EP2743492B1 - Piston cylinder unit - Google Patents

Piston cylinder unit Download PDF

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Publication number
EP2743492B1
EP2743492B1 EP13188691.3A EP13188691A EP2743492B1 EP 2743492 B1 EP2743492 B1 EP 2743492B1 EP 13188691 A EP13188691 A EP 13188691A EP 2743492 B1 EP2743492 B1 EP 2743492B1
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EP
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Prior art keywords
piston
cylinder
longitudinal
region
longitudinal depression
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EP13188691.3A
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German (de)
French (fr)
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EP2743492A1 (en
Inventor
Gerd Dornhoefer
David Breuer
Andreas Michalowski
Thomas Kiedrowski
Gernot Repphun
Bernd Schaefer
Sergey Solovyev
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Robert Bosch GmbH
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Robert Bosch GmbH
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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
    • 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
    • F02M59/442—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 means preventing fuel leakage around pump plunger, e.g. fluid barriers

Definitions

  • the invention relates to a piston-cylinder unit and to a method for producing a piston-cylinder unit according to the invention.
  • the piston-cylinder unit is formed in a fuel injector between a nozzle needle and a nozzle needle leading bore of the injector.
  • the grooves formed for lubrication on the nozzle needle in particular have a groove width of between 100 ⁇ m and 500 ⁇ m, and are thus made relatively wide in relation to the diameter of the nozzle needle.
  • the nozzle needle rests against the bore of the injector housing serving as a guide only with a relatively small proportion of its peripheral surface.
  • the EP 0 789 145 A1 shows piston for a compressor with longitudinal recesses, as shown in the Fig. 10 the addressed document, the longitudinal recess of an intermediate portion of the piston, but spaced from the end face of the piston, which faces the side of a lubricant reservoir begins.
  • This piston-cylinder unit has a piston which can be moved back and forth in a bore of the cylinder, on whose peripheral surface a row of radially circumferential transverse grooves and at least two longitudinal grooves extending in the longitudinal direction are formed.
  • the longitudinal grooves are axially in Longitudinal direction of the piston considered by two, in relatively small axial distance from each other arranged transverse grooves separated from each other.
  • the invention is the object of the DE 101 02 234 A1 further develop known piston-cylinder unit such that an optimization of the supply of lubricant to the at least one longitudinal recess is achieved.
  • This object is achieved in a piston-cylinder unit with the features of claim 1, characterized in that the cross-sectional area of the at least one longitudinal recess changes over its axial length, and that the at least one longitudinal recess emanates from an end face of the piston, which has a lubricant reservoir connection.
  • the inlet region of the piston into the cylinder is arranged in each operating position of the piston hydraulically separated from the end region of the at least one longitudinal recess facing away from the first side of the cylinder.
  • the dimensioning of the length of the longitudinal recess is based on the forces introduced into the piston. So usually occur on the piston transverse forces, which leads to a tilting of the piston in the bore of the cylinder. This tilting has the consequence that the surface pressure between the piston and the bore in the cylinder is seen over the circumference of different sizes. In order to avoid that an increased leakage over the area takes place, which has a relatively low load or surface pressure, it is useful or advantageous for such transverse forces, if the length does not reach into the region of the bore or the piston, the has increased or decreased surface pressure.
  • the axial portion of the piston or the bore in the cylinder between the end of the at least one longitudinal recess and the inlet region of the piston is configured in the cylinder such that due to production only leakage losses occur that arise due to manufacturing or due to manufacturing inaccuracies. It should thus be achieved such a fit between the piston and the cylinder that as little or no leakage losses possible occur.
  • no additional longitudinal grooves o.ä. be provided for lubricant management.
  • the cylinder-located portion of the piston and the cooperating surface of the cylinder with the exception of at least one longitudinal recess and production-related surface roughness Well-free surfaces are formed.
  • a plurality of longitudinal recesses are provided, which are arranged at equal angular intervals to each other.
  • the at least one longitudinal recess covers at most 20% of the circumferential surface of the piston in the axial section of the piston, in which the at least one longitudinal depression is arranged.
  • a change in the cross-sectional area can take place via a variation of the groove width.
  • the already mentioned formation of the at least one longitudinal recess by means of a laser beam device proves to be particularly advantageous, since it can be used to produce particularly simple and exactly different groove widths.
  • the depth of the at least one longitudinal recess decreases continuously at least in regions in the end region of the longitudinal depression.
  • an improved or targeted supply of the at least one longitudinal recess with lubricant can take place via a supply bore arranged in the piston in its longitudinal direction, in particular in the form of a blind bore, and a bore which connects the at least one longitudinal recess to the supply bore and hydraulically to the side the cylinder is connected, via which the lubricant supply takes place.
  • Another embodiment of the invention relates to the case of the occurrence of shear forces. Specifically, it may be provided in the context of the invention, on the side facing the inlet region of the cylinder on the piston engages a force which is perpendicular to the longitudinal axis of the piston that by the force in the inlet region of the cylinder facing end portion of the cylinder in a Area is generated with respect to the remaining area of the cylinder increased compressive stress or surface pressure between the piston and the cylinder, and that the at least one Longitudinal recess spaced from the region on the piston ends.
  • Such a design ensures a minimization of leakage losses.
  • the area of the increased compressive stress or surface pressure can be defined by definition as being at least one compressive stress or surface pressure which is 20% or more above the mean value of the compressive stress or surface pressure increased by the force.
  • the invention comprises a method for producing a piston-cylinder unit according to the invention. This is characterized in that the at least one longitudinal recess or groove is generated by a laser beam. Such a manufacturing method allows compliance with the required manufacturing tolerances in an advantageous manner.
  • the piston-cylinder unit 10 comprises a sleeve-shaped in the exemplary embodiment cylinder 11 in the form of a sleeve 12 with a cylindrical through hole 13.
  • a piston 15 In the through hole 13 projects a piston 15 with an end portion 16 into which is reciprocally arranged in the direction of the double arrow 17.
  • the one end face of the cylinder 11 is arranged on the side facing away from the piston 15 in operative connection with a lubricant reservoir 20 located under high pressure.
  • the direction of a transverse force is illustrated by the force F, which acts perpendicular to the longitudinal axis 21 of the piston 15 on the projecting out of the cylinder 11 region of the piston 15, and which acts in addition to a force which is responsible for a movement of the piston 15 in the cylinder in the direction of the double arrow 17.
  • This force F has the consequence that in an area 22 which is located on the opposite side of the force of the piston 15, in the inlet region of the piston 15 in the cylinder 11, an increased compressive stress or surface pressure between the cylinder 11 and the piston 15 occurs , In the exemplary embodiment shown, this region 22 protrudes into the through-bore 13 by approximately one third.
  • the region 22 is also referred to as a support region, wherein the force F causes a tilting of the piston 15 in the through-bore 13 due to the tolerances between the diameter of the piston 15 and the through-bore 13.
  • the piston 15 has on its mantle or circumferential surface 23 at least one, but in particular a plurality of longitudinal grooves 25 arranged at regular angular intervals relative to one another.
  • the longitudinal grooves 25 extend from the one end face 26 of the cylinder 15, which is located on the It is essential that none of the longitudinal grooves 25, which in the illustrated embodiment all have the same length, regardless of the movement of the piston 15 in the direction of the double arrow 17 and the position of the piston 15 extends into the region 22.
  • peripheral surface 23 of the piston 15 at least from the end portions 27 of the longitudinal grooves 25 on the side facing away from the lubricant reservoir 20 to the low pressure region forming inlet portion 28 of the piston 15 in the cylinder 11, with the exception of production-related surface roughness as recess-free surface is trained.
  • the surface of the through hole 13 is formed as deep as possible in the addressed area. Due to the recess-free design of the peripheral surface 23 and the through hole 12 leakage losses between the end portions 27 and the inlet portion 28 should be avoided or minimized as possible, which may occur at a tilting of the cylinder 15 due to the transverse force F in particular on the radially opposite side of the region 22 ,
  • the longitudinal groove 25a corresponding to the illustration of Fig. 2 a semi-circular cross-sectional area.
  • the longitudinal groove 25b of the Fig. 3 on the other hand has a triangular cross-sectional area.
  • the cross-sectional area of the longitudinal groove 25c of Fig. 4 is formed channel-shaped with two obliquely arranged side surfaces.
  • the longitudinal groove 25d is corresponding to Fig. 5 equipped with a rectangular cross section.
  • end portion 27 of the longitudinal grooves 25, 25a to 25d can be configured differently. So one recognizes by the representation of the Fig. 6 a rounded end portion 27a.
  • the end portion 27b corresponding to Fig. 7 In contrast, has a slope 29 which extends from the bottom of the longitudinal groove 25 to the top thereof.
  • the end portion 27c at the longitudinal groove 25 corresponding to Fig. 8 formed without a reduction of the groove depth.
  • the groove width b of the longitudinal groove 25 may be configured differently over the axial length thereof.
  • the longitudinal groove 25e according to the Fig. 9 is the width b of the longitudinal groove 25e over the entire length of the same width.
  • the groove width b of the longitudinal groove 25f in the Fig. 10 different over the axial length thereof, such that the groove width b on the side facing the lubricant reservoir 20 has the greatest width.
  • the groove width b of the longitudinal groove 25g in the Fig. 11 On the other hand, it has varying widths in the longitudinal direction, such that a kind of waist having the smallest width is obtained in a central region of the longitudinal groove 25g.
  • the piston 15 has a running in the longitudinal axis 21, extending from the end face 26 supply bore 30 in the form of a blind hole. Via the supply bore 30 and from the supply bore 30 outgoing transverse bores 31, the longitudinal grooves 25, 25a to 25g seen over the axial length can be targeted and additionally provided with lubricant. It can also be provided that a longitudinal groove 25, 25a to 25g is supplied via a plurality of transverse bores 21 with lubricant.
  • the longitudinal grooves 25, 25a to 25g described so far have a width between 1 ⁇ m and 100 ⁇ m and are preferably produced by a laser beam device or by means of a laser beam.
  • the piston-cylinder unit 10 according to the invention can be modified or modified in many ways without departing from the spirit of the invention. It is preferred but not limited to use in automotive products, particularly pumps, valves or similar components.

