EP1731750B1 - Device with junction of drilled holes - Google Patents

Device with junction of drilled holes Download PDF

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Publication number
EP1731750B1
EP1731750B1 EP06018655A EP06018655A EP1731750B1 EP 1731750 B1 EP1731750 B1 EP 1731750B1 EP 06018655 A EP06018655 A EP 06018655A EP 06018655 A EP06018655 A EP 06018655A EP 1731750 B1 EP1731750 B1 EP 1731750B1
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EP
European Patent Office
Prior art keywords
screw
pressurisation means
bore
tension
solid body
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.)
Expired - Lifetime
Application number
EP06018655A
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German (de)
French (fr)
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EP1731750A3 (en
EP1731750A2 (en
Inventor
Christoph Klesse
Hinrich Dr. Krueger
Christian Taudt
Martin Werner
Eckbert Zander
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Continental Automotive GmbH
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Continental Automotive GmbH
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Publication of EP1731750A3 publication Critical patent/EP1731750A3/en
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Publication of EP1731750B1 publication Critical patent/EP1731750B1/en
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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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • 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

Definitions

  • the invention relates to a device with a bore intersection
  • Bohrungsschneschneidung having solids has been reduced as far as possible by design changes.
  • Such structural changes include, for example, increasing the intersecting angle between the channels to at least 90 °, decreasing the bore diameter, and rounding the intersecting edge. But such structural changes are not applicable in many cases for a variety of reasons.
  • the object of the invention is therefore to provide a device of the type mentioned, in which the stresses occurring at a Bohrungsverschneidung can be reduced.
  • compressive stresses are introduced at this point by an essentially vertical force applied from the outside to an example, for example, an endangered point.
  • the advantage here is that in a simple manner targeted at the points of critical stress, the stress in the solid can be reduced by an external intervention. This can be done for example by a screw that presses on the channel intersection, thereby reducing the stresses that arise from the internal pressure in the channels and thus the Bohrungsverschneidung be reduced.
  • the introduction of the stresses can be realized both by an elastic, as well as by a plastic deformation.
  • the strength of the solid can be increased in a simple manner.
  • the compensating force can advantageously be used simultaneously for the attachment of certain components.
  • the stresses introduced from the outside can also be introduced by a clamping device in the solid.
  • this type of voltage reduction of critical points is advantageously used in high-pressure pumps, for example in radial piston pumps that compress fuel in common-rail systems to a high pressure of 1,500 bar and more and promote it in a fuel tank.
  • the critical points in high pressure pumps are the high pressure and intersecting fuel lines.
  • the voltage in the intersection of two or more fuel lines in the high-pressure pump is thereby reduced by applying a force from the outside to the housing containing the fuel lines.
  • the type of voltage reduction according to the invention is also used in fuel distributors, which are connected, for example, on the input side with a high-pressure pump and on the output side branching, each with a fuel storage.
  • the strain-relieving force is introduced onto the solid body substantially perpendicular to the plane formed by the respective intersecting bores.
  • FIG. 1 are in a solid state 2 three holes 4, 5, 6 introduced such that they open into one another at a point, the two holes 4 and 6 at an acute angle to each other, forming a blending edge 3.
  • the holes 4, 5, 6 form Channels for a not shown in detail in the drawing, pressurized medium, such as a gas or a liquid. Due to the pressure of the medium, compressive stresses build up in the solid 2, whose maximum occurs at the acute intersecting edge 3 of the bores 4 and 6.
  • a threaded hole 7 is introduced, in which a screw 1 is screwed as a threaded member such that by screwing the screw 1 compressive stresses in the solid 2 arise, which counteract the tensile stresses from the internal pressure of the holes 4, 5, 6 and thereby also at least reduce, if not neutralize, the stress maximum occurring at the intersection edge 3.
  • the force of the screw 1 acts in the region of the vulnerable point (bore intersection) essentially perpendicular to the plane formed by the respective intersecting bores 4, 5, 6 on the solid body 2.
  • the solid 2 is preferably part of a radial piston pump designed as a high-pressure pump.
