EP1700028A1 - Valve arrangement in particular inlet valve for a high pressure fuel pump - Google Patents

Valve arrangement in particular inlet valve for a high pressure fuel pump

Info

Publication number
EP1700028A1
EP1700028A1 EP04802632A EP04802632A EP1700028A1 EP 1700028 A1 EP1700028 A1 EP 1700028A1 EP 04802632 A EP04802632 A EP 04802632A EP 04802632 A EP04802632 A EP 04802632A EP 1700028 A1 EP1700028 A1 EP 1700028A1
Authority
EP
European Patent Office
Prior art keywords
channel section
valve
channel
valve arrangement
longitudinal axis
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP04802632A
Other languages
German (de)
French (fr)
Other versions
EP1700028B1 (en
Inventor
Ulrich Maier
Sascha Ambrock
Peter Bauer
Achim Koehler
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1700028A1 publication Critical patent/EP1700028A1/en
Application granted granted Critical
Publication of EP1700028B1 publication Critical patent/EP1700028B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/04—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • 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
    • 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
    • F02M59/46—Valves
    • F02M59/462—Delivery valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/001—Noise damping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/06—Venting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • 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
    • F02M2200/04—Fuel-injection apparatus having means for avoiding effect of cavitation, e.g. erosion
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/206—Flow affected by fluid contact, energy field or coanda effect [e.g., pure fluid device or system]
    • Y10T137/2087—Means to cause rotational flow of fluid [e.g., vortex generator]

Definitions

  • the invention relates to a valve arrangement, in particular an inlet valve arrangement of a high-pressure fuel pump, with a valve element arranged in a valve chamber and a fluid channel adjoining the valve chamber upstream.
  • the object of the present invention is a valve arrangement of the type mentioned to further develop that it works with as little loss as possible and, as a result, the efficiency, for example of a high-pressure fuel pump, in which the valve arrangement is used, is improved.
  • Opening time of the valve element leads to a greater throughput.
  • the length of the fluid channel can also be shorter, which overall reduces the size of the valve arrangement and, for example, a fuel pump in which it is used. Due to the swirling flow otherwise existing highly unsteady turbulent flow processes (pulse-like speed profile) is reduced or completely prevented, which reduces the load on the fluid channel and a region located further upstream. For example, a feed pump that supplies the fluid to the valve arrangement is also protected.
  • valve element Due to the even flow in the fluid channel, the valve element itself is evenly flowed around and remains in the center even in the open state of suspension, which means that there is no transverse force on the valve due to a fluid flowing past on one side. This also leads to an improvement in the efficiency of the valve arrangement and to a reduction in wear on the valve element.
  • the fluid channel comprises a first channel section and a second channel section adjoining it, the longitudinal axes of the channel sections being at an angle of ⁇ 180 ° to one another, and the longitudinal axis of the first channel section being laterally offset from the longitudinal axis of the second channel section.
  • the rotation of the flow in the second channel section is caused in a simple manner by the lateral offset. Turbulence generated due to the kink between the two channel sections is effectively smoothed out, or such turbulence cannot arise at all.
  • valve arrangement comprises a ball or a cone element as a valve element.
  • a particularly preferred embodiment of the valve arrangement according to the invention is characterized in that the two channel sections have at least approximately the same radius in cross section and that the lateral offset of the longitudinal axes is greater than the radius. This simplifies the manufacture of the valve arrangement according to the invention and thus lowers the manufacturing costs, since the same drilling tool can be used for both channel sections.
  • a transition area between the first channel section and the second channel section be machined by means of electrochemical material removal. This enables a largely edge-free transition from one channel section to the other channel section, which is also favorable for a uniform flow.
  • the transition area comprises a wall curved from the first to the second channel section. This leads to a particularly smooth flow in which little turbulence occurs. It is also particularly preferred if the first channel section does not extend axially or not significantly beyond the second channel section. As a result, the dynamic pressure upstream of the deflection from the first channel section to the second channel section is reduced, which further reduces the flow resistance and improves the overall efficiency of the valve arrangement in terms of flow technology.
  • the longitudinal axis of the first channel section and the longitudinal axis of the second channel section enclose an angle> 90 °. This leads to an additional reduction in resistance.
  • Figure 1 is a schematic representation of an internal combustion engine with a high pressure fuel pump
  • FIG. 5 shows a section along the line VV of Figure 4;
  • Figure 6 is a section along the line VI-VI of Figure 4;
  • FIG. 8 shows a representation similar to FIG. 3 of a modified embodiment of a housing of the high-pressure fuel pump from FIG. 1.
  • An internal combustion engine bears the overall reference number 10 in FIG. 1. It comprises a fuel tank 12, from which a prefeed pump 14 converts the fuel to one
  • High pressure fuel pump 16 promotes. This compresses the fuel to a very high pressure and delivers it to a fuel collecting line 18 (“rail”), in which the fuel is stored under high pressure. A plurality of injectors 20 are connected to these and inject the fuel directly into combustion chambers 22 assigned to them.