Description

Stand der TechnikState of the art

Die Erfindung betrifft eine Kolbenzylindereinheit und ein Verfahren zum Herstellen einer erfindungsgemäßen Kolbenzylindereinheit.The invention relates to a piston-cylinder unit and to a method for producing a piston-cylinder unit according to the invention.

Bei einer aus der DE 101 02 234 A1 der Anmelderin bekannten Kolbenzylindereinheit ist die Kolbenzylindereinheit in einem Kraftstoffinjektor zwischen einer Düsennadel und einem die Düsennadel führenden Bohrung des Injektorgehäuses ausgebildet. Die zur Schmierung an der Düsennadel ausgebildeten Nuten weisen dabei insbesondere eine Nutbreite zwischen 100µm und 500µm auf, und sind somit im Verhältnis zu dem Durchmesser der Düsennadel relativ breit ausgebildet. Dadurch liegt die Düsennadel nur mit einem relativ geringen Anteil ihrer Umfangsfläche an der als Führung dienenden Bohrung des Injektorgehäuses an.At one of the DE 101 02 234 A1 the applicant known piston-cylinder unit, the piston-cylinder unit is formed in a fuel injector between a nozzle needle and a nozzle needle leading bore of the injector. The grooves formed for lubrication on the nozzle needle in particular have a groove width of between 100 μm and 500 μm, and are thus made relatively wide in relation to the diameter of the nozzle needle. As a result, the nozzle needle rests against the bore of the injector housing serving as a guide only with a relatively small proportion of its peripheral surface.

Aus der DE 10 2004 007 513 A1 der Anmelderin ist es darüber hinaus bekannt, an einem Kraftstoff-Einspritzventil Längsvertiefungen vorzusehen, deren Querschnittsfläche sich über die axiale Länge der Längsvertiefung verändert.From the DE 10 2004 007 513 A1 The applicant is also known to provide longitudinal depressions on a fuel injection valve whose cross-sectional area changes over the axial length of the longitudinal recess.