  • FIG. 2 are two holes 13 and 14 are introduced in a solid 12, which open into each other at a certain angle in the interior of the solid 12.
  • the turn channels forming holes 13 and 14 are also subjected to a pressurized medium, whereby voltages in the solid state 12 are generated, which are at the trapped by the bores 13 and 14 intersecting edge 15 the strongest.
  • a clamping device is provided which consists of a solid body 12 annularly enclosing, rigid clamp body 10, on whose inner side an abutment 16 and on the opposite inner side a continuous threaded hole 17 is arranged. In the threaded hole 17, a screw 11 is screwed.
  • the solid body 12 is such that the connecting axis between the abutment 16 and screw 11 passes perpendicular to the Bohrungsverschneidung through this.
  • the screw 11 is tightened and exerts in conjunction with the abutment 16 a force on the solid 12. Again, the tension at the most critical point is reduced by an external force.
  • the solid body 12 is preferably part of a high pressure pump designed as a radial piston pump.
  • the compensating voltages generated by elastic deformations in the solid state 2 it is in the embodiment according to FIG. 3 the tension achieved by a plastic deformation.
  • channels 23, 24, 25 formed by corresponding bores are introduced in a solid body 22 in such a way that they open into one another at a point from the outside into the interior of the solid body. Starting from this point, the channels 24 and 25 separate at an acute angle to each other and form there an intersecting edge 26.
  • two plastic deformations 20 and 21 are provided, which are corresponding recesses in the parallel to the Holes 23, 24, 25 and mutually parallel end faces 27 and 28 of the solid 22 are formed.
  • the solid 22 is preferably part of a radial piston pump designed as a high-pressure pump.
  • FIG. 4 an embodiment is shown which is preferably used in radial piston pumps for common rail systems application.
  • a solid body such as a housing 30, three holes 31, 32, 33 incorporated. These holes connect the individual cylinders of a fuel pump not shown higher and are under high pressure during operation.
  • the high-pressure outlet of the fuel pump is a Stub 35, which is connected via a bore 34 with the bores 31, 32, 33.
  • the bores 31, 32, 33, 34 open at a certain point into one another, wherein the bores 31 and 32 are arranged at a certain angle to each other and include an intersection edge 36 with.
  • the intersection edge 36 is the location where the maximum stress occurs.
  • the bore 34 continues within the nozzle 35, which is screwed into a threaded bore 37.
  • the nozzle 35 thus serves, on the one hand, as a continuation of the bore 34, for example for the purpose of connecting a high-pressure line, and on the other hand to reduce the stress in the housing 30 and in particular at the intersection edge 36 due to the screwed into the threaded bore 37, serving as a threaded element neck 35th
  • a recess is introduced, which causes a plastic deformation in addition to the elastic deformation of the nozzle 35 and the threaded bore 37, a voltage which generates the voltage generated by the internal pressure in the housing 30 and counteracts in particular at the intersection edge 36.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Measuring Fluid Pressure (AREA)
  • Fuel Cell (AREA)

Description

Die Erfindung betrifft eine Vorrichtung mit einer BohrungsverschneidungThe invention relates to a device with a bore intersection

Bei vielen Vorrichtungen wird mit unter hohem Druck stehenden Medien gearbeitet. Durch den Druck entstehen Spannungen in den die Medien führenden Rohren oder Kanälen. Bei Rohren treten dabei axiale Spannungen, radiale Spannungen und Spannungen in Umfangsrichtung auf, von denen die Spannung in Umfangsrichtung den größten Anteil an der Rohrbelastung haben. An Bohrungsverschneidungen wie beispielsweise sich verzweigenden Kanälen oder Bohrungen entstehen insbesondere bei spitzen Winkeln durch die Überlagerung der Spannungen aus beiden oder mehreren Bohrungen besonders hohe Spannungen in Form von Zugspannungen im Material. Das Spannungsmaximum wird direkt an der Verschneidungskante erreicht. Diese Stellen sind besonders bei nicht konstanten Drücken, also bei schwellender Belastung, stark bruchgefährdet. Es ist deshalb in erster Linie erforderlich, die Umfangsspannungen zu reduzieren.Many devices work with high pressure media. The pressure creates stresses in the pipes or channels carrying the media. In the case of pipes, axial stresses, radial stresses and stresses occur in the circumferential direction, of which the stress in the circumferential direction has the largest share of the pipe load. At Bohrungsschneschneidungen such as branching channels or holes especially at acute angles caused by the superposition of tensions from two or more holes particularly high voltages in the form of tensile stresses in the material. The maximum stress is reached directly at the intersection edge. These points are particularly at non-constant pressures, so with swelling load, high risk of breakage. It is therefore necessary first of all to reduce the hoop stresses.

