EP1304476A2 - High pressure resistant injector body - Google Patents
High pressure resistant injector body Download PDFInfo
- Publication number
- EP1304476A2 EP1304476A2 EP02015756A EP02015756A EP1304476A2 EP 1304476 A2 EP1304476 A2 EP 1304476A2 EP 02015756 A EP02015756 A EP 02015756A EP 02015756 A EP02015756 A EP 02015756A EP 1304476 A2 EP1304476 A2 EP 1304476A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve chamber
- injector body
- inlet opening
- bulges
- inlet
- 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
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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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/008—Arrangement of fuel passages inside of injectors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/03—Fuel-injection apparatus having means for reducing or avoiding stress, e.g. the stress caused by mechanical force, by fluid pressure or by temperature variations
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
- F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
- F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
Definitions
- the invention relates to an injector body for a Fuel injection system, wherein the injector body one essentially cylindrical valve chamber has in the via an inlet bore in a Inlet opening in the valve compartment opens, fuel under High pressure can be introduced.
- Such injector bodies for fuel injection systems have a substantially cylindrical shape Valve chamber, in the wall of which an inlet opening Inlet bore comes to rest.
- the inlet bore is in place for its part in connection with a pressure connection at which the supply line for fuel under high pressure flows out of a high-pressure collecting space.
- the High pressure resistance of the injector body depends on the The geometry of the inlet area is crucial.
- the Intersection of the inlet bore with the valve chamber is the most stressed part.
- One of the parameters is here the inlet angle of the inlet bore from High pressure manifold (common rail) in the injector body. Is this angle between the central axis of the Inlet bore and longitudinal axis of the valve chamber about 90 °, the stresses in the intersection area can be low being held.
- the installation conditions on the cylinder head However, an internal combustion engine does not always allow Entry angle of 90 °.
- the Valve space at least in the area of the inlet opening of the Inlet bore to the valve chamber in the circumferential direction adjacent to this inlet opening, a bulge of the Cross section on. So it comes from both sides of the Inlet opening in the valve chamber for an increase in volume.
- Is the entry angle (angle between the central axis the inlet bore and the longitudinal axis of the valve chamber) 90 ° are the bulges proposed according to the invention of the valve chamber cross section advantageously in one Plane perpendicular to the longitudinal axis of the valve space.
- the longitudinal direction of the valve chamber extends Bulge at least over the area of the inlet opening.
- the plane in which the bulges lie in orientate in the same way as the inlet bore so that the center line of the inlet bore through this plane runs.
- the bulges in the Cross section perpendicular to the longitudinal axis of the valve chamber to install.
- valve chambers are cylindrical in shape accordingly have a circular cross section (perpendicular to the longitudinal axis of the valve chamber).
- the Bulges according to the invention run in the area of Inlet opening of the inlet hole in each case in the circumferential direction of the valve chamber adjacent to the inlet opening, so that the Bulges to deviate from the circular Cross section. It has been shown that a large Strength increases when there is a bulge extends at least to a level defined by the Inlet opening and parallel to the longitudinal axis of the valve chamber runs. Again, it is particularly advantageous if the bulges are arranged symmetrically to the inlet opening are. Extend the bulges over the above Level out, so that arise under internal pressure Bending compressive stresses in the area of the inlet opening Even better compensate for notch tension stresses that occur.
- the invention proposed bulges up to the above Plane parallel to the longitudinal axis of the valve space and extends through the inlet opening, is it is advantageous if the valve chamber cross-section is even is continued up to the named level, the Diameter then the maximum diameter of the valve space can correspond. With such a configuration showed that a further increase in strength can be achieved if the inlet bore is eccentric in with respect to the valve chamber.
- FIG. 1 The essential structure of an injector body 1 is shown in FIG. 1 in a section through the longitudinal axis of the injector body 1.