Die EP 0 789 145 A1 zeigt Kolben für einen Verdichter mit Längsvertiefungen, wobei entsprechend der Darstellung der Fig. 10 der angesprochenen Schrift die Längsvertiefung von einem Zwischenbereich des Kolbens, jedoch beabstandet von der Stirnseite des Kolbens, die der Seite eines Schmiermittelreservoirs zugewandt ist, beginnt.The EP 0 789 145 A1 shows piston for a compressor with longitudinal recesses, as shown in the Fig. 10 the addressed document, the longitudinal recess of an intermediate portion of the piston, but spaced from the end face of the piston, which faces the side of a lubricant reservoir begins.

Aus der EP 1 234 975 A2 ist eine weitere Kolbenzylindereinheit bekannt. Diese Kolbenzylindereinheit weist einen in einer Bohrung des Zylinders hin- und herbewegbaren Kolben auf, an dessen Umfangsfläche eine Reihe von radial umlaufenden Quernuten sowie wenigstens zwei, sich in Längsrichtung erstreckende Längsnuten ausgebildet sind. Die Längsnuten sind axial in Längsrichtung des Kolbens betrachtet durch zwei, in relativ geringem axialen Abstand zueinander angeordnete Quernuten voneinander getrennt. Zwischen den beiden Quernuten findet ein gezielter, erhöhter Leckageverlust durch eine entsprechende Geometrie des Kolbens zwischen des beiden Quernuten statt, so dass Schmiermittel, das sich unter hohem Druck im Bereich der einen Seite des Zylinders befindet, über eine in Längsrichtung des Kolbens stattfindende Strömung in den Längsnuten bis zum Austrittsbereich des Kolbens an der anderen Seite des Zylinders gefördert wird. Dadurch wird über die gesamte Länge des Zylinders eine gewünschte Schmierung erzeugt. Nachteilig dabei sind jedoch die relativ hohen Leckageverluste.From the EP 1 234 975 A2 Another piston-cylinder unit is known. This piston-cylinder unit has a piston which can be moved back and forth in a bore of the cylinder, on whose peripheral surface a row of radially circumferential transverse grooves and at least two longitudinal grooves extending in the longitudinal direction are formed. The longitudinal grooves are axially in Longitudinal direction of the piston considered by two, in relatively small axial distance from each other arranged transverse grooves separated from each other. Between the two transverse grooves a targeted, increased leakage loss takes place by a corresponding geometry of the piston between the two transverse grooves, so that lubricant, which is under high pressure in the region of one side of the cylinder, via a taking place in the longitudinal direction of the piston flow in the Longitudinal grooves is conveyed to the exit area of the piston on the other side of the cylinder. This creates a desired lubrication over the entire length of the cylinder. The disadvantage here, however, are the relatively high leakage losses.

Darüber hinaus ist es aus der EP 1 275 864 B1 bekannt, mittels eines Laserstrahls Taschen in eine Kolbenlauffläche einzubringen, die als geschlossene Mikrodruckkammern für ein Schmiermittel dienen. Weiterhin werden die Oberflächen durch Honen so strukturiert, dass ein Netz aus Kanälen entsteht, die zufällig verteilt sind und eine zufällig variierende Tiefe aufweisen. Diese Strukturierung bewirkt ebenfalls eine Reduzierung der Reibung. Eine derartige Strukturierung der Kolbenlauffläche ist relativ aufwendig herzustellen.In addition, it is from the EP 1 275 864 B1 known to introduce by means of a laser beam pockets in a piston running surface, which serve as closed micro-pressure chambers for a lubricant. Furthermore, the surfaces are patterned by honing to form a network of channels that are randomly distributed and have a randomly varying depth. This structuring also causes a reduction in friction. Such structuring of the piston tread is relatively expensive to produce.

Offenbarung der ErfindungDisclosure of the invention

Ausgehend von dem dargestellten Stand der Technik liegt der Erfindung die Aufgabe zugrunde, die aus der DE 101 02 234 A1 bekannte Kolbenzylindereinheit derart weiterzubilden, dass eine Optimierung der Schmiermittelversorgung der wenigstens einen Längsvertiefung erzielt wird. Diese Aufgabe wird erfindungsgemäß bei einer Kolbenzylindereinheit mit den Merkmalen des Anspruchs 1 dadurch gelöst, dass sich die Querschnittsfläche der wenigstens einen Längsvertiefung über deren axiale Länge verändert, und dass die wenigstens eine Längsvertiefung von einer Stirnseite des Kolben ausgeht, die mit einem Schmiermittelreservoir Verbindung hat.Based on the illustrated prior art, the invention is the object of the DE 101 02 234 A1 further develop known piston-cylinder unit such that an optimization of the supply of lubricant to the at least one longitudinal recess is achieved. This object is achieved in a piston-cylinder unit with the features of claim 1, characterized in that the cross-sectional area of the at least one longitudinal recess changes over its axial length, and that the at least one longitudinal recess emanates from an end face of the piston, which has a lubricant reservoir connection.

Ergänzend wird erwähnt, dass wie beim eingangs erwähnten Stand der Technik der Eintrittsbereich des Kolbens in den Zylinder, mit Ausnahme von eventuell auftretenden Leckageverlusten, in jeder Betriebsstellung des Kolbens hydraulisch getrennt von dem der ersten Seite des Zylinders abgewandten Endbereich der wenigstens einen Längsvertiefung angeordnet ist. Mit anderen Worten gesagt bedeutet dies, dass die wenigstens eine Längsvertiefung in einem gewissen Abstand von dem Eintrittsbereich des Kolbens in den Zylinder auf der der Schmiermittelversorgung abgewandten Seite des Zylinders endet.In addition, it is mentioned that, as in the prior art mentioned above, the inlet region of the piston into the cylinder, with the exception of any leakage losses occurring, is arranged in each operating position of the piston hydraulically separated from the end region of the at least one longitudinal recess facing away from the first side of the cylinder. With others In other words, this means that the at least one longitudinal depression ends at a certain distance from the inlet region of the piston into the cylinder on the side of the cylinder facing away from the lubricant supply.