In EP 0 717 227 A wird zu Erhöhung der Festigkeit die Methode der Kompressions-Restbeanspruchung beschrieben.In EP 0 717 227 A To increase the strength, the method of compression residual stress is described.

Aus DE 198 08 807 A1 ist ein Kraftstoffverteiler bekannt, von dem aus radial Anschlussstutzen ausgehen. Zur Erhöhung der Festigkeit wird der Kraftstoffverteiler in radialer Richtung bzw. der Anschlussstutzen in paralleler Richtung verformt.Out DE 198 08 807 A1 a fuel distributor is known from which emanate radially connecting piece. To increase the strength of the fuel rail in the radial direction or the connecting piece is deformed in a parallel direction.

Die Festigkeit des die Bohrungsverschneidung aufweisenden Festkörpers wurde bisher soweit als möglich durch konstruktive Änderungen reduziert. Derartige konstruktive Änderungen umfassen beispielsweise das Erhöhen des Verschneidungswinkels zwischen den Kanälen auf mindestens 90°, Verkleinern der Bohrungsdurchmesser sowie das Verrunden der Verschneidungskante. Derartige konstruktive Änderungen sind aber in vielen Fällen aus den verschiedensten Gründen nicht einsetzbar.The strength of Bohrungsschneschneidung having solids has been reduced as far as possible by design changes. Such structural changes include, for example, increasing the intersecting angle between the channels to at least 90 °, decreasing the bore diameter, and rounding the intersecting edge. But such structural changes are not applicable in many cases for a variety of reasons.

Aufgabe der Erfindung ist es daher, eine Vorrichtung der eingangs genannten Art anzugeben, bei der die auftretenden Spannungen an einer Bohrungsverschneidung herabgesetzt werden können.The object of the invention is therefore to provide a device of the type mentioned, in which the stresses occurring at a Bohrungsverschneidung can be reduced.

Die Aufgabe wird gelöst durch eine Vorrichtung gemäß dem Patentanspruch 1. Ausgestaltungen und Weiterbildungen des Erfindungsgedankens sind Gegenstand von Unteransprüchen.The object is achieved by a device according to the patent claim 1. refinements and developments of the inventive concept are the subject of dependent claims.

Erfindungsgemäß werden durch eine von außen auf eine beispielsweise gefährdete Stelle aufgebrachte, im Wesentlichen senkrechte Kraft Druckspannungen an dieser Stelle eingebracht. Vorteil dabei ist, dass auf einfache Weise gezielt an den Stellen kritischer Belastung die Spannung im Festkörper durch einen Eingriff von außen reduziert werden kann. Dies kann beispielsweise durch eine Schraube geschehen, die so auf die Kanalverschneidung drückt, dass dadurch die Spannungen, welche aus dem Innendruck in den Kanälen und damit der Bohrungsverschneidung entstehen, reduziert werden. Das Einbringen der Spannungen kann dabei sowohl durch eine elastische, als auch durch eine plastische Verformung realisiert werden. Weiterhin ist vorteilhaft, dass auch bei komplizierten Geometrien die Festigkeit des Festkörpers auf einfache Weise erhöht werden kann. Darüber hinaus kann die kompensierende Kraft vorteilhafterweise gleichzeitig zur Befestigung bestimmter Bauteile verwendet werden. Schließlich können die von außen eingebrachten Spannungen auch durch eine Klemmeinrichtung in den Festkörper eingebracht werden.According to the invention, compressive stresses are introduced at this point by an essentially vertical force applied from the outside to an example, for example, an endangered point. The advantage here is that in a simple manner targeted at the points of critical stress, the stress in the solid can be reduced by an external intervention. This can be done for example by a screw that presses on the channel intersection, thereby reducing the stresses that arise from the internal pressure in the channels and thus the Bohrungsverschneidung be reduced. The introduction of the stresses can be realized both by an elastic, as well as by a plastic deformation. Furthermore, it is advantageous that even with complicated geometries, the strength of the solid can be increased in a simple manner. In addition, the compensating force can advantageously be used simultaneously for the attachment of certain components. Finally, the stresses introduced from the outside can also be introduced by a clamping device in the solid.