- the injector body 1 essentially comprises one cylindrical valve chamber 3, in the wall of which one Inlet opening 7 for the supply of high pressure standing fuel. This inlet opening 7 forms the mouth of the inlet bore 2 in the valve chamber 3. Die Inlet bore 2 leads to the pressure connection 5 to which the High pressure manifold (common rail) connects.
- the injector body in turn has an internal thread 4 Connection to the injection system.
- the entry angle i.e. the angle between Longitudinal axis of the valve chamber 3 and central axis of the Inlet bore 2, in the illustration according to FIG. 1 Although less than 90 °, it is still in the area above 75 °, i.e. in an area in which one tension-reducing effect through the entry angle given is.
- FIG. 2A is a highly schematized one according to the invention Injector body 1 in the same way as from Fig. 1 shown. The same elements are the same Provide reference numerals.
- the inlet hole 2 leads here in the right angle to the valve chamber 3 of the injector body 1.
- FIG. 2A are those in the plane Bulges 8 of the perpendicular to the plane of the drawing Valve chamber cross section hardly due to the type of representation recognizable.
- FIG. 2B shows Section along the line A-A of Fig. 2A in a clear manner the bulges 8 according to the invention on both sides of the Inlet opening 7 of the inlet hole 2.
- the bulges 8 of the valve chamber cross section are in this example symmetrical to the inlet opening 7 and are wide led back towards the inlet hole.
- the bulges 8 change the Cross section of the valve chamber 3 at least in the area of Inlet opening 7 such that the original circular cross section only in the inlet opening 7 opposite half of the valve chamber 3 maintained while in the other half with the valve compartment maximum diameter up to a plane 9 that is parallel to the longitudinal axis 10 of the valve chamber 3 and through the Inlet opening 7 runs, is continued and above in addition two symmetrical to the center line of the inlet bore 2 and has indentations lying behind level 9.
- the bulges 8 shown lead to a Deformation of the valve chamber 3 under internal pressure with a Training of bending pressure and circumferential tensile stresses in Area of the bulges 8, the notch tension in the Reduce intersection area 6. So overall it comes for a partial compensation of the occurring Voltages so that the maximum voltage in Intersection area 6 is reduced.
- FIG. 2C shows a section along the line B-B from FIG. 2 B. This results in the course of the bulges 8 in Longitudinal direction of the valve chamber 3.
- the bulges 8 focus on the area of the inlet opening 7 and take on both sides in the longitudinal direction of the valve chamber 3 off again, so that the valve chamber 3 there its original takes cylindrical shape again.
- FIG. 3 Another embodiment of the invention is shown in FIG. 3 shown schematically.
- the eccentric The arrangement of the inlet bore 2 has this Embodiment as a further strength-increasing Measure proven.
- the invention can be different Geometries of valve chamber cross sections in the area of Inlet opening to be specified, leading to a reduction the stresses occurring in the intersection area and thus to an increase in the high pressure resistance of the Guide injector body. Especially at High-pressure fuel injectors can be used with it Achieve success.
Abstract
Description
Die Erfindung betrifft einen Injektorkörper für ein Kraftstoffeinspritzsystem, wobei der Injektorkörper einen im wesentlichen zylindrisch ausgestalteten Ventilraum aufweist, in den über eine Zulaufbohrung, die in einer Zulauföffnung im Ventilraum mündet, Kraftstoff unter Hochdruck einleitbar ist.The invention relates to an injector body for a Fuel injection system, wherein the injector body one essentially cylindrical valve chamber has in the via an inlet bore in a Inlet opening in the valve compartment opens, fuel under High pressure can be introduced.