  • a housing 24 of the high-pressure fuel pump 16 is shown in greater detail in FIGS. 2 and 3. It comprises three cylinders 26a, 2 ⁇ b, and 26c, which are constructed essentially identically. For the sake of simplicity, only the cylinder 26a is referred to below.
  • a piston bore 28 is present in the cylinder 26a, in which a piston, not shown, is accommodated in a longitudinally displaceable manner.
  • the piston bore 28 can be connected to a fuel inlet 32 via a fluid channel 30.
  • the fuel inlet 32 is in turn connected to the prefeed pump 14.
  • the fluid channel 28 is divided into two channel sections 34 and 36.
  • the first duct section 34 extends at an angle from an inlet duct (without reference number), which in turn leads away from a fuel inlet 32. To the outside, the first channel section 34 is blocked by a ball that is not provided with reference symbols.
  • Its longitudinal axis 38 runs perpendicular to the longitudinal axis 40 of the piston bore 28 and of the second channel section 36 (see FIG. 3). However, the two longitudinal axes 38 and 40 do not intersect. As especially from the
  • the longitudinal axis 38 of the first channel section 34 is instead laterally offset with respect to the longitudinal axis 40 of the second channel section 36.
  • the lateral offset is designated by V in FIGS. 6 and 7.
  • the two channel sections 38 and 40 have the same radius, which is greater than the lateral offset V of the two longitudinal axes 38 and 40.
  • a valve chamber 42 is present between the second channel section 36 of the fluid channel 30 and the piston bore 28. Between the valve chamber 42 and the second channel section 36, a shoulder is formed, which forms a valve seat 44 for a valve ball 46, which in the Valve chamber 42 is received (see Figures 4 and 5). The valve ball 46 is urged against the valve seat 44 by a spring, not shown in the drawing. A delivery chamber 47 connects to the valve chamber 42. As can also be seen in particular from FIG. 7, the first channel section 34 hardly extends beyond the second channel section 36. The fluid channel 30, the valve seat 44 and the valve ball 46 overall form a valve arrangement 47.
  • the high-pressure fuel pump 16 operates as follows (again, only the cylinder 26a is referred to here):
  • the fuel passes from the first channel section 34 into the second channel section 36. It experiences a change in direction of 90 °. Due to the lateral movement component 48, however, the fluid flow in the second channel section 36 additionally results in a rotary movement about the longitudinal axis 40 of the second Channel section 36 a. This rotary movement is also referred to as "swirl" or “spin” and bears the reference symbol 50 in FIGS. 6 and 7.
  • the swirl 50 prevents the fluid flow in the transition region between the first channel section 34 and the second channel section 36 from changing Flow detaches, which would lead to increased flow resistance and the risk of cavitation and corresponding wear.
  • the swirl 50 also causes the valve ball 46 to rotate in the open state, so that it wears evenly.
  • their sealing effect and that of the valve seat 44 is retained over a very long period of time. Since separation of the fuel flow in the transition area between the two channel sections 34 and 36 and in particular in the second channel section 36 is prevented, there is also no constriction of the fluid flow with a correspondingly reduced hydraulic diameter, which would lead to increased throttling.
  • FIG. 8 An alternative embodiment is shown in FIG. 8. Elements and areas which have functions equivalent to elements and areas of the previous figures have the same reference numerals. They are not explained in detail again.
  • the longitudinal axis 38 of the first channel section 34 is not at an angle of 90 °, but at an angle of approximately 45 ° to the longitudinal axis 40 of the second channel section 36. less drag flow realized.

Landscapes

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

Abstract

A valve arrangement (47), for a high-pressure fuel pump (16), comprises a valve element (46), arranged in a valve chamber (42) and a fluid channel (30), contiguous with the valve chamber (42) upstream thereof. According to the invention, the fluid channel (30) is embodied such that the fluid flow entering the valve chamber (42) is at least partly forced to undergo a rotation about a longitudinal axis (40) of the fluid channel (30) (swirl).

Description

Ventilanordnung, insbesondere Einlassventil einer Hochdruck-KraftstoffpumpeValve arrangement, in particular inlet valve of a high-pressure fuel pump
Stand der TechnikState of the art
Die Erfindung betrifft eine Ventilanordnung, insbesondere eine Einlassventilanordnung einer Hochdruck- Kraftstoffpumpe, mit einem in einer Ventilkammer angeordneten Ventilelement und einem stromaufwärts an die Ventilkammer angrenzenden Fluidkanal.The invention relates to a valve arrangement, in particular an inlet valve arrangement of a high-pressure fuel pump, with a valve element arranged in a valve chamber and a fluid channel adjoining the valve chamber upstream.