Weiterhin wird diese Art der Spannungsreduzierung von kritischen Stellen vorteilhaft in Hochdruckpumpen eingesetzt, beispielsweise in Radialkolbenpumpen, die in Common-Rail Systemen Kraftstoff auf einen Hochdruck von 1.500 bar und mehr komprimieren und in einen Kraftstoffspeicher fördern. Die kritischen Stellen sind in Hochdruckpumpen die unter Hochdruck stehenden und sich schneidenden Kraftstoffleitungen.Furthermore, this type of voltage reduction of critical points is advantageously used in high-pressure pumps, for example in radial piston pumps that compress fuel in common-rail systems to a high pressure of 1,500 bar and more and promote it in a fuel tank. The critical points in high pressure pumps are the high pressure and intersecting fuel lines.

Die Spannung in der Verschneidung von zweien oder mehreren Kraftstoffleitungen in der Hochdruckpumpe wird dabei reduziert, indem von außen auf das die Kraftstoffleitungen enthaltende Gehäuse eine Kraft aufgebracht wird.The voltage in the intersection of two or more fuel lines in the high-pressure pump is thereby reduced by applying a force from the outside to the housing containing the fuel lines.

Vorteilhaft wird die erfindungsgemäße Art der Spannungsverminderung auch bei Kraftstoffverteilern eingesetzt, die beispielsweise eingangsseitig mit einer Hochdruckpumpe und ausgangsseitig verzweigend mit je einem Kraftstoffspeicher verbunden sind.Advantageously, the type of voltage reduction according to the invention is also used in fuel distributors, which are connected, for example, on the input side with a high-pressure pump and on the output side branching, each with a fuel storage.

Im Bereich der gefährdeten Stelle (Bohrungsverschneidung) wird die spannungsmindernde Kraft im wesentlichen senkrecht zur Ebene, die von den jeweiligen sich schneidenden Bohrungen gebildet werden, auf den Festkörper eingebracht.In the area of the vulnerable site (bore intersection), the strain-relieving force is introduced onto the solid body substantially perpendicular to the plane formed by the respective intersecting bores.

Die Erfindung wird nachfolgend anhand der in den Figuren der Zeichnung dargestellten Ausführungsbeispiele näher erläutert. Es zeigt:

Figur 1
eine erste Ausführungsform einer erfindungsgemäßen Vorrichtung mit einer Schraube zur Spannungserzeugung,
Figur 2
eine zweite Ausführungsform einer erfindungsgemäßen Vorrichtung mit einer Klemmeinrichtung zur Spannungserzeugung
Figur 3
eine vom Stand der Technik bekannte Ausführungsform mit einer plastischen Verformung zur Spannungserzeugung und
Figur 4
eine vierte Ausführungsform der Erfindung, bei der sowohl elastische als auch plastische Verformungen eingesetzt werden.
The invention will be explained in more detail with reference to the embodiments illustrated in the figures of the drawing. It shows:
FIG. 1
a first embodiment of a device according to the invention with a screw for generating voltage,
FIG. 2
A second embodiment of a device according to the invention with a clamping device for voltage generation
FIG. 3
a known from the prior art embodiment with a plastic deformation for voltage generation and
FIG. 4
a fourth embodiment of the invention, in which both elastic and plastic deformations are used.