Derartige Injektorkörper für Kraftstoffeinspritzsysteme besitzen einen im wesentlichen zylindrisch ausgeformten Ventilraum, in dessen Wandung die Zulauföffnung einer Zulaufbohrung zu liegen kommt. Die Zulaufbohrung steht ihrerseits mit einem Druckanschluß in Verbindung, an dem die Zuleitung für unter hohem Druck stehenden Kraftstoff aus einem Hochdrucksammelraum mündet. Die Hochdruckfestigkeit des Injektorkörpers hängt von der Geometrie des Zulaufbereichs entscheidend ab. Die Verschneidung der Zulaufbohrung mit dem Ventilraum stellt die höchstbelastete Stelle dar. Einer der Parameter ist hier der Einlaufwinkel der Zulaufbohrung vom Hochdrucksammelraum (Common Rail) in den Injektorkörper. Beträgt dieser Winkel zwischen Mittelachse der Zulaufbohrung und Längsachse des Ventilraums etwa 90°, können die Beanspruchungen im Verschneidungsbereich gering gehalten werden. Die Einbauverhältnisse am Zylinderkopf einer Verbrennungskraftmaschine erlaubt jedoch nicht immer Einlaufwinkel von 90°.Such injector bodies for fuel injection systems have a substantially cylindrical shape Valve chamber, in the wall of which an inlet opening Inlet bore comes to rest. The inlet bore is in place for its part in connection with a pressure connection at which the supply line for fuel under high pressure flows out of a high-pressure collecting space. The High pressure resistance of the injector body depends on the The geometry of the inlet area is crucial. The Intersection of the inlet bore with the valve chamber is the most stressed part. One of the parameters is here the inlet angle of the inlet bore from High pressure manifold (common rail) in the injector body. Is this angle between the central axis of the Inlet bore and longitudinal axis of the valve chamber about 90 °, the stresses in the intersection area can be low being held. The installation conditions on the cylinder head However, an internal combustion engine does not always allow Entry angle of 90 °.
Die Hauptbeanspruchung der Verschneidungsstelle wird durch den anliegenden Innendruck hervorgerufen. Unter diesem Innendruck führt die Kerbwirkung der Zulaufbohrung im Verschneidungsbereich der Bohrungen zu hohen lokalen Kerbzugspannungen in Umfangsrichtung des Ventilraumes. Auch bei optimalem Einlaufwinkel sind die genannten Zugspannungen der begrenzende Faktor für die Hochdruckfestigkeit des Injektorkörpers.The main stress on the intersection is by the applied internal pressure. Under this Internal pressure leads to the notch effect of the inlet bore in the Intersection area of the holes to high local Notch tension in the circumferential direction of the valve space. Also with an optimal entry angle, these are Tension is the limiting factor for the High pressure resistance of the injector body.
Es stellt sich folglich das Problem, die Kerbzugspannungen in Umfangsrichtung des Ventilraumes bei einem gattungsgemäßen Injektorkörper herabzusetzen, um diesen für höhere Druckbelastungen auslegen zu können.The problem then arises, the notch tension in the circumferential direction of the valve chamber at one Generic injector body to reduce this for to be able to design higher pressure loads.
Bei der erfindungsgemäß vorgeschlagenen Lösung weist der Ventilraum zumindest im Bereich der Zulauföffnung der Zulaufbohrung zum Ventilraum jeweils in Umfangsrichtung benachbart zu dieser Zulauföffnung eine Ausbuchtung des Querschnitts auf. Somit kommt es beiderseits der Zulauföffnung im Ventilraum zu einer Volumenvergrößerung. Hierdurch verformt sich der Ventilraum im Verschneidungsbereich der Bohrungen unter Innendruck derart, daß es durch die stärkere Krümmung im Bereich der Hochdruckverschneidung zu einer Überlagerung von Biegedruck- und Umfangszugspannungen kommt, welche wiederum die Kerbzugspannungen im Verschneidungsbereich der beiden Bohrungen (Zulaufbohrung und Ventilraumbohrung) verringert.In the solution proposed according to the invention, the Valve space at least in the area of the inlet opening of the Inlet bore to the valve chamber in the circumferential direction adjacent to this inlet opening, a bulge of the Cross section on. So it comes from both sides of the Inlet opening in the valve chamber for an increase in volume. This deforms the valve chamber in the Intersection area of the holes under internal pressure such that it is due to the greater curvature in the area of High pressure blending to an overlay of Bending pressure and circumferential tensile stresses come, which in turn the notch tensile stresses in the intersection area of the two Bores (inlet bore and valve chamber bore) reduced.