Eine Ventilanordnung der eingangs genannten Art ist vom Markt her bekannt. Sie kommt beispielsweise bei einer Hochdruck-Kraftstoffpumpe eines Common-Rail- Einspritzsystems zum Einsatz. Eine solche Hochdruck- Kraftstoff umpe ist als Kolbenpumpe ausgeführt. Als Einlassventil zu einem Förderraum hin ist ein Kugel- Rückschlagventil vorgesehen. Die Kugel desA valve arrangement of the type mentioned is known from the market. It is used, for example, in a high-pressure fuel pump of a common rail injection system. Such high pressure fuel umpe is designed as a piston pump. A ball check valve is provided as an inlet valve to a delivery chamber. The ball of the
Rückschlagventils ist in einer Ventilkammer angeordnet, in die eine Zulaufbohrung mündet. Die Zulaufbohrung umfasst einen ersten Kanalabschnitt, der im Wesentlichen senkrecht zur Längsachse eines Kolbens der Kolbenpumpe liegt, sowie einen zweiten Kanalabschnitt, der koaxial zur Längsachse des Kolbens der Kolbenpumpe liegt. Die Längsachsen der beiden Kanalabschnitte schneiden sich in einem Verschneidungsbereich. In diesem Verschneidungsbereich kommt es im Betrieb der Kolbenpumpe zu einer scharfkantigen Umlenkung des dem Einlassventil zuströmenden Kraftstoffes.Check valve is arranged in a valve chamber into which an inlet bore opens. The inlet bore comprises a first channel section which is essentially perpendicular to the longitudinal axis of a piston of the piston pump, and a second channel section which is coaxial to the longitudinal axis of the piston of the piston pump. The longitudinal axes of the two channel sections intersect in an intersection area. In this intersection area, there is a sharp-edged deflection of the fuel flowing to the inlet valve during operation of the piston pump.
Aufgabe der vorliegenden Erfindung ist es, eine Ventilanordnung der eingangs genannten Art so weiterzubilden, dass sie möglichst verlustarm arbeitet und hierdurch der Wirkungsgrad beispielsweise einer Hochdruck- Kraftstoffpumpe, bei welcher die Ventilanordnung eingesetzt wird, besser wird.The object of the present invention is a valve arrangement of the type mentioned to further develop that it works with as little loss as possible and, as a result, the efficiency, for example of a high-pressure fuel pump, in which the valve arrangement is used, is improved.
Diese Aufgabe wird bei einer Ventilanordnung der eingangs genannten Art dadurch gelöst, dass der Fluidkanal so ausgebildet ist, dass dem Fluidstrom, welcher der Ventilkammer zuströmt, eine Rotation um die Längsachse des Fluidkanals (Drall) aufgeprägt wird.This object is achieved in a valve arrangement of the type mentioned at the outset in that the fluid channel is designed in such a way that a rotation about the longitudinal axis of the fluid channel (swirl) is impressed on the fluid flow which flows into the valve chamber.
Vorteile der ErfindungAdvantages of the invention
Die der Strömung aufgeprägte Rotation ("Drall" oder "Spin") führt zu Fliehkräften, durch welche die Strömung an die Wand gedrückt wird. Auf diese Weise wird verhindert, dass sich der Fluidstrom von der Wand des Fluidkanals beispielsweise bei einer Richtungsänderung unter Bildung eines entsprechenden Unterdruckgebietes löst. Hierdurch wird der Staudruck im Umlenkungsbereich vermindert und der Strömungswiderstand gesenkt. Kavitationsschäden im Fluidkanal werden ferner vermieden. Aufgrund der an der Wand des Fluidkanals anliegenden Fluidströmung ist der Fluidkanal gleichmäßig gefüllt, was bei gleicherThe rotation imposed on the flow ("swirl" or "spin") leads to centrifugal forces, by means of which the flow is pressed against the wall. In this way it is prevented that the fluid flow separates from the wall of the fluid channel, for example in the event of a change of direction, with the formation of a corresponding vacuum region. As a result, the dynamic pressure in the deflection area is reduced and the flow resistance is reduced. Cavitation damage in the fluid channel is also avoided. Due to the fluid flow applied to the wall of the fluid channel, the fluid channel is filled uniformly, which is the same
Öffnungsdauer des Ventilelements zu einem größeren Durchsatz führt.Opening time of the valve element leads to a greater throughput.
Aufgrund der jederzeit anliegenden Strömung kann darüber hinaus die Länge des Fluidkanals geringer ausfallen, was insgesamt die Baugröße der Ventilanordnung und beispielsweise einer Kraftstoffpumpe, in welcher diese zum Einsatz kommt, reduziert. Durch die drallbehaftete Strömung werden sonst vorhandene stark instationäre turbulente Strömungsvorgänge (pulsartiges Geschwindigkeitsprofil) vermindert beziehungsweise vollständig verhindert, was die Belastung des Fluidkanals und eines weiter stromaufwärts gelegenen Bereichs vermindert. So wird beispielsweise eine Zuführpumpe, welche das Fluid der Ventilanordnung zuleitet, ebenfalls geschont.Due to the flow at all times, the length of the fluid channel can also be shorter, which overall reduces the size of the valve arrangement and, for example, a fuel pump in which it is used. Due to the swirling flow otherwise existing highly unsteady turbulent flow processes (pulse-like speed profile) is reduced or completely prevented, which reduces the load on the fluid channel and a region located further upstream. For example, a feed pump that supplies the fluid to the valve arrangement is also protected.