Bei dem Ausführungsbeispiel nach Figur 1 sind in einen Festkörper 2 drei Bohrungen 4, 5, 6 derart eingebracht, daß sie an einer Stelle ineinander münden, wobei die beiden Bohrungen 4 und 6 in spitzem Winkel zueinander, eine Verschneidungskante 3 bildend angeordnet sind. Die Bohrungen 4, 5, 6 bilden Kanäle für ein in der Zeichnung nicht näher dargestelltes, unter Druck stehendes Medium, wie beispielsweise ein Gas oder eine Flüssigkeit. Durch den Druck des Mediums bauen sich Druckspannungen im Festkörper 2 auf, deren Maximum an der spitzen Verschneidungskante 3 der Bohrungen 4 und 6 auftritt. Senkrecht zur Bohrungsverschneidung ist eine Gewindebohrung 7 eingebracht, in die eine Schraube 1 als Gewindeelement derart eingedreht ist, daß durch das Einschrauben der Schraube 1 Druckspannungen im Festkörper 2 entstehen, die den Zugspannungen aus dem Innendruck der Bohrungen 4, 5, 6 entgegenwirken und dadurch auch das an der Verschneidungskante 3 auftretende Spannungsmaximum zumindest herabsetzen, wenn nicht neutralisieren. Dabei wirkt die Kraft der Schraube 1 im Bereich der gefährdeten Stelle (Bohrungsverschneidung) im wesentlichen senkrecht zur Ebene, die von den jeweiligen sich schneidenden Bohrungen 4, 5, 6 gebildet werden, auf den Festkörper 2 ein.According to the embodiment FIG. 1 are in a solid state 2 three holes 4, 5, 6 introduced such that they open into one another at a point, the two holes 4 and 6 at an acute angle to each other, forming a blending edge 3. The holes 4, 5, 6 form Channels for a not shown in detail in the drawing, pressurized medium, such as a gas or a liquid. Due to the pressure of the medium, compressive stresses build up in the solid 2, whose maximum occurs at the acute intersecting edge 3 of the bores 4 and 6. Perpendicular to Bohrungsschneschneidung a threaded hole 7 is introduced, in which a screw 1 is screwed as a threaded member such that by screwing the screw 1 compressive stresses in the solid 2 arise, which counteract the tensile stresses from the internal pressure of the holes 4, 5, 6 and thereby also at least reduce, if not neutralize, the stress maximum occurring at the intersection edge 3. In this case, the force of the screw 1 acts in the region of the vulnerable point (bore intersection) essentially perpendicular to the plane formed by the respective intersecting bores 4, 5, 6 on the solid body 2.

Der Festkörper 2 ist dabei vorzugsweise Teil einer als Radialkolbenpumpe ausgebildeten Hochdruckpumpe.The solid 2 is preferably part of a radial piston pump designed as a high-pressure pump.