Vorteilhaft sind hierbei zu beiden Seiten der Zulauföffnung symmetrisch geformte Ausbuchtungen. Durch diese Symmetrie können sich auftretende Spannungen optimal kompensieren.This is advantageous on both sides of the inlet opening symmetrically shaped bulges. Because of this symmetry can optimally compensate for occurring tensions.
Beträgt der Einlaufwinkel (Winkel zwischen der Mittelachse der Zulaufbohrung und der Längsachse des Ventilraums) 90°, liegen die erfindungsgemäß vorgeschlagenen Ausbuchtungen des Ventilraumquerschnitts vorteilhafterweise in einer Ebene senkrecht zur Längsachse des Ventilraums. In Längsrichtung des Ventilraums erstreckt sich die Ausbuchtung zumindest über den Bereich der Zulauföffnung. Bei anderen Einlaufwinkeln als 90°, kann es vorteilhaft sein, die Ebene, in der die Ausbuchtungen liegen, in gleicher Weise wie die Zulaufbohrung zu orientieren, so daß die Mittellinie der Zulaufbohrung durch diese Ebene verläuft. Meist ist es jedoch ausreichend und herstellungstechnisch einfacher, die Ausbuchtungen im Querschnitt senkrecht zur Längsachse des Ventilraums anzubringen.Is the entry angle (angle between the central axis the inlet bore and the longitudinal axis of the valve chamber) 90 °, are the bulges proposed according to the invention of the valve chamber cross section advantageously in one Plane perpendicular to the longitudinal axis of the valve space. In The longitudinal direction of the valve chamber extends Bulge at least over the area of the inlet opening. With entry angles other than 90 °, it can be advantageous be, the plane in which the bulges lie, in orientate in the same way as the inlet bore so that the center line of the inlet bore through this plane runs. However, it is usually sufficient and technically simpler, the bulges in the Cross section perpendicular to the longitudinal axis of the valve chamber to install.
Die in den meisten Fällen zylindrisch geformten Ventilräume besitzen demgemäß einen kreisförmigen Querschnitt (senkrecht zur Längsachse des Ventilraums). Die erfindungsgemäßen Ausbuchtungen verlaufen im Bereich der Zulauföffnung der Zulaufbohrung jeweils in Umfangsrichtung des Ventilraums benachbart zur Zulauföffnung, so daß die Ausbuchtungen zu einem Abweichen vom kreisförmigen Querschnitt führen. Es hat sich gezeigt, daß eine große Festigkeitssteigerung eintritt, wenn eine Ausbuchtung sich mindestens bis zu einer Ebene erstreckt, die durch die Zulauföffnung sowie parallel zur Längsachse des Ventilraums verläuft. Hierbei ist es wieder besonders vorteilhaft, wenn die Ausbuchtungen symmetrisch zur Zulauföffnung angeordnet sind. Erstrecken sich die Ausbuchtungen über die genannte Ebene hinaus, so können die unter Innendruck entstehenden Biegedruckspannungen im Bereich der Zulauföffnung die auftretenden Kerbzugspannungen noch besser kompensieren.In most cases the valve chambers are cylindrical in shape accordingly have a circular cross section (perpendicular to the longitudinal axis of the valve chamber). The Bulges according to the invention run in the area of Inlet opening of the inlet hole in each case in the circumferential direction of the valve chamber adjacent to the inlet opening, so that the Bulges to deviate from the circular Cross section. It has been shown that a large Strength increases when there is a bulge extends at least to a level defined by the Inlet opening and parallel to the longitudinal axis of the valve chamber runs. Again, it is particularly advantageous if the bulges are arranged symmetrically to the inlet opening are. Extend the bulges over the above Level out, so that arise under internal pressure Bending compressive stresses in the area of the inlet opening Even better compensate for notch tension stresses that occur.