Insbesondere orientiert sich die Dimensionierung der Länge der Längsvertiefung dabei an den in den Kolben eingeleiteten Kräften. So treten üblicherweise auf den Kolben Querkräfte auf, die zu einem Verkippen des Kolbens in der Bohrung des Zylinders führt. Dieses Verkippen hat zur Folge, dass die Flächenpressung zwischen dem Kolben und der Bohrung im Zylinder über den Umfang gesehen unterschiedlich groß ist. Um zu vermeiden, dass eine erhöhte Leckage über den Bereich stattfindet, der eine relativ geringe Belastung bzw. Flächenpressung aufweist, ist es bei derartigen Querkräften sinnvoll bzw. vorteilhaft, wenn die Länge nicht bis in den Bereich der Bohrung bzw. des Kolbens reicht, der eine erhöhte bzw. verringerte Flächenpressung aufweist. Darüber hinaus ist der axiale Abschnitt des Kolbens bzw. der Bohrung im Zylinder zwischen dem Ende der wenigstens einen Längsvertiefung und dem Eintrittsbereich des Kolbens in den Zylinder derart ausgestaltet, dass fertigungsbedingt lediglich Leckageverluste auftreten, die aufgrund der Fertigung bzw. aufgrund von Fertigungsungenauigkeiten entstehen. Es soll somit eine derartige Passung zwischen dem Kolben und dem Zylinder erzielt werden, dass möglichst keine bzw. nur geringe Leckageverluste auftreten. Insbesondere sollen in dem angesprochenen Bereich, im Gegensatz zur Lehre des Stands der Technik, keine zusätzlichen Längsnuten o.ä. zur Schmiermittelführung vorgesehen sein. Vorteilhafte Weiterbildungen der erfindungsgemäßen Kolbenzylindereinheit sind in den Unteransprüchen aufgeführt.In particular, the dimensioning of the length of the longitudinal recess is based on the forces introduced into the piston. So usually occur on the piston transverse forces, which leads to a tilting of the piston in the bore of the cylinder. This tilting has the consequence that the surface pressure between the piston and the bore in the cylinder is seen over the circumference of different sizes. In order to avoid that an increased leakage over the area takes place, which has a relatively low load or surface pressure, it is useful or advantageous for such transverse forces, if the length does not reach into the region of the bore or the piston, the has increased or decreased surface pressure. In addition, the axial portion of the piston or the bore in the cylinder between the end of the at least one longitudinal recess and the inlet region of the piston is configured in the cylinder such that due to production only leakage losses occur that arise due to manufacturing or due to manufacturing inaccuracies. It should thus be achieved such a fit between the piston and the cylinder that as little or no leakage losses possible occur. In particular, in the area mentioned, in contrast to the teaching of the prior art, no additional longitudinal grooves o.ä. be provided for lubricant management. Advantageous developments of the piston-cylinder unit according to the invention are listed in the subclaims.

Zur Minimierung der Leckageverluste in Richtung des Niederdruckbereichs (bezogen auf den Druck des Schmiermittels) ist es darüber hinaus bevorzugt vorgesehen, dass der im Zylinder befindliche Abschnitt des Kolbens sowie die damit zusammenwirkende Fläche des Zylinders, mit Ausnahme der wenigstens einen Längsvertiefung sowie fertigungsbedingter Oberflächenrauhigkeiten, als vertiefungsfreie Oberflächen ausgebildet sind.In order to minimize the leakage losses in the direction of the low-pressure region (based on the pressure of the lubricant), it is furthermore preferably provided that the cylinder-located portion of the piston and the cooperating surface of the cylinder, with the exception of at least one longitudinal recess and production-related surface roughness Well-free surfaces are formed.

Um über den Umfang des Kolbens bzw. der Bohrung eine möglichst gleichmäßige Schmierung zu erzielen, ist es darüber hinaus in einer weiteren Ausgestaltung der Erfindung vorgesehen, dass mehrere Längsvertiefungen vorgesehen sind, die in gleichmäßigen Winkelabständen zueinander angeordnet sind.In order to achieve the most uniform possible lubrication over the circumference of the piston or the bore, it is also provided in a further embodiment of the invention, that a plurality of longitudinal recesses are provided, which are arranged at equal angular intervals to each other.

Darüber hinaus hat es sich für die mechanisch definierte Führung des Kolbens im Zylinder als vorteilhaft erwiesen, dass die wenigstens eine Längsvertiefung maximal 20% der Umfangfläche des Kolbens in dem axialen Abschnitt des Kolbens überdeckt, in dem die wenigstens eine Längsvertiefung angeordnet ist.Moreover, it has proved to be advantageous for the mechanically defined guidance of the piston in the cylinder that the at least one longitudinal recess covers at most 20% of the circumferential surface of the piston in the axial section of the piston, in which the at least one longitudinal depression is arranged.

Insbesondere kann eine Veränderung der Querschnittsfläche über eine Variation der Nutbreite erfolgen. Gerade bei einer Variation der Nutbreite erweist sich das bereits angesprochene Ausbilden der wenigstens einen Längsvertiefung mittels einer Laserstrahleinrichtung als besonders vorteilhaft, da damit besonders einfach und genau unterschiedliche Nutbreiten erzeugt werden können.In particular, a change in the cross-sectional area can take place via a variation of the groove width. Especially with a variation of the groove width, the already mentioned formation of the at least one longitudinal recess by means of a laser beam device proves to be particularly advantageous, since it can be used to produce particularly simple and exactly different groove widths.

Um die Schmierwirkung über die wenigstens eine Längsvertiefung im Endbereich der wenigstens einen Längsvertiefung kontinuierlich ausklingen zu lassen, ist es darüber hinaus in einer weiteren bevorzugten Ausgestaltung der Erfindung vorgesehen, dass die Tiefe der wenigstens einen Längsvertiefung im Endbereich der Längsvertiefung zumindest bereichsweise kontinuierlich abnimmt.In order to allow the lubrication effect to end continuously via the at least one longitudinal recess in the end region of the at least one longitudinal recess, it is additionally provided in a further preferred embodiment of the invention that the depth of the at least one longitudinal recess decreases continuously at least in regions in the end region of the longitudinal depression.

Darüber hinaus kann eine verbesserte bzw. gezielte Versorgung der wenigstens einen Längsvertiefung mit Schmiermittel über eine in dem Kolben in dessen Längsrichtung angeordnete Versorgungsbohrung stattfinden, insbesondere in Form einer Sacklochbohrung, sowie einer die wenigstens eine Längsvertiefung mit der Versorgungsbohrung verbindenden Bohrung, die hydraulisch mit der Seite des Zylinders verbunden ist, über die die Schmiermittelversorgung stattfindet.In addition, an improved or targeted supply of the at least one longitudinal recess with lubricant can take place via a supply bore arranged in the piston in its longitudinal direction, in particular in the form of a blind bore, and a bore which connects the at least one longitudinal recess to the supply bore and hydraulically to the side the cylinder is connected, via which the lubricant supply takes place.