Bei dem Ausführungsbeispiel nach Figur 2 sind in einem Festkörper 12 zwei Bohrungen 13 und 14 eingebracht, die im Inneren des Festkörpers 12 unter einem bestimmten Winkel ineinander münden. Die wiederum Kanäle bildenden Bohrungen 13 und 14 sind ebenfalls mit einem unter Druck stehenden Medium beaufschlagt, wodurch Spannungen im Festkörper 12 erzeugt werden, die an der von den Bohrungen 13 und 14 eingeschlossenen Verschneidungskante 15 am stärksten sind. Zum Erzeugen der von außen zugeführten Kompensationsspannung ist eine Klemmvorrichtung vorgesehen, die aus einem den Festkörper 12 ringförmig umschließenden, starren Klemmenkörper 10 besteht, an dessen einen Innenseite ein Widerlager 16 und an der gegenüberliegenden Innenseite eine durchgängige Gewindebohrung 17 angeordnet ist. In die Gewindebohrung 17 ist eine Schraube 11 eingedreht. Zwischen den Stirnflächen des Widerlagers 16 und der Schraube 11 befindet sich der Festkörper 12 derart, daß die Verbindungsachse zwischen Widerlager 16 und Schraube 11 senkrecht zur Bohrungsverschneidung durch diese hindurchführt. Die Schraube 11 ist dabei festgedreht und übt in Verbindung mit dem Widerlager 16 eine Kraft auf den Festkörper 12 aus. Auch hier wird durch eine äußere Kraft die Spannung an der kritischsten Stelle reduziert.According to the embodiment FIG. 2 are two holes 13 and 14 are introduced in a solid 12, which open into each other at a certain angle in the interior of the solid 12. The turn channels forming holes 13 and 14 are also subjected to a pressurized medium, whereby voltages in the solid state 12 are generated, which are at the trapped by the bores 13 and 14 intersecting edge 15 the strongest. For generating the externally supplied compensation voltage, a clamping device is provided which consists of a solid body 12 annularly enclosing, rigid clamp body 10, on whose inner side an abutment 16 and on the opposite inner side a continuous threaded hole 17 is arranged. In the threaded hole 17, a screw 11 is screwed. Between the end faces of the abutment 16 and the screw 11, the solid body 12 is such that the connecting axis between the abutment 16 and screw 11 passes perpendicular to the Bohrungsverschneidung through this. The screw 11 is tightened and exerts in conjunction with the abutment 16 a force on the solid 12. Again, the tension at the most critical point is reduced by an external force.

Der Festkörper 12 ist dabei vorzugsweise Teil einer als Radialkolbenpumpe ausgebildeten Hochdruckpumpe.The solid body 12 is preferably part of a high pressure pump designed as a radial piston pump.

Waren bei den bisherigen Ausführungsbeispiel die kompensierenden Spannungen durch elastische Verformungen in dem Festkörper 2 erzeugt worden, so wird bei dem Ausführungsbeispiel nach Figur 3 die Spannung durch eine plastische Verformung erzielt. Bei diesem nicht beanspruchten Ausführungsbeispiel sind in einem Festkörper 22 durch entsprechende Bohrungen gebildete Kanäle 23, 24, 25 derart eingebracht, dass diese von außen in das Festkörperinnere führend an einer Stelle ineinander münden. Ausgehend von dieser Stelle trennen sich die Kanäle 24 und 25 in einem spitzen Winkel zueinander und bilden dort eine Verschneidungskante 26. Um die Spannung an der Bohrungsverschneidung 26 zu verringern sind zwei plastische Verformungen 20 und 21 vorgesehen, die als entsprechende Vertiefungen in den parallel zu den Bohrungen 23, 24, 25 und parallel zueinander angeordneten Stirnflächen 27 und 28 des Festkörpers 22 ausgebildet sind.Were in the previous embodiment, the compensating voltages generated by elastic deformations in the solid state 2, it is in the embodiment according to FIG. 3 the tension achieved by a plastic deformation. In this embodiment not claimed, channels 23, 24, 25 formed by corresponding bores are introduced in a solid body 22 in such a way that they open into one another at a point from the outside into the interior of the solid body. Starting from this point, the channels 24 and 25 separate at an acute angle to each other and form there an intersecting edge 26. To reduce the voltage at the bore intersection 26, two plastic deformations 20 and 21 are provided, which are corresponding recesses in the parallel to the Holes 23, 24, 25 and mutually parallel end faces 27 and 28 of the solid 22 are formed.

Der Festkörper 22 ist dabei vorzugsweise Teil einer als Radialkolbenpumpe ausgebildeten Hochdruckpumpe.The solid 22 is preferably part of a radial piston pump designed as a high-pressure pump.