Durch die vergleichmäßigte Strömung im Fluidkanal wird auch das Ventilelement selbst gleichmäßig umströmt und bleibt so auch im geöffneten Schwebezustand mittig, das heißt es entsteht keine Querkraft auf das Ventil durch ein einseitig vorbeifließendes Fluid. Dies führt ebenfalls zu einer Wirkungsgradverbesserung der Ventilanordnung und zu einer Minderung des Verschleißes am Ventilelement.Due to the even flow in the fluid channel, the valve element itself is evenly flowed around and remains in the center even in the open state of suspension, which means that there is no transverse force on the valve due to a fluid flowing past on one side. This also leads to an improvement in the efficiency of the valve arrangement and to a reduction in wear on the valve element.
Vorteilhafte Weiterbildungen der Erfindung sind in Unteransprüchen angegeben.Advantageous developments of the invention are specified in the subclaims.
Zunächst wird vorgeschlagen, dass der Fluidkanal einen ersten Kanalabschnitt und einen an diesen anschließenden zweiten Kanalabschnitt umfasst, wobei die Längsachsen der Kanalabschnitte zueinander in einem Winkel < 180° stehen, und wobei die Längsachse des ersten Kanalabschnitts gegenüber der Längsachse des zweiten Kanalabschnitts seitlich versetzt ist. Durch den seitlichen Versatz wird die Rotation der Strömung im zweiten Kanalabschnitt auf einfache Weise hervorgerufen. Aufgrund des Knicks zwischen den beiden Kanalabschnitten erzeugte Turbulenzen werden so wirkungsvoll geglättet, oder derartige Turbulenzen können erst gar nicht entstehen.First, it is proposed that the fluid channel comprises a first channel section and a second channel section adjoining it, the longitudinal axes of the channel sections being at an angle of <180 ° to one another, and the longitudinal axis of the first channel section being laterally offset from the longitudinal axis of the second channel section. The rotation of the flow in the second channel section is caused in a simple manner by the lateral offset. Turbulence generated due to the kink between the two channel sections is effectively smoothed out, or such turbulence cannot arise at all.
Besonders deutlich ist die Rotation dann, wenn die Längsachsen der beiden Kanalabschnitte wenigstens in etwa in einem rechten Winkel zueinander stehen. In diesem Fall ist der der Strömung im zweiten Kanalabschnitt aufgeprägte Drall am stärksten, und daher sind die mit der erfindungsgemäßen Ventilanordnung erzielbaren Vorteile am größten.The rotation is particularly clear when the longitudinal axes of the two channel sections are at least approximately at right angles to one another. In this case, the swirl imparted to the flow in the second channel section is strongest, and therefore those with the Advantages achievable valve assembly according to the invention greatest.
Vorgeschlagen wird auch, dass die Ventilanordnung als Ventilelement eine Kugel oder ein Kegelelement umfasst.It is also proposed that the valve arrangement comprises a ball or a cone element as a valve element.
Aufgrund der Drehbewegung des der Ventilkammer zuströmenden Fluids werden auch diese rotationssymmetrischen Ventilelemente in Drehung versetzt. Dies verhindert einen einseitigen Verschleiß an diesen Ventilelementen und erhöht die Dauerhaltbarkeit eines dem Ventilelement zugeordneten Ventilsitzes.Due to the rotational movement of the fluid flowing to the valve chamber, these rotationally symmetrical valve elements are also set in rotation. This prevents one-sided wear on these valve elements and increases the durability of a valve seat assigned to the valve element.
Eine besonders bevorzugte Ausgestaltung der erfindungsgemäßen Ventilanordnung zeichnet sich dadurch aus, dass beide Kanalabschnitte im Querschnitt wenigstens in etwa den gleichen Radius aufweisen und dass der seitliche Versatz der Längsachsen größer ist als der Radius. Dies vereinfacht die Herstellung der erfindungsgemäßen Ventilanordnung und senkt somit die Herstellkosten, da für beide Kanalabschnitte das gleiche Bohrwerkzeug verwendet werden kann.A particularly preferred embodiment of the valve arrangement according to the invention is characterized in that the two channel sections have at least approximately the same radius in cross section and that the lateral offset of the longitudinal axes is greater than the radius. This simplifies the manufacture of the valve arrangement according to the invention and thus lowers the manufacturing costs, since the same drilling tool can be used for both channel sections.