Eine weitere Ausgestaltung der Erfindung betrifft den Fall des Auftretens von Querkräften. Speziell kann es dabei im Rahmen der Erfindung vorgesehen sein, auf der dem Eintrittsbereich zugewandten Seite des Zylinders an dem Kolben eine Kraft angreift, die senkrecht zur Längsachse des Kolbens verläuft, dass durch die Kraft in dem dem Eintrittsbereich des Zylinders zugewandten Endabschnitt des Zylinders in einem Bereich eine gegenüber dem restlichen Bereich des Zylinders erhöhte Druckspannung bzw. Flächenpressung zwischen dem Kolben und dem Zylinder erzeugt wird, und dass die wenigstens eine Längsvertiefung beabstandet zum Bereich an dem Kolben endet. Eine derartige Ausbildung sorgt für eine Minimierung von Leckageverlusten. Dabei liegt es im Rahmen der Erfindung, abhängig von der Höhe der Kraft und der sonstigen Geometrie eine entsprechend erhöhte Druckspannung bzw. Flächenpressung zu definieren, die hinsichtlich des Abstands als relevant angesehen wird. So kann der Bereich der erhöhten Druckspannung bzw. Flächenpressung per Definition zum Beispiel dahingehend definiert werden, dass mindestens eine Druckspannung bzw. Flächenpressung vorhanden ist, die 20% oder mehr über dem Mittelwert der durch die Kraft erhöhten Druckspannung bzw. Flächenpressung beträgt.Another embodiment of the invention relates to the case of the occurrence of shear forces. Specifically, it may be provided in the context of the invention, on the side facing the inlet region of the cylinder on the piston engages a force which is perpendicular to the longitudinal axis of the piston that by the force in the inlet region of the cylinder facing end portion of the cylinder in a Area is generated with respect to the remaining area of the cylinder increased compressive stress or surface pressure between the piston and the cylinder, and that the at least one Longitudinal recess spaced from the region on the piston ends. Such a design ensures a minimization of leakage losses. It is within the scope of the invention, depending on the magnitude of the force and the other geometry to define a correspondingly increased compressive stress or surface pressure, which is considered relevant in terms of distance. For example, the area of the increased compressive stress or surface pressure can be defined by definition as being at least one compressive stress or surface pressure which is 20% or more above the mean value of the compressive stress or surface pressure increased by the force.

Um in allen Betriebsstellungen des Kolbens die Leckageverluste gering zu halten und darüber hinaus etwaige fertigungsbedingte Bauteiltoleranzen zu berücksichtigen, ist es bei der zuletzt beschriebenen Ausgestaltung der Erfindung besonders bevorzugt vorgesehen, dass zwischen dem Bereich der erhöhten Druckspannung bzw. Flächenpressung des Zylinders und dem Endbereich der wenigstens einen Längsvertiefung in allen Stellungen des Kolbens im Zylinder wenigstens ein Abstand von 10% der Länge des Zylinders ausgebildet ist. Auch dieser Wert kann selbstverständlich ggf. im Rahmen der tatsächlich vorhandenen Umstände im Einzelfall erhöht bzw. verringert werden.In order to keep the leakage losses low in all operating positions of the piston and also to take into account any production-related component tolerances, it is particularly preferably provided in the last described embodiment of the invention that between the region of increased compressive stress or surface pressure of the cylinder and the end of the at least a longitudinal recess in all positions of the piston in the cylinder at least a distance of 10% of the length of the cylinder is formed. Of course, this value can of course also be increased or reduced in the individual case in the context of the actual circumstances.

Weiterhin umfasst die Erfindung ein Verfahren zur Herstellung einer erfindungsgemäßen Kolbenzylindereinheit. Dieses zeichnet sich dadurch aus, dass die wenigstens eine Längsvertiefung bzw. Nut durch einen Laserstrahl erzeugt wird. Ein derartiges Fertigungsverfahren ermöglicht in vorteilhafter Art und Weise die Einhaltung der erforderlichen Fertigungstoleranzen.Furthermore, the invention comprises a method for producing a piston-cylinder unit according to the invention. This is characterized in that the at least one longitudinal recess or groove is generated by a laser beam. Such a manufacturing method allows compliance with the required manufacturing tolerances in an advantageous manner.

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der Zeichnung.Further advantages, features and details of the invention will become apparent from the following description of preferred embodiments and from the drawing.

Diese zeigt in:

Fig. 1
einen Längsschnitt durch eine erfindungsgemäße Kolbenzylindereinheit,
Fig. 2 bis Fig. 5
unterschiedliche Querschnitte von Längsnuten in Kolbenoberflächen, in jeweils perspektivischer Ansicht,
Fig. 6 bis Fig. 8
unterschiedliche Auslaufbereiche von Längsnuten, jeweils im Längsschnitt,
Fig. 9 bis Fig. 11
typische Querschnittsverläufe der Längsnuten über deren axiale Länge, in vereinfachten Draufsichten und
Fig. 12
einen abgewandelten Zylinder mit einer Schmiermittelversorgungsbohrung.
This shows in:
Fig. 1
a longitudinal section through a piston-cylinder unit according to the invention,
Fig. 2 to Fig. 5
different cross sections of longitudinal grooves in piston surfaces, in each perspective view,
Fig. 6 to Fig. 8
different outlet areas of longitudinal grooves, each in longitudinal section,
Fig. 9 to Fig. 11
typical cross-sectional profiles of the longitudinal grooves over the axial length, in simplified plan views and
Fig. 12
a modified cylinder with a lubricant supply hole.

Gleiche Elemente bzw. Elemente mit gleicher Funktion sind in den Figuren mit den gleichen Bezugsziffern versehen.The same elements or elements with the same function are provided in the figures with the same reference numerals.

