und Ankerplatte 34 in Öffnungsrichtung verschoben, so dass sich bei offenstehendem Druckregelventil 20 ein etwas vergrößertes Volumen zwischen der Planseite 36 der Ankerplatte 34 und der Stirnseite 38 des Gehäuses 22 des Druckregelventiles 20 ergibt. Dieses Volumen ist jedoch erheblich reduziert. Erfindungsgemäß kann die Maßnahme der Ausbildung eines verringerten Volumens 40 zusammen mit dem Einbringen eines Füllvolumens 42 zwischen die Planseite 36 der Ankerplatte und die Stirnseite 38 des Gehäuses 22 ergriffen werden, oder es kann lediglich eine Verringerung des Volumens 40 durchgeführt werden, wie auch ein Einbringen des Füllvolumens 42 zwischen die Planseite 36 der Ankerplatte und die Stirnseite 38 des Gehäuses 22. Anstelle der beiden in der Darstellung gemäß Figur 3 dargestellten Federn, der Druckfeder 30 und der Feder, die die Ankerplatte 34 beaufschlagt, kann auch lediglich eine dieser beiden Federn vorhanden sein, d.h. entweder nur die Druckfeder 30 oder nur die die Ankerplatte 34 an ihrer Rückseite beaufschlagende, in den Einsatz 26 eingelassene Feder. In der Fig. 3 sind beide möglichen Einbaupositionen wiedergegeben.In the pressure regulating valve 20 proposed according to the invention, the greater robustness and the avoidance of points of discontinuity and instabilities 14 in the characteristic curve 12 are achieved by the volume previously present at pressure regulating valves 20 between the plane side 36 of the anchor plate 34 of the end face 38 of the housing 22 through the FM volume 42, which is preferably represented by an amagnetic material is reduced. Due to the reduced volume 40, which is then still filled by the diverted medium, a significant reduction of the hydraulic forces, which would otherwise be effective in the volume between the armature plate 34 of the end face 38 of the housing 22. would be achievable, which in turn favors the precision of actuation of the armature assembly 32. In order to be able to design the non-magnetic gap 48, which determines the pressure-current characteristic of the pressure regulating valve 20 proposed according to the invention, despite small air gap, the remaining reduced volume 40 between the flat side 36 of the armature plate 34 and the end face 38 of the housing 22 of the pressure control valve 20 filled with the filling volume 42 of non-magnetic material. This filling volume 42 can be realized either in the form of a coating or in the form of the introduction of a film or the like. When the pressure regulating valve 20 proposed according to the invention is closed, there is a remaining non-magnetic gap between the end face 38 of the housing 22 and the plane side 36 of the anchor plate 34, which is reduced by the filling volume 42 such that hydraulic forces do not occur in relation to those shown in connection with FIG Instabilities 14 can lead to the pressure control valve 20. If the pressure regulating valve 20 proposed according to the invention is in its open position according to FIG. 3, the armature assembly 32 is displaced from the anchor bolt 50 and armature plate 34 in the opening direction, so that when the pressure regulating valve 20 is open, a somewhat larger volume exists between the flat side 36 of the armature plate 34 and the end face 38 of the housing 22 of the pressure control valve 20 results. However, this volume is significantly reduced. According to the invention, the measure of the formation of a reduced volume 40 can be taken together with the introduction of a filling volume 42 between the planar side 36 of the anchor plate and the end face 38 of the housing 22, or it can only a reduction of the volume 40 are performed, as well as an introduction of the Filling volume 42 between the plan side 36 of the anchor plate and the end face 38 of the housing 22. Instead of the two springs shown in the illustration of Figure 3, the compression spring 30 and the spring which acts on the anchor plate 34, only one of these two springs may be present That is, either only the compression spring 30 or only the armature plate 34 acting on its back, inserted into the insert 26 spring. In Fig. 3 both possible mounting positions are shown.
Die erfindungsgemäß vorgeschlagenen Maßnahmen, die Verringerung des Volumens 40 sowie das Einbringen des Füllvolumens 42 aus nicht-magnetischem Material können jede für sich oder kombiniert auch an Magnetventilen verwirklicht werden, die zur Betätigung von Kraftstoffinjektoren an Kraftstoffeinspritzsystemen, wie zum Beispiel Hochdruckspei- chereinspritzsystemen (Common-Rail) eingesetzt werden. The measures proposed according to the invention, the reduction of the volume 40 and the introduction of the filling volume 42 of non-magnetic material can be implemented individually or in combination with solenoid valves which are used to actuate fuel injectors on fuel injection systems, such as high-pressure accumulator injection systems (common-rail systems). Rail) are used.