In einer Ausgestaltung, bei der die erfindungsgemäß vorgeschlagenen Ausbuchtungen sich bis zu der obengenannten Ebene, die parallel zur Längsachse des Ventilraums und durch die Zulauföffnung hindurch verläuft, erstrecken, ist es vorteilhaft, wenn der Ventilraumquerschnitt gleichmäßig bis zu der genannten Ebene fortgeführt wird, wobei der Durchmesser dann dem maximalen Durchmesser des Ventilraums entsprechen kann. Bei einer derartigen Ausgestaltung hat sich gezeigt, daß eine weitere Festigkeitssteigerung erzielt werden kann, wenn die Zulaufbohrung exzentrisch in bezug auf den Ventilraum verläuft.In an embodiment in which the invention proposed bulges up to the above Plane parallel to the longitudinal axis of the valve space and extends through the inlet opening, is it is advantageous if the valve chamber cross-section is even is continued up to the named level, the Diameter then the maximum diameter of the valve space can correspond. With such a configuration showed that a further increase in strength can be achieved if the inlet bore is eccentric in with respect to the valve chamber.
Im folgenden sollen Ausführungsbeispiele die Erfindung anhand der beigefügten Figuren näher erläutern.The following are exemplary embodiments of the invention explain in more detail with reference to the accompanying figures.
- Fig. 1Fig. 1
- den Schnitt durch die Längsachse eines Injektorkörpers für ein Kraftstoff-Hochdruckeinspritzsystem,the section through the longitudinal axis of a Injector body for a high-pressure fuel injection system,
- Fig. 2 AFig. 2A
- einen erfindungsgemäßen Injektorkörper in stark schematisierter Form im Längsschnitt, an injector body according to the invention in strong schematic form in longitudinal section,
- Fig. 2 BFig. 2B
- den Schnitt durch die Linie A-A aus Fig. 2 A,the section through the line A-A of Fig. 2 A,
- Fig. 2 CFig. 2C
- den Schnitt durch die Linie B-B aus Fig. 2 B undthe section through the line B-B of Fig. 2 B and
- Fig. 3Fig. 3
- eine weitere Ausführungsform des erfindungsgemäßen Injektorkörpers in der gleichen Darstellung wie Fig. 3.a further embodiment of the injector body according to the invention in the same Representation as Fig. 3rd
Den wesentlichen Aufbau eines Injektorkörpers 1 zeigt Fig.
1 in einem Schnitt durch die Längsachse des Injektorkörpers
1.The essential structure of an
Der Injektorkörper 1 umfaßt einen im wesentlichen
zylindrischen Ventilraum 3, in dessen Wandung sich eine
Zulauföffnung 7 für die Zuleitung von unter hohem Druck
stehenden Kraftstoff befindet. Diese Zulauföffnung 7 bildet
die Mündung der Zulaufbohrung 2 in den Ventilraum 3. Die
Zulaufbohrung 2 führt zum Druckanschluß 5, an den sich der
Hochdrucksammelraum (Common Rail) anschließt. Der
Injektorkörper weist seinerseits ein Innengewinde 4 zum
Anschluß an das Einspritzsystem auf.The
Im Verschneidungsbereich 6 der Zulaufbohrung 2 zum
Ventilraum 3 kommt es aufgrund der hohen Kraftstoffdrücke
zu starken Belastungen. Bei hohen Innendrücken führt die
Kerbwirkung der Zulaufbohrung 2 im Verschneidungsbereich 6
zu hohen lokalen Kerbzugspannungen in Umfangrichtung des
Ventilraums 3, so daß die Gefahr von Rissbildung besteht.