In der Fig. 1 ist eine erfindungsgemäße Kolbenzylindereinheit 10 dargestellt. Die Kolbenzylindereinheit 10 umfasst einen im Ausführungsbeispiel hülsenförmig ausgebildeten Zylinder 11 in Form einer Buchse 12 mit einer zylindrischen Durchgangsbohrung 13. In die Durchgangsbohrung 13 ragt ein Kolben 15 mit einem Endbereich 16 hinein, der in Richtung des Doppelpfeils 17 hin- und herbeweglich angeordnet ist.In the Fig. 1 a piston-cylinder unit 10 according to the invention is shown. The piston-cylinder unit 10 comprises a sleeve-shaped in the exemplary embodiment cylinder 11 in the form of a sleeve 12 with a cylindrical through hole 13. In the through hole 13 projects a piston 15 with an end portion 16 into which is reciprocally arranged in the direction of the double arrow 17.

Die eine Stirnseite des Zylinders 11 ist auf der dem Kolben 15 abgewandten Seite in Wirkverbindung mit einem unter hohem Druck befindlichen Schmiermittelreservoir 20 angeordnet. Über das Schmiermittelreservoir 20 gelangt Schmiermittel in die offene Durchgangsbohrung 13 des Zylinders 11. Darüber hinaus ist durch die Kraft F die Richtung einer Querkraft verdeutlicht, die senkrecht zur Längsachse 21 des Kolbens 15 an dem aus dem Zylinder 11 herausragenden Bereich des Kolbens 15 wirkt, und die zusätzlich zu einer Kraft wirkt, die für eine Bewegung des Kolbens 15 im Zylinder in Richtung des Doppelpfeils 17 verantwortlich ist. Diese Kraft F hat zur Folge, dass in einem Bereich 22, der sich auf der Kraft F gegenüberliegenden Seite des Kolbens 15 befindet, im Eintrittsbereich des Kolbens 15 in den Zylinder 11 eine erhöhte Druckspannung bzw. Flächenpressung zwischen dem Zylinder 11 und dem Kolben 15 auftritt. Dieser Bereich 22 ragt im dargestellten Ausführungsbeispiel in etwa bis zu einem Drittel in die Durchgangsbohrung 13 hinein. Der Bereich 22 wird auch als Tragbereich bezeichnet, wobei durch die Kraft F aufgrund der Toleranzen zwischen dem Durchmesser des Kolbens 15 und der Durchgangsbohrung 13 ein Verkippen des Kolbens 15 in der Durchgangsbohrung 13 bewirkt wird.The one end face of the cylinder 11 is arranged on the side facing away from the piston 15 in operative connection with a lubricant reservoir 20 located under high pressure. In addition, the direction of a transverse force is illustrated by the force F, which acts perpendicular to the longitudinal axis 21 of the piston 15 on the projecting out of the cylinder 11 region of the piston 15, and which acts in addition to a force which is responsible for a movement of the piston 15 in the cylinder in the direction of the double arrow 17. This force F has the consequence that in an area 22 which is located on the opposite side of the force of the piston 15, in the inlet region of the piston 15 in the cylinder 11, an increased compressive stress or surface pressure between the cylinder 11 and the piston 15 occurs , In the exemplary embodiment shown, this region 22 protrudes into the through-bore 13 by approximately one third. The region 22 is also referred to as a support region, wherein the force F causes a tilting of the piston 15 in the through-bore 13 due to the tolerances between the diameter of the piston 15 and the through-bore 13.

Erfindungsgemäß weist der Kolben 15 an seiner Mantel- bzw. Umfangsfläche 23 wenigstens eine, insbesondere jedoch mehrere, in gleichmäßigen Winkelabständen zueinander angeordnete Längsnuten 25 auf. Die Längsnuten 25 reichen von der einen Stirnseite 26 des Zylinders 15, die sich auf der Schmiermittelreservoir 20 zugewandten Seite des Kolbens 15 befindet bis in etwa in dem mittleren Bereich der axialen Erstreckung des Zylinders 11. Wesentlich ist, dass keine der Längsnuten 25, die in dem dargestellten Ausführungsbeispiel alle dieselbe Länge aufweisen, unabhängig von der Bewegung des Kolbens 15 in Richtung des Doppelpfeils 17 bzw. der Stellung des Kolbens 15 bis in den Bereich 22 reicht.According to the invention, the piston 15 has on its mantle or circumferential surface 23 at least one, but in particular a plurality of longitudinal grooves 25 arranged at regular angular intervals relative to one another. The longitudinal grooves 25 extend from the one end face 26 of the cylinder 15, which is located on the It is essential that none of the longitudinal grooves 25, which in the illustrated embodiment all have the same length, regardless of the movement of the piston 15 in the direction of the double arrow 17 and the position of the piston 15 extends into the region 22.

Darüber hinaus ist es vorgesehen, dass die Umfangsfläche 23 des Kolbens 15 zumindest von den Endbereichen 27 der Längsnuten 25 auf der dem Schmiermittelreservoir 20 abgewandten Seite bis zum einen Niederdruckbereich ausbildenden Eintrittsbereich 28 des Kolbens 15 in den Zylinder 11, mit Ausnahme fertigungsbedingter Oberflächenrauhigkeiten als vertiefungsfreie Oberfläche ausgebildet ist. Ebenso ist die Oberfläche der Durchgangsbohrung 13 in dem angesprochenen Bereich möglichst vertiefungsfrei ausgebildet. Durch die vertiefungsfreie Ausbildung der Umfangsfläche 23 sowie der Durchgangsbohrung 12 sollen Leckageverluste zwischen den Endbereichen 27 und dem Eintrittsbereich 28 möglichst vermieden bzw. minimiert werden, die bei einem Verkippen des Zylinders 15 aufgrund der Querkraft F insbesondere auf der dem Bereich 22 radial gegenüberliegenden Seite auftreten können.In addition, it is provided that the peripheral surface 23 of the piston 15 at least from the end portions 27 of the longitudinal grooves 25 on the side facing away from the lubricant reservoir 20 to the low pressure region forming inlet portion 28 of the piston 15 in the cylinder 11, with the exception of production-related surface roughness as recess-free surface is trained. Likewise, the surface of the through hole 13 is formed as deep as possible in the addressed area. Due to the recess-free design of the peripheral surface 23 and the through hole 12 leakage losses between the end portions 27 and the inlet portion 28 should be avoided or minimized as possible, which may occur at a tilting of the cylinder 15 due to the transverse force F in particular on the radially opposite side of the region 22 ,