Vorgeschlagen wird auch, dass ein Übergangsbereich zwischen dem ersten Kanalabschnitt und dem zweiten Kanalabschnitt mittels elektrochemischen Materialabtrags bearbeitet ist. Dies ermöglicht einen weitgehend kantenfreien Übergang von einem Kanalabschnitt zum anderen Kanalabschnitt, was für eine gleichmäßige Strömung ebenfalls günstig ist.It is also proposed that a transition area between the first channel section and the second channel section be machined by means of electrochemical material removal. This enables a largely edge-free transition from one channel section to the other channel section, which is also favorable for a uniform flow.
Dabei wird besonders bevorzugt, wenn der Übergangsbereich eine vom ersten zum zweiten Kanalabschnitt gekrümmte Wand umfasst. Dies führt zu einer besonders glatten Strömung, in der wenig Turbulenzen auftreten. Besonders bevorzugt ist auch, wenn sich der erste Kanalabschnitt axial nicht oder nicht wesentlich über den zweiten Kanalabschnitt hinaus erstreckt. Hierdurch wird der Staudruck stromaufwärts von der Umlenkung vom ersten Kanalabschnitt zum zweiten Kanalabschnitt gesenkt, was den Strömungswiderstand nochmals reduziert und den Wirkungsgrad der Ventilanordnung insgesamt in strömungstechnischer Hinsicht verbessert.It is particularly preferred if the transition area comprises a wall curved from the first to the second channel section. This leads to a particularly smooth flow in which little turbulence occurs. It is also particularly preferred if the first channel section does not extend axially or not significantly beyond the second channel section. As a result, the dynamic pressure upstream of the deflection from the first channel section to the second channel section is reduced, which further reduces the flow resistance and improves the overall efficiency of the valve arrangement in terms of flow technology.
Möglich ist ferner, dass die Längsachse des ersten Kanalabschnitts und die Längsachse des zweiten Kanalabschnitts einen Winkel > 90° einschließen. Dies führt zu einer zusätzlichen Widerstandsreduzierung.It is also possible that the longitudinal axis of the first channel section and the longitudinal axis of the second channel section enclose an angle> 90 °. This leads to an additional reduction in resistance.
Zeichnungdrawing
Nachfolgend wird ein besonders bevorzugtes Ausführungsbeispiel der vorliegenden Erfindung unter Bezugnahme auf die beiliegende Zeichnung näher erläutert. In der Zeichnung zeigen:A particularly preferred exemplary embodiment of the present invention is explained in more detail below with reference to the accompanying drawing. The drawing shows:
Figur 1 eine schematische Darstellung einer Brennkraftmaschine mit einer Hochdruck- Kraftstoffpumpe;Figure 1 is a schematic representation of an internal combustion engine with a high pressure fuel pump;
Figur 2 einen Schnitt durch ein Gehäuse der Hochdruck- Kraftstoffpumpe von Figur 1;FIG. 2 shows a section through a housing of the high-pressure fuel pump from FIG. 1;
Figur 3 einen Schnitt längs der Linie III-III von Figur 2;3 shows a section along the line III-III of Figure 2;
Figur 4 ein Detail IV von Figur 2;Figure 4 shows a detail IV of Figure 2;
Figur 5 einen Schnitt längs der Linie V-V von Figur 4; Figur 6 einen Schnitt längs der Linie VI-VI von Figur 4;5 shows a section along the line VV of Figure 4; Figure 6 is a section along the line VI-VI of Figure 4;
Figur 7 einen Schnitt längs der Linie VII-VII von Figur 6; und7 shows a section along the line VII-VII of Figure 6; and
Figur 8 eine Darstellung ähnlich Figur 3 einer abgewandelten Ausführungsform eines Gehäuses der Hochdruck-Kraftstoffpumpe von Figur 1.FIG. 8 shows a representation similar to FIG. 3 of a modified embodiment of a housing of the high-pressure fuel pump from FIG. 1.
Beschreibung der AusführungsbeispieleDescription of the embodiments
Eine Brennkraftmaschine trägt in Figur 1 insgesamt das Bezugszeichen 10. Sie umfasst einen Kraftstoffbehälter 12, aus dem eine Vorförderpumpe 14 den Kraftstoff zu einerAn internal combustion engine bears the overall reference number 10 in FIG. 1. It comprises a fuel tank 12, from which a prefeed pump 14 converts the fuel to one
Hochdruck-Kraftstoffpumpe 16 fördert. Diese komprimiert den Kraftstoff auf einen sehr hohen Druck und fördert ihn zu einer Kraftstoff-Sammelleitung 18 ("Rail"), in der der Kraftstoff unter hohem Druck gespeichert ist. An diese sind mehrere Injektoren 20 angeschlossen, die den Kraftstoff direkt in ihnen zugeordnete Brennräume 22 einspritzen.High pressure fuel pump 16 promotes. This compresses the fuel to a very high pressure and delivers it to a fuel collecting line 18 (“rail”), in which the fuel is stored under high pressure. A plurality of injectors 20 are connected to these and inject the fuel directly into combustion chambers 22 assigned to them.