In Figur 4 ist eine Ausführungsform dargestellt, die bevorzugt in Radialkolbenpumpen für Common-Rail-Systeme Anwendung findet. Dabei sind in einem Festkörper, beispielsweise einem Gehäuse 30, drei Bohrungen 31, 32, 33 eingearbeitet. Diese Bohrungen verbinden die einzelnen Zylinder einer nicht höher gezeigten Kraftstoffpumpe und stehen im Betrieb unter Hochdruck. Als Hochdruckausgang der Kraftstoffpumpe dient ein Stutzen 35, der über eine Bohrung 34 mit den Bohrungen 31, 32, 33 verbunden ist. Die Bohrungen 31, 32, 33, 34 münden an einer bestimmten Stelle ineinander, wobei die Bohrungen 31 und 32 in einem bestimmten Winkel zueinander angeordnet sind und eine Verschneidungskante 36 mit einschließen. Die Verschneidungskante 36 ist der Ort, an dem die maximale Spannung auftritt. Die Bohrung 34 setzt sich dabei innerhalb des Stutzens 35 fort, welcher in eine Gewindebohrung 37 eingedreht ist. Der Stutzen 35 dient folglich zum einen als Fortsetzung der Bohrung 34, beispielsweise zum Zwecke des Anschlusses einer Hochdruckleitung, und zum anderen zur Spannungsverringerung im Gehäuse 30 und dabei insbesondere an der Verschneidungskante 36 aufgrund des in die Gewindebohrung 37 eingedrehten, als Gewindeelement dienenden Stutzens 35. Schließlich ist an der der Stirnseite des Stutzens 35 gegenüberliegenden Oberfläche des Gehäuses 30 eine Vertiefung eingebracht, welche als plastische Verformung zusätzlich zu der elastischen Verformung durch den Stutzen 35 und der Gewindebohrung 37 eine Spannung hervorruft, die der durch den Innendruck erzeugten Spannung im Gehäuse 30 und insbesondere an der Verschneidungskante 36 entgegenwirkt.In FIG. 4 an embodiment is shown which is preferably used in radial piston pumps for common rail systems application. In this case, in a solid body, such as a housing 30, three holes 31, 32, 33 incorporated. These holes connect the individual cylinders of a fuel pump not shown higher and are under high pressure during operation. The high-pressure outlet of the fuel pump is a Stub 35, which is connected via a bore 34 with the bores 31, 32, 33. The bores 31, 32, 33, 34 open at a certain point into one another, wherein the bores 31 and 32 are arranged at a certain angle to each other and include an intersection edge 36 with. The intersection edge 36 is the location where the maximum stress occurs. The bore 34 continues within the nozzle 35, which is screwed into a threaded bore 37. The nozzle 35 thus serves, on the one hand, as a continuation of the bore 34, for example for the purpose of connecting a high-pressure line, and on the other hand to reduce the stress in the housing 30 and in particular at the intersection edge 36 due to the screwed into the threaded bore 37, serving as a threaded element neck 35th Finally, on the front side of the nozzle 35 opposite surface of the housing 30, a recess is introduced, which causes a plastic deformation in addition to the elastic deformation of the nozzle 35 and the threaded bore 37, a voltage which generates the voltage generated by the internal pressure in the housing 30 and counteracts in particular at the intersection edge 36.

Claims (10)