In den Fig. 2 bis 5 sind unterschiedliche Querschnittsformen der Längsnuten 25 dargestellt. So weist die Längsnut 25a entsprechend der Darstellung der Fig. 2 eine halbkreisförmige Querschnittsfläche auf. Die Längsnut 25b der Fig. 3 weist hingegen eine dreiecksförmige Querschnittsfläche auf. Die Querschnittsfläche der Längsnut 25c der Fig. 4 ist rinnenförmig mit zwei schräg angeordneten Seitenflächen ausgebildet. Zuletzt ist die Längsnut 25d entsprechend der Fig. 5 mit einem rechteckförmigen Querschnitt ausgestattet.In the Fig. 2 to 5 different cross-sectional shapes of the longitudinal grooves 25 are shown. Thus, the longitudinal groove 25a corresponding to the illustration of Fig. 2 a semi-circular cross-sectional area. The longitudinal groove 25b of the Fig. 3 on the other hand has a triangular cross-sectional area. The cross-sectional area of the longitudinal groove 25c of Fig. 4 is formed channel-shaped with two obliquely arranged side surfaces. Lastly, the longitudinal groove 25d is corresponding to Fig. 5 equipped with a rectangular cross section.

Auch der Endbereich 27 der Längsnuten 25, 25a bis 25d kann unterschiedlich ausgestaltet sein. So erkennt man anhand der Darstellung der Fig. 6 einen gerundet ausgebildeten Endbereich 27a. Der Endbereich 27b entsprechend der Fig. 7 weist demgegenüber eine Schräge 29 auf, die vom Grund der Längsnut 25 bis zu deren Oberseite reicht. Zuletzt ist der Endbereich 27c bei der Längsnut 25 entsprechend der Fig. 8 ohne eine Reduzierung der Nuttiefe ausgebildet.Also, the end portion 27 of the longitudinal grooves 25, 25a to 25d can be configured differently. So one recognizes by the representation of the Fig. 6 a rounded end portion 27a. The end portion 27b corresponding to Fig. 7 In contrast, has a slope 29 which extends from the bottom of the longitudinal groove 25 to the top thereof. Finally, the end portion 27c at the longitudinal groove 25 corresponding to Fig. 8 formed without a reduction of the groove depth.

Zuletzt kann auch die Nutbreite b der Längsnut 25 über deren axiale Länge unterschiedlich ausgestaltet sein. Bei der Längsnut 25e entsprechend der Fig. 9 ist die Breite b der Längsnut 25e über deren gesamte Länge gleich breit. Demgegenüber ist die Nutbreite b der Längsnut 25f bei der Fig. 10 über deren axiale Länge unterschiedlich, derart, dass die Nutbreite b auf der dem Schmiermittelreservoir 20 zugewandten Seite die größte Breite aufweist. Die Nutbreite b der Längsnut 25g bei der Fig. 11 weist demgegenüber in Längsrichtung schwankende Breiten auf, derart, dass in einem mittleren Bereich der Längsnut 25g eine Art Taille mit der geringsten Breite erzielt wird. Zusätzlich zur Versorgung der Längsnuten 25, 25a bis 25g über die dem Schmiermittelreservoir 20 zugewandte Stirnseite 26 des Kolbens 15 kann es entsprechend der Fig. 12 vorgesehen sein, dass der Kolben 15 beispielsweise eine in der Längsachse 21 verlaufende, von der Stirnseite 26 ausgehende Versorgungsbohrung 30 in Form einer Sacklochbohrung aufweist. Über die Versorgungsbohrung 30 sowie von der Versorgungsbohrung 30 ausgehende Querbohrungen 31 können die Längsnuten 25, 25a bis 25g über deren axiale Länge gesehen gezielt und zusätzlich mit Schmiermittel versehen werden. Dabei kann es auch vorgesehen sein, dass eine Längsnut 25, 25a bis 25g über mehrere Querbohrungen 21 mit Schmiermittel versorgt wird.Finally, the groove width b of the longitudinal groove 25 may be configured differently over the axial length thereof. In the longitudinal groove 25e according to the Fig. 9 is the width b of the longitudinal groove 25e over the entire length of the same width. In contrast, the groove width b of the longitudinal groove 25f in the Fig. 10 different over the axial length thereof, such that the groove width b on the side facing the lubricant reservoir 20 has the greatest width. The groove width b of the longitudinal groove 25g in the Fig. 11 On the other hand, it has varying widths in the longitudinal direction, such that a kind of waist having the smallest width is obtained in a central region of the longitudinal groove 25g. In addition to the supply of the longitudinal grooves 25, 25a to 25g via the lubricant reservoir 20 facing end face 26 of the piston 15, it may according to the Fig. 12 be provided that the piston 15, for example, has a running in the longitudinal axis 21, extending from the end face 26 supply bore 30 in the form of a blind hole. Via the supply bore 30 and from the supply bore 30 outgoing transverse bores 31, the longitudinal grooves 25, 25a to 25g seen over the axial length can be targeted and additionally provided with lubricant. It can also be provided that a longitudinal groove 25, 25a to 25g is supplied via a plurality of transverse bores 21 with lubricant.

Die soweit beschriebenen Längsnuten 25, 25a bis 25g weisen eine Breite zwischen 1µm und 100µm auf und sind bevorzugt durch eine Laserstrahleinrichtung bzw. mittels eines Laserstrahls erzeugt.The longitudinal grooves 25, 25a to 25g described so far have a width between 1 μm and 100 μm and are preferably produced by a laser beam device or by means of a laser beam.

Die erfindungsgemäße Kolbenzylindereinheit 10 kann in vielfältiger Art und Weise abgewandelt bzw. modifiziert werden, ohne vom Erfindungsgedanken abzuweichen. Sie findet bevorzugt, jedoch nicht einschränkend, Verwendung bei Kraftfahrzeugerzeugnissen, insbesondere bei Pumpen, Ventilen oder ähnlichen Bauteilen.The piston-cylinder unit 10 according to the invention can be modified or modified in many ways without departing from the spirit of the invention. It is preferred but not limited to use in automotive products, particularly pumps, valves or similar components.