Ein Gehäuse 24 der Hochdruck-Kraftstoffpumpe 16 ist in den Figuren 2 und 3 stärker im Detail dargestellt. Es umfasst drei Zylinder 26a, 2βb, und 26c, welche im Wesentlichen identisch aufgebaut sind. Der Einfachheit halber wird nachfolgend nur auf den Zylinder 26a Bezug genommen.A housing 24 of the high-pressure fuel pump 16 is shown in greater detail in FIGS. 2 and 3. It comprises three cylinders 26a, 2βb, and 26c, which are constructed essentially identically. For the sake of simplicity, only the cylinder 26a is referred to below.
Im Zylinder 26a ist eine Kolbenbohrung 28 vorhanden, in welcher ein nicht gezeigter Kolben längsverschieblich aufgenommen ist. Über einen Fluidkanal 30 ist die Kolbenbohrung 28 mit einem Kraftstoff-Einlass 32 verbindbar. Der Kraftstoff-Einlass 32 ist wiederum mit der Vorförderpumpe 14 verbunden. Der Fluidkanal 28 ist in zwei Kanalabschnitte 34 und 36 unterteilt. Der erste Kanalabschnitt 34 geht unter einem Winkel von einem Einlasskanal (ohne Bezugszeichen) ab, der wiederum von einem Kraftstoff-Einlass 32 wegführt. Nach außen hin ist der erste Kanalabschnitt 34 durch eine nicht mit Bezugszeichen versehen Kugel verstopft. Seine Längsachse 38 verläuft senkrecht zur Längsachse 40 der Kolbenbohrung 28 und des zweiten Kanalabschnitts 36 (vergleiche Figur 3) . Die beiden Längsachsen 38 und 40 schneiden sich jedoch nicht. Wie insbesondere aus denA piston bore 28 is present in the cylinder 26a, in which a piston, not shown, is accommodated in a longitudinally displaceable manner. The piston bore 28 can be connected to a fuel inlet 32 via a fluid channel 30. The fuel inlet 32 is in turn connected to the prefeed pump 14. The fluid channel 28 is divided into two channel sections 34 and 36. The first duct section 34 extends at an angle from an inlet duct (without reference number), which in turn leads away from a fuel inlet 32. To the outside, the first channel section 34 is blocked by a ball that is not provided with reference symbols. Its longitudinal axis 38 runs perpendicular to the longitudinal axis 40 of the piston bore 28 and of the second channel section 36 (see FIG. 3). However, the two longitudinal axes 38 and 40 do not intersect. As especially from the
Figuren 2 und 4 sowie 6 und 7 hervorgeht, ist stattdessen die Längsachse 38 des ersten Kanalabschnitts 34 gegenüber der Längsachse 40 des zweiten Kanalabschnitts 36 seitlich versetzt. Der seitliche Versatz ist in den Figuren 6 und 7 mit V bezeichnet. Die beiden Kanalabschnitte 38 und 40 haben im Querschnitt den gleichen Radius, welcher größer ist als der seitliche Versatz V der beiden Längsachsen 38 und 40.2 and 4 and 6 and 7, the longitudinal axis 38 of the first channel section 34 is instead laterally offset with respect to the longitudinal axis 40 of the second channel section 36. The lateral offset is designated by V in FIGS. 6 and 7. In cross section, the two channel sections 38 and 40 have the same radius, which is greater than the lateral offset V of the two longitudinal axes 38 and 40.
Wie insbesondere aus Figur 6 hervorgeht, ist in einemAs can be seen in particular from FIG. 6, in one
Übergangsbereich zwischen dem ersten Kanalabschnitt 34 und dem zweiten Kanalabschnitt 36 eine vom ersten Kanalabschnitt 34 zum zweiten Kanalabschnitt 36 hin gekrümmte Wandfläche 41 vorhanden. Diese ist mittels elektrochemischen Materialabtrags eingearbeitet. Durch diese geht die in der Schnittebene von Figur 6 radial äußere Wand des Kanalabschnitts 34 ohne Knick oder Kante in den entsprechenden Wandabschnitt des Kanalabschnitts 36 über.Transition area between the first channel section 34 and the second channel section 36 there is a wall surface 41 curved from the first channel section 34 to the second channel section 36. This is incorporated by means of electrochemical material removal. Through this, the radially outer wall of the channel section 34 in the sectional plane of FIG. 6 merges into the corresponding wall section of the channel section 36 without a kink or edge.