Sich ausbildende Risse führen letztendlich zu einem Ausfall
des Injektors. Der Einlaufwinkel, also der Winkel zwischen
Längsachse des Ventilraums 3 und Mittelachse der
Zulaufbohrung 2, beträgt in der Darstellung nach Fig. 1
zwar weniger als 90°, liegt jedoch noch im Bereich oberhalb
75°, also in einem Bereich, in dem eine
spannungsreduzierende Wirkung durch den Einlaufwinkel
gegeben ist.In the
In Fig. 2 A ist stark schematisiert ein erfindungsgemäßer
Injektorkörper 1 in der gleichen Betrachtungsweise wie aus
Fig. 1 dargestellt. Gleiche Elemente sind mit gleichen
Bezugszeichen versehen. Die Zulaufbohrung 2 führt hier im
rechten Winkel zum Ventilraum 3 des Injektorkörpers 1. In
der Darstellung der Fig. 2 A sind die in der Ebene
senkrecht zur Zeichenebene liegenden Ausbuchtungen 8 des
Ventilraumquerschnitts aufgrund der Darstellungsart kaum
erkennbar. Hingegen zeigt der in Fig. 2 B dargestellte
Schnitt entlang der Linie A-A aus Fig. 2 A in klarer Weise
die erfindungsgemäßen Ausbuchtungen 8 zu beiden Seiten der
Zulauföffnung 7 der Zulaufbohrung 2. Die Ausbuchtungen 8
des Ventilraumquerschnitts sind in diesem Beispiel
symmetrisch zur Zulauföffnung 7 ausgebildet und sind weit
nach hinten in Richtung Zulaufbohrung geführt. Wie aus Fig.
2 B ersichtlich, verändern die Ausbuchtungen 8 den
Querschnitt des Ventilraums 3 zumindest im Bereich der
Zulauföffnung 7 dergestalt, daß der ursprünglich
kreisförmige Querschnitt nur noch in der der Zulauföffnung
7 gegenüberliegenden Hälfte des Ventilraums 3 beibehalten
wird, während in der anderen Hälfte der Ventilraum mit
maximalem Durchmesser bis zu einer Ebene 9, die parallel
zur Längsachse 10 des Ventilraums 3 und durch die
Zulauföffnung 7 verläuft, fortgeführt wird und darüber
hinaus zwei symmetrisch zur Mittellinie der Zulaufbohrung 2
und hinter der Ebene 9 liegende Einbuchtungen aufweist.2A is a highly schematized one according to the
Die dargestellten Ausbuchtungen 8 führen zu einer
Verformung des Ventilraums 3 unter Innendruck mit einer
Ausbildung von Biegedruck- und Umfangszugspannungen im
Bereich der Ausbuchtungen 8, die die Kerbzugspannungen im
Verschneidungsbereich 6 verringern. Insgesamt kommt es also
zu einer teilweisen Kompensation der auftretenden
Spannungen, so daß die Maximalspannung im
Verschneidungsbereich 6 reduziert wird.The
Fig. 2 C zeigt einen Schnitt entlang der Linie B-B aus Fig.
2 B. Hieraus ergibt sich der Verlauf der Ausbuchtungen 8 in
Längsrichtung des Ventilraums 3. Die Ausbuchtungen 8
konzentrieren sich auf den Bereich der Zulauföffnung 7 und
nehmen zu beiden Seiten in Längsrichtung des Ventilraums 3
wieder ab, so daß der Ventilraum 3 dort seine ursprüngliche
zylinderförmige Gestalt wieder einnimmt.FIG. 2C shows a section along the line B-B from FIG.