Claims (10)

  1. Piston-cylinder unit (10), having a piston (15) which is movable in a bore (13) of a cylinder (11) back and forth along a longitudinal axis (21), wherein the cylinder (11) has a first side at which hydraulically pressurized lubricant for lubricating the surface between the cylinder (11) and the piston (15) is arranged, wherein, on the circumferential surface (23) of the piston (15), there is formed at least one longitudinal depression (25; 25a to 25g) which runs preferably in the direction of the longitudinal axis (21) and which is connected to the lubricant on the first side of the cylinder (11), wherein, axially spaced apart from the other, second side, arranged opposite the first side, of the cylinder (11), the at least one longitudinal depression (25; 25a to 25g) ends on the piston (15) in an end region (27; 27a to 27c), wherein the second side of the cylinder (11) forms an entry region (28) of the piston (15) into the bore (13) of the cylinder (11), wherein the entry region (28) is, in every operating position of the piston (15), hydraulically separated from the end region (27; 27a to 27c), averted from the first side of the cylinder (11), of the at least one longitudinal depression (25; 25a to 25g) aside from possibly occuring leakage losses, wherein the at least one longitudinal depression (25; 25a to 25g) is formed in the manner of a groove and has a groove width (b) between 1 µm and 100 µm,
    characterized
    in that the cross-sectional area of the at least one longitudinal depression (25; 25a to 25g) varies over the axial length thereof, and in that the at least one longitudinal depression (25; 25a to 25e) extends from an end side (26), which has a connection to a lubricant reservoir (20), of the piston (15).
  2. Piston-cylinder unit according to Claim 1,
    characterized
    in that the circumferential surface (23), arranged in the cylinder (11), of the piston (15), and the surface, which interacts with said circumferential surface, of the bore (13) of the cylinder (11) are formed as depression-free surfaces aside from the at least one longitudinal depression (25; 25a to 25g) and manufacturing-induced surface roughnesses.
  3. Piston-cylinder unit according to Claim 1 or 2,
    characterized
    in that multiple longitudinal depressions (25; 25a to 25g) are provided, which are arranged at uniform angular intervals with respect to one another.
  4. Piston-cylinder unit according to any of Claims 1 to 3,
    characterized
    in that the at least one longitudinal depression (25; 25a to 25g) covers at most 20% of the circumferential surface (23) of the piston (15) in that axial portion of the piston (15) in which the at least one longitudinal depression (25; 25a to 25g) is arranged.
  5. Piston-cylinder unit according to Claim 1,
    characterized
    in that the variation of the cross-sectional area of the at least one longitudinal depression (25; 25a to 25g) is realized by means of a variation of the groove width (b).
  6. Piston-cylinder unit according to Claim 1 or 5,
    characterized
    in that the depth of the at least one longitudinal depression (25) decreases in continuous fashion at least in regions in the end region (27a; 27b) of the longitudinal depression (25).
  7. Piston-cylinder unit according to any of Claims 1 to 6,
    characterized
    in that the at least one longitudinal depression (25; 25a to 25g) is, via a feed bore (30), in particular in the form of a blind bore, arranged in the piston (15) in the longitudinal direction thereof, and via a bore (31) which connects the at least one longitudinal depression (25; 25a to 25g) to the feed bore (30), hydraulically connected to that side of the cylinder (11) which is connected to the lubricant.
  8. Piston-cylinder unit according to any of Claims 1 to 7,
    characterized
    in that, on that side of the cylinder (11) which faces towards the inlet region (28), the piston (15) is acted on by a force (F) which runs perpendicular to the longitudinal axis (21), in that, by means of the force (F), in that end portion of the cylinder (11) which faces towards the inlet region (28) of the cylinder (11), in a region (22), an increased compressive stress or contact pressure between the piston (15) and the cylinder (11) is generated in relation to the remaining region of the cylinder (11), and in that the at least one longitudinal depression (25; 25a to 25g) ends on the piston (15) at a distance from the region (22).
  9. Piston-cylinder unit according to Claim 8,
    characterized
    in that, in all positions of the piston (15) in the cylinder (11), at least a distance of 10% of the length of the cylinder (11) is formed between the region (22) of the cylinder (11) and the end region (27; 27a to 27c) of the at least one longitudinal depression (25; 25a to 25g) .
  10. Method for producing a piston-cylinder unit (10) according to any of Claims 1 to 9,
    characterized
    in that the at least one longitudinal depression (25; 25a to 25g) is generated by means of a laser beam.
EP13188691.3A 2012-12-17 2013-10-15 Piston cylinder unit Active EP2743492B1 (en)

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Publication number Priority date Publication date Assignee Title
DE102014218179A1 (en) 2014-09-11 2016-03-17 Robert Bosch Gmbh Axial piston machine and use of an axial piston machine

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DE102004007513A1 (en) * 2004-02-17 2005-09-01 Robert Bosch Gmbh Fuel injection needle valve for combustion engine, with valve seat surrounding aperture in valve body, through which passes valve needle

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DE10102234A1 (en) * 2001-01-19 2002-07-25 Bosch Gmbh Robert High pressure fuel supply unit, for an IC motor with fuel injection, has a drilling through the valve body to take a piston with a sealing section against the guide section of the drilling, with a hydraulic piston centering action
KR100773437B1 (en) * 2001-02-26 2007-11-05 베르트질레 슈바이츠 악티엔게젤샤프트 A high pressure piston in cylinder unit
EP1275864B2 (en) 2001-07-09 2010-10-27 Gehring Technologies GmbH Workpiece with a tribologically stressed surface and method of manufacture such a surface
DE102006016702A1 (en) * 2006-04-08 2007-10-18 Man Diesel Se Piston pump for supplying fuel in fuel injection system of internal-combustion engine, has recesses provided in guiding area between pump cylinder and pump piston, where fuel is supplied into recesses in axial direction
DE102006040468A1 (en) * 2006-08-29 2008-03-06 Man Diesel Se Lubricating piston pump for fuel injection device, particularly for application in common rail fuel injection device of internal combustion engine, pump housing in which pump cylinder is formed, and recess is provided in guiding area

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EP0789145A1 (en) * 1995-06-05 1997-08-13 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Piston for a compressor and piston-type compressor
DE102004007513A1 (en) * 2004-02-17 2005-09-01 Robert Bosch Gmbh Fuel injection needle valve for combustion engine, with valve seat surrounding aperture in valve body, through which passes valve needle

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CN103867711A (en) 2014-06-18
CN103867711B (en) 2017-11-21
EP2743492A1 (en) 2014-06-18

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