Zwischen dem zweiten Kanalabschnitt 36 des Fluidkanals 30 und der Kolbenbohrung 28 ist eine Ventilkammer 42 vorhanden. Zwischen der Ventilkammer 42 und dem zweiten Kanalabschnitt 36 ist ein Absatz ausgebildet, welcher einen Ventilsitz 44 für eine Ventilkugel 46 bildet, die in der Ventilkammer 42 aufgenommen ist (vergleiche Figuren 4 und 5) . Die Ventilkugel 46 wird von einer in der Zeichnung nicht gezeigten Feder gegen den Ventilsitz 44 beaufschlagt. An die Ventilkammer 42 schließt sich ein Förderraum 47 an. Wie insbesondere auch aus Figur 7 ersichtlich ist, erstreckt sich der erste Kanalabschnitt 34 kaum über den zweiten Kanalabschnitt 36 hinaus. Der Fluidkanal 30, der Ventilsitz 44 und die Ventilkugel 46 bilden insgesamt eine Ventilanordnung 47.A valve chamber 42 is present between the second channel section 36 of the fluid channel 30 and the piston bore 28. Between the valve chamber 42 and the second channel section 36, a shoulder is formed, which forms a valve seat 44 for a valve ball 46, which in the Valve chamber 42 is received (see Figures 4 and 5). The valve ball 46 is urged against the valve seat 44 by a spring, not shown in the drawing. A delivery chamber 47 connects to the valve chamber 42. As can also be seen in particular from FIG. 7, the first channel section 34 hardly extends beyond the second channel section 36. The fluid channel 30, the valve seat 44 and the valve ball 46 overall form a valve arrangement 47.
Die Hochdruck-Kraftstoffpumpe 16 arbeitet folgendermaßen (auch hier wird wiederum nur auf den Zylinder 26a Bezug genommen) :The high-pressure fuel pump 16 operates as follows (again, only the cylinder 26a is referred to here):
Bei einem Saughub des Kolbens hebt die Ventilkugel 46 vom Ventilsitz 44 ab. Kraftstoff strömt nun von der Vorförderpumpe 14 über den Kraftsto f-Einlass 32, den ersten Kanalabschnitt 34, den zweiten Kanalabschnitt 36, und durch den Spalt zwischen Ventilkugel 46 und Ventilsitz 44 hindurch in die Ventilkammer 42 und weiter in den Förderraum 47. Aufgrund des Versatzes V zwischen der Längsachse 38 des ersten Kanalabschnitts 34 und der Längsachse 40 des zweiten Kanalabschnitts 36 erfährt der Fluidstrom eine seitliche Bewegungskomponente (Pfeile 48 in Figur 6) . Diese seitliche Bewegungskomponente wird durch die gekrümmte Wand 41 unterstützt, ohne dass sich hierdurch im ersten Kanalabschnitt 34 ein wesentlicher Staudruck aufbauen kann.During a suction stroke of the piston, the valve ball 46 lifts off the valve seat 44. Fuel now flows from the pre-feed pump 14 via the fuel inlet 32, the first channel section 34, the second channel section 36, and through the gap between valve ball 46 and valve seat 44 into valve chamber 42 and further into delivery chamber 47. Because of the offset V between the longitudinal axis 38 of the first channel section 34 and the longitudinal axis 40 of the second channel section 36, the fluid flow experiences a lateral movement component (arrows 48 in FIG. 6). This lateral movement component is supported by the curved wall 41 without a substantial back pressure being able to build up in the first channel section 34.
Von dem ersten Kanalabschnitt 34 gelangt der Kraftstoff in den zweiten Kanalabschnitt 36. Dabei erfährt er eine Richtungsänderung von 90°. Aufgrund der seitlichen Bewegungskomponente 48 stellt sich jedoch bei der Fluidstrom im zweiten Kanalabschnitt 36 zusätzlich eine Drehbewegung um die Längsachse 40 des zweiten Kanalabschnitts 36 ein. Diese Drehbewegung wird auch als "Drall" oder "Spin" bezeichnet und trägt in den Figuren 6 und 7 das Bezugszeichen 50. Durch den Drall 50 wird bei der Richtungsänderung des Fluidstroms im Übergangsbereich zwischen erstem Kanalabschnitt 34 und zweitem Kanalabschnitt 36 verhindert, dass sich die Strömung ablöst, was zu einem erhöhten Strömungswiderstand sowie der Gefahr von Kavitation und entsprechendem Verschleiß führen würde.The fuel passes from the first channel section 34 into the second channel section 36. It experiences a change in direction of 90 °. Due to the lateral movement component 48, however, the fluid flow in the second channel section 36 additionally results in a rotary movement about the longitudinal axis 40 of the second Channel section 36 a. This rotary movement is also referred to as "swirl" or "spin" and bears the reference symbol 50 in FIGS. 6 and 7. The swirl 50 prevents the fluid flow in the transition region between the first channel section 34 and the second channel section 36 from changing Flow detaches, which would lead to increased flow resistance and the risk of cavitation and corresponding wear.