2 B. This results in the course of the
Eine weitere Ausführungsform der Erfindung ist in Fig. 3
schematisch dargestellt. Auch hier weist der Ventilraum 3
Ausbuchtung 8 zu beiden Seiten der Zulauföffnung 7 auf, so
daß insgesamt ein symmetrischer Querschnitt des
Ventilinnenraums 3 entsteht, wobei hier eine Verbreiterung
des ursprünglich kreisförmigen Querschnitts auf einen
Querschnitt mit konstantem Durchmesser, der dem des
kreisförmigen Ventilraums 3 entspricht, bis zu der Ebene 9
stattfindet, die parallel zur Längsachse 10 des Ventilraums
3 und durch die Zulauföffnung 7 verläuft. Die exzentrische
Anordnung der Zulaufbohrung 2 hat sich bei diesem
Ausführungsbeispiel als weitere festigkeitssteigernde
Maßnahme bewährt.Another embodiment of the invention is shown in FIG. 3
shown schematically. Here too, the
Insgesamt können durch die Erfindung verschiedene Geometrien von Ventilraumquerschnitten im Bereich der Zulauföffnung angegeben werden, die zu einer Verminderung der auftretenden Spannungen im Verschneidungsbereich und somit zu einer Steigerung der Hochdruckfestigkeit des Injektorkörpers führen. Insbesondere bei Hochdruckkraftstoffinjektoren lassen sich damit gute Erfolge erzielen.Overall, the invention can be different Geometries of valve chamber cross sections in the area of Inlet opening to be specified, leading to a reduction the stresses occurring in the intersection area and thus to an increase in the high pressure resistance of the Guide injector body. Especially at High-pressure fuel injectors can be used with it Achieve success.
Claims (6)
dadurch gekennzeichnet, daß der Ventilraum (3) zumindest im Bereich der Zulauföffnung (7) jeweils in Umfangsrichtung benachbart zur Zulauföffnung (7) eine Ausbuchtung (8) seines Querschnitts aufweist.Injector body for a fuel injection system, the injector body (1) having an essentially cylindrically shaped valve chamber (3) into which fuel can be introduced under high pressure via an inlet bore (2) which opens into an inlet opening (7) in the valve chamber (3) .
characterized in that the valve chamber (3) has a bulge (8) in its cross section at least in the area of the inlet opening (7) in the circumferential direction adjacent to the inlet opening (7).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE10152230A DE10152230A1 (en) | 2001-10-20 | 2001-10-20 | High pressure resistant injector body |
| DE10152230 | 2001-10-20 |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| EP1304476A2 true EP1304476A2 (en) | 2003-04-23 |
| EP1304476A3 EP1304476A3 (en) | 2004-05-19 |
| EP1304476B1 EP1304476B1 (en) | 2011-09-14 |
Family
ID=7703405
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP02015756A Expired - Lifetime EP1304476B1 (en) | 2001-10-20 | 2002-07-13 | High pressure resistant injector body |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US6796512B2 (en) |
| EP (1) | EP1304476B1 (en) |
| JP (1) | JP4227393B2 (en) |
| DE (1) | DE10152230A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2010012393A1 (en) * | 2008-07-29 | 2010-02-04 | Robert Bosch Gmbh | Valve housing |
| WO2012103899A1 (en) * | 2011-02-01 | 2012-08-09 | Robert Bosch Gmbh | Housing for a pressure-loaded component |
| EP2960486A1 (en) * | 2014-06-25 | 2015-12-30 | Robert Bosch Gmbh | Method for reducing the tension at a connection between two channels which open into one another |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102007018471A1 (en) * | 2007-04-19 | 2008-10-23 | Robert Bosch Gmbh | Intersection between a high pressure chamber and a high pressure channel |
| DE102008040383A1 (en) | 2008-07-14 | 2010-01-21 | Robert Bosch Gmbh | High pressure resistant fuel injector |
| DE102011101770A1 (en) * | 2011-05-17 | 2012-08-02 | L'orange Gmbh | Assembly has solid body and intersection of high-pressure fluid channel with another high-pressure fluid channel is formed in solid body |