Claims

Ansprüche claims
1. Druckregelventil (20), insbesondere für einen Hochdruckspeicherkörper (72) oder eine Hochdruckförderpumpe eines Kraftstoffeinspritzsystems, mit einem Gehäuse (22), einer Ankerbaugruppe (32), mit einer Ankerplatte (34) und einem Ankerbolzen (50), wobei die Ankerplatte (34) und eine Stirnseite (38) des Gehäuses (22) ein mit aus dem Hochdruckspeicherkörper (72) abgesteuertem Medium befüllbares Volumen (40) darstellen, dadurch gekennzeichnet, dass das Volumen (40) durch ein Füllvolumen (42) verringert ist.A pressure regulating valve (20), in particular for a high-pressure accumulator body (72) or a high-pressure pump of a fuel injection system, comprising a housing (22), an armature assembly (32), an armature plate (34) and an anchor bolt (50), the armature plate ( 34) and an end face (38) of the housing (22) constitute a volume (40) which can be filled with fluid from the high-pressure storage body (72), characterized in that the volume (40) is reduced by a filling volume (42).
2. Druckregelventil (20) gemäß Anspruch 1, dadurch gekennzeichnet, dass das Füllvolumen (42) ein amagnetisches Material ist.2. Pressure control valve (20) according to claim 1, characterized in that the filling volume (42) is an amagnetic material.
3. Druckregelventil (20) gemäß Anspruch 1, dadurch gekennzeichnet, dass das Füllvolu- men (42) zwischen eine Planseite (36) der Ankerplatte (34) und eine Stirnseite (38) des3. Pressure control valve (20) according to claim 1, characterized in that the Füllvolu- men (42) between a plane side (36) of the anchor plate (34) and an end face (38) of the
Gehäuses (22) eingebracht ist.Housing (22) is introduced.
4. Druckregelventil (20) gemäß Anspruch 2, dadurch gekennzeichnet, dass das Füllvolumen (42) als Folie oder als Beschichtung ausgebildet ist.4. Pressure control valve (20) according to claim 2, characterized in that the filling volume (42) is formed as a film or as a coating.
5. Druckregelventil (20) gemäß Anspruch 3, dadurch gekennzeichnet, dass das als Folie oder als Beschichtung ausgebildete Füllvolumen (42) auf eine Planseite (36) der Ankerplatte (34) aufgebracht ist, oder zwischen die Planseite (36) und die Stirnseite (38) des Gehäuses (22) eingelegt ist.5. Pressure control valve (20) according to claim 3, characterized in that the formed as a film or coating filling volume (42) on a plan side (36) of the anchor plate (34) is applied, or between the plan side (36) and the end face ( 38) of the housing (22) is inserted.
6. Druckregelventil (20) gemäß Anspruch 3, dadurch gekennzeichnet, dass das als Folie oder als Beschichtung ausgebildete Füllvolumen (42) auf die Stirnseite (38) des Gehäuses (22) aufgebracht ist.6. Pressure control valve (20) according to claim 3, characterized in that the foil or coating formed as a filling volume (42) on the end face (38) of the housing (22) is applied.
7. Druckregelventil (20) gemäß Anspruch 3, dadurch gekennzeichnet, dass zwischen dem Füllvolumen (42) und der Planseite (36) der Ankerplatte (34) oder der Stirnseite (38) des Gehäuses (22) ein nicht-magnetischer Spalt (48) verbleibt.7. Pressure control valve (20) according to claim 3, characterized in that between the filling volume (42) and the plan side (36) of the anchor plate (34) or the end face (38) of the housing (22) has a non-magnetic gap (48). remains.
8. Druckregelventil (20) gemäß Anspruch 1, dadurch gekennzeichnet, dass ein Volumen in einem Einsatz (26) des Gehäuses (22), in dem die Ankerplatte (34) der Ankerbaugruppe (32) aufgenommen ist, von dem verringerten Volumen (40) in das Medium aus dem Hochdruckspeicher (42) abgesteuert wird, entkoppelt ist. 8. Pressure control valve (20) according to claim 1, characterized in that a volume in an insert (26) of the housing (22), in which the armature plate (34) of the armature assembly (32) is received, from the reduced volume (40). is decoupled into the medium from the high-pressure accumulator (42) is decoupled.
9. Druckregelventil (20) gemäß Anspruch 1, dadurch gekennzeichnet, dass im Hochdruckspeicherkörper (72) ein Systemdruck p von mindestens > 1500 bar herrscht, während im Gehäuse (22) des Druckregelventils (20) der in einer Absteuerleitung (70) herrschende Druck vorliegt.9. Pressure control valve (20) according to claim 1, characterized in that in the high-pressure accumulator body (72) a system pressure p of at least> 1500 bar prevails, while in the housing (22) of the pressure control valve (20) in a Absteuerleitung (70) prevailing pressure is present ,
10. Druckregelventil (20) gemäß einem oder mehreren der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass dieses in einem Kraftstoffeinspritzsystem, insbesondere einem Hochdruckspeichereinspritzsystem, angeordnet ist. 10. Pressure control valve (20) according to one or more of the preceding claims, characterized in that it is arranged in a fuel injection system, in particular a high-pressure accumulator injection system.
EP08717877.8A 2007-03-21 2008-03-17 Pressure control valve Active EP2137400B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007013525A DE102007013525A1 (en) 2007-03-21 2007-03-21 Pressure control valve
PCT/EP2008/053140 WO2008113776A1 (en) 2007-03-21 2008-03-17 Pressure control valve

Publications (2)

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EP2137400A1 true EP2137400A1 (en) 2009-12-30
EP2137400B1 EP2137400B1 (en) 2013-05-29

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US (1) US20110220740A1 (en)
EP (1) EP2137400B1 (en)
JP (1) JP2010521621A (en)
CN (1) CN101641514A (en)
DE (1) DE102007013525A1 (en)
ES (1) ES2412232T3 (en)
WO (1) WO2008113776A1 (en)

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DE102007013525A1 (en) 2008-09-25
ES2412232T3 (en) 2013-07-10
JP2010521621A (en) 2010-06-24
CN101641514A (en) 2010-02-03
US20110220740A1 (en) 2011-09-15
WO2008113776A1 (en) 2008-09-25
EP2137400B1 (en) 2013-05-29

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