  1. Device with a solid body (2; 12; 22, 30), an intersecting bore (3, 4, 5, 6; 13, 14, 15; 23, 24, 25, 26; 31, 32, 33, 34, 36) to which internal pressure is applied and pressurisation means (1; 7, 10, 11, 16, 17; 35, 37, 38) arranged on the exterior of the solid body (2; 12; 22, 30) such that said pressurisation means introduce a tension into the solid body (2; 12; 30), said tension counteracting the tension generated by the internal pressure in the intersecting bores (3, 4, 5, 6; 13, 14, 15; 23, 24, 25, 26; 31, 32, 33, 34, 36), with the tension-reducing force of the pressurisation means (1; 7, 10, 11, 16, 17; 35, 37, 38) acting on the solid body (2; 12; 22; 30) essentially at right angles to that plane which is formed by the intersecting bores (3, 4, 5, 6; 13, 14, 15; 23, 24, 25, 26; 31, 32, 33, 34, 36).
  2. Device according to claim 1, in which pressurisation means (1; 10, 11, 16, 17; 35) produce a plastic deformation generating compression stresses.
  3. Device according to one of the preceding claims, wherein a bore (7; 37) and elements (1; 35) inserted therein are provided as pressurisation means.
  4. Device according to one of the preceding claims, wherein a bore (7; 37) with a screw thread is provided as pressurisation means, into which screw thread a screw element (1; 35) is introduced, generating a tension.
  5. Device according to one of the preceding claims, wherein a clamping unit (10, 11, 16, 17) is provided as a pressurisation means.
  6. Device according to claim 5, wherein the clamping unit (10) comprises a screw element (17), a screw (11) fastened therein, and an abutment (16) rigidly coupled to the clamping unit (10) and facing the screw (11), and the solid body (12) between the screw (11) and the abutment (16) is arranged under pressure.
  7. Device according to one of the preceding claims, wherein the pressurisation means (1; 10, 11, 17; 35, 38) are arranged such that the tension generated by the pressurisation means (1; 10, 11, 16, 17; 35) is at its greatest where the tension generated by the internal pressure of the bore intersection (3, 4, 5, 6; 13, 14, 15; 31, 32, 33, 34, 36) is also at its greatest.
  8. Device according to one of claims 4 to 7, wherein the screw element (35) is provided to fasten a further part.
  9. Device according to one of the preceding claims, wherein two channels bordering the intersecting bore (3, 4, 5, 6; 13, 14, 15; 31, 32, 33, 34, 36) join at an acute angle.
  10. High pressure pump, in particular radial piston pump, having a device according to one of the preceding claims.
EP06018655A 1998-11-06 1999-11-05 Device with junction of drilled holes Expired - Lifetime EP1731750B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1998151286 DE19851286C2 (en) 1998-11-06 1998-11-06 Device with intersection of holes
EP19990121000 EP0999361B1 (en) 1998-11-06 1999-11-05 Device with junction of drilled holes

Related Parent Applications (2)

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EP19990121000 Division EP0999361B1 (en) 1998-11-06 1999-11-05 Device with junction of drilled holes
EP99121000.6 Division 1999-11-05

Publications (3)

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EP1731750A2 EP1731750A2 (en) 2006-12-13
EP1731750A3 EP1731750A3 (en) 2006-12-27
EP1731750B1 true EP1731750B1 (en) 2008-06-25

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EP06018655A Expired - Lifetime EP1731750B1 (en) 1998-11-06 1999-11-05 Device with junction of drilled holes
EP19990121000 Expired - Lifetime EP0999361B1 (en) 1998-11-06 1999-11-05 Device with junction of drilled holes

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10029425B4 (en) * 2000-06-15 2004-11-18 Siemens Ag Bore arrangement with an intersection formed from at least three bores and method for the production thereof
DE102009000538A1 (en) 2009-02-02 2010-08-05 Robert Bosch Gmbh Geometry for increasing the strength of bore intersections in the high pressure area
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

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4163561A (en) * 1978-08-15 1979-08-07 Dart Industries Inc. Fatigue resistant fittings and methods of fabrication
GB2296039A (en) * 1994-12-16 1996-06-19 Perkins Ltd Stress reduction at a high pressure fluid passage junction
JP3841369B2 (en) * 1996-11-30 2006-11-01 臼井国際産業株式会社 Common rail
CA2230744A1 (en) * 1997-03-03 1998-09-03 Usui Kokusai Sangyo Kaisha Limited Common rail and method of manufacturing the same
DE19802476A1 (en) * 1998-01-23 1999-07-29 Bosch Gmbh Robert Pump fitting to supply fuel at high pressure for common rail fuel injection system of internal combustion engine

Also Published As

Publication number Publication date
EP1731750A3 (en) 2006-12-27
DE59914263D1 (en) 2007-05-03
DE19851286C2 (en) 2001-05-17
EP1731750A2 (en) 2006-12-13
EP0999361A3 (en) 2003-12-10
EP0999361A2 (en) 2000-05-10
EP0999361B1 (en) 2007-03-21
DE59914795D1 (en) 2008-08-07
DE19851286A1 (en) 2000-05-18

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