| AT512893B1 (en) * | 2013-02-05 | 2013-12-15 | Bosch Gmbh Robert | Component with intermeshing high pressure holes |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0449662A1 (en) * | 1990-03-29 | 1991-10-02 | Cummins Engine Company, Inc. | A fuel injector and a method of relieving stress concentration within a fuel injector bore |
| EP0717227A2 (en) * | 1994-12-16 | 1996-06-19 | Perkins Limited | A method for reducing stress at a junction of high pressure fluid flow passages in a body, and a junction formed thereby |
| DE19826719A1 (en) * | 1998-06-16 | 1999-12-23 | Bosch Gmbh Robert | Valve control unit for a fuel injector |
| DE10022378A1 (en) * | 2000-05-08 | 2001-11-22 | Bosch Gmbh Robert | Motor fuel injector body has an inflow channel from the common rail which opens into the ring zone through a recess in the zone wall for increased pressure resistance |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4709679A (en) * | 1985-03-25 | 1987-12-01 | Stanadyne, Inc. | Modular accumulator injector |
| KR880005354A (en) * | 1986-10-08 | 1988-06-28 | 나까무라 겐조 | Electronic actuator |
| JP3750126B2 (en) * | 1996-03-26 | 2006-03-01 | 株式会社デンソー | Fuel injection valve |
| US5755190A (en) * | 1996-11-18 | 1998-05-26 | Ronen; Avner | Reciprocating machine with cooling jacket |
| JP3939864B2 (en) * | 1998-08-27 | 2007-07-04 | ヤマハ発動機株式会社 | In-cylinder injection engine |
| US6598592B2 (en) * | 2000-10-04 | 2003-07-29 | Seimens Automotive Corporation | Fuel system including a fuel injector internally mounted to a fuel rail |
-
2001
- 2001-10-20 DE DE10152230A patent/DE10152230A1/en not_active Withdrawn
-
2002
- 2002-07-13 EP EP02015756A patent/EP1304476B1/en not_active Expired - Lifetime
- 2002-10-21 JP JP2002306325A patent/JP4227393B2/en not_active Expired - Fee Related
- 2002-10-21 US US10/274,106 patent/US6796512B2/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0449662A1 (en) * | 1990-03-29 | 1991-10-02 | Cummins Engine Company, Inc. | A fuel injector and a method of relieving stress concentration within a fuel injector bore |
| EP0717227A2 (en) * | 1994-12-16 | 1996-06-19 | Perkins Limited | A method for reducing stress at a junction of high pressure fluid flow passages in a body, and a junction formed thereby |
| DE19826719A1 (en) * | 1998-06-16 | 1999-12-23 | Bosch Gmbh Robert | Valve control unit for a fuel injector |
| DE10022378A1 (en) * | 2000-05-08 | 2001-11-22 | Bosch Gmbh Robert | Motor fuel injector body has an inflow channel from the common rail which opens into the ring zone through a recess in the zone wall for increased pressure resistance |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2010012393A1 (en) * | 2008-07-29 | 2010-02-04 | Robert Bosch Gmbh | Valve housing |
| US8844902B2 (en) | 2008-07-29 | 2014-09-30 | Robert Bosch Gmbh | Valve housing |
| WO2012103899A1 (en) * | 2011-02-01 | 2012-08-09 | Robert Bosch Gmbh | Housing for a pressure-loaded component |
| US20140026983A1 (en) * | 2011-02-01 | 2014-01-30 | Robert Bosch Gmbh | Housing for a pressure-loaded component |
| US9291278B2 (en) | 2011-02-01 | 2016-03-22 | Robert Bosch Gmbh | Housing for a pressure-loaded component |
| EP2960486A1 (en) * | 2014-06-25 | 2015-12-30 | Robert Bosch Gmbh | Method for reducing the tension at a connection between two channels which open into one another |
Also Published As
| Publication number | Publication date |
|---|---|
| DE10152230A1 (en) | 2003-04-30 |
| JP4227393B2 (en) | 2009-02-18 |
| EP1304476B1 (en) | 2011-09-14 |
| US20030089793A1 (en) | 2003-05-15 |
| EP1304476A3 (en) | 2004-05-19 |
| US6796512B2 (en) | 2004-09-28 |
| JP2003139013A (en) | 2003-05-14 |
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