Durch den Drall 50 wird ferner die Ventilkugel 46 im geöffneten Zustand in eine Drehung versetzt, so dass sie gleichmäßig verschleißt. Somit bleibt ihre Dichtwirkung und auch jene des Ventilsitzes 44 über einen sehr langen Zeitraum erhalten. Da eine Ablösung der KraftstoffStrömung im Übergangsbereich zwischen den beiden Kanalabschnitten 34 und 36 und insbesondere im zweiten Kanalabschnitt 36 verhindert wird, kommt es auch nicht zu einer Einschnürung des Fluidstromes mit entsprechend reduziertem hydraulischem Durchmesser, welcher zu einer erhöhten Drosselung führen würde.The swirl 50 also causes the valve ball 46 to rotate in the open state, so that it wears evenly. Thus, their sealing effect and that of the valve seat 44 is retained over a very long period of time. Since separation of the fuel flow in the transition area between the two channel sections 34 and 36 and in particular in the second channel section 36 is prevented, there is also no constriction of the fluid flow with a correspondingly reduced hydraulic diameter, which would lead to increased throttling.
Eine alternative Ausführungsform ist in Figur 8 gezeigt, Dabei tragen solche Elemente und Bereiche, welche äquivalente Funktionen zu Elementen und Bereichen der vorhergehenden Figuren aufweisen, die gleichen Bezugszeichen. Sie sind nicht nochmals im Detail erläutert. Im Gegensatz zu dem ersten Ausführungsbeispiel steht hier die Längsachse 38 des ersten Kanalabschnitts 34 nicht in einem Winkel von 90°, sondern in einem Winkel von ungefähr 45° zur Längsachse 40 des zweiten Kanalabschnitts 36. Hierdurch wird zusätzlich eine günstigere, d.h. widerstandsärmere Strömung realisiert. An alternative embodiment is shown in FIG. 8. Elements and areas which have functions equivalent to elements and areas of the previous figures have the same reference numerals. They are not explained in detail again. In contrast to the first exemplary embodiment, the longitudinal axis 38 of the first channel section 34 is not at an angle of 90 °, but at an angle of approximately 45 ° to the longitudinal axis 40 of the second channel section 36. less drag flow realized.

Claims

Ansprüche Expectations
1. Ventilanordnung (47), insbesondere Einlassventilanordnung einer Hochdruck-Kraftstoffpumpe (16), mit einem in einer Ventilkammer (42) angeordneten Ventilelement (46) und einem stromaufwärts an die Ventilkammer (42) angrenzenden Fluidkanal (30), dadurch gekennzeichnet, dass der Fluidkanal (30) so ausgebildet ist, dass dem Fluidstrom, welcher der Ventilkammer (42) zuströmt, eine Rotation um die Längsachse (38, 40) des Fluidkanals (30) (Drall) aufgeprägt wird.1. Valve arrangement (47), in particular inlet valve arrangement of a high-pressure fuel pump (16), with a valve element (46) arranged in a valve chamber (42) and a fluid channel (30) adjoining the valve chamber (42) upstream, characterized in that the Fluid channel (30) is designed such that a rotation about the longitudinal axis (38, 40) of the fluid channel (30) (swirl) is impressed on the fluid flow which flows into the valve chamber (42).
2. Ventilanordnung (47) nach Anspruch 1, dadurch gekennzeichnet, dass der Fluidkanal einen ersten Kanalabschnitt (34) und einen an diesen anschließenden, zweiten Kanalabschnitt (36) umfasst, wobei die Längsachsen (38, 40) der Kanalabschnitte (34, 36) zueinander in einem Winkel < 180° stehen, und wobei die Längsachse (38) des ersten Kanalabschnitts (34) gegenüber der Längsachse (40) des zweiten Kanalabschnitts (36) seitlich versetzt (V) ist.2. Valve arrangement (47) according to claim 1, characterized in that the fluid channel comprises a first channel section (34) and an adjoining second channel section (36), the longitudinal axes (38, 40) of the channel sections (34, 36) are at an angle of <180 ° to one another, and the longitudinal axis (38) of the first channel section (34) being laterally offset (V) with respect to the longitudinal axis (40) of the second channel section (36).
3. Ventilanordnung (47) nach Anspruch 2, dadurch gekennzeichnet, dass die Längsachsen (38, 40) der beiden Kanalabschnitte (34, 36) wenigstens in etwa in einem rechten Winkel zueinander stehen.3. Valve arrangement (47) according to claim 2, characterized in that the longitudinal axes (38, 40) of the two channel sections (34, 36) are at least approximately at right angles to one another.
4. Ventilanordnung (47) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass sie als4. Valve arrangement (47) according to one of the preceding claims, characterized in that it as
Ventilelement eine Kugel (46) oder ein Kegelelement umfasst . Valve element comprises a ball (46) or a cone element.
5. Ventilanordnung (47) nach einem der Ansprüche 2 bis 4, dadurch gekennzeichnet, dass beide Kanalabschnitte (34, 36) im Querschnitt wenigstens in etwa den gleichen Radius aufweisen und dass der seitliche Versatz (V) der Längsachsen (38, 40) größer ist als der Radius.5. Valve arrangement (47) according to one of claims 2 to 4, characterized in that both channel sections (34, 36) have at least approximately the same radius in cross section and that the lateral offset (V) of the longitudinal axes (38, 40) is greater is than the radius.
6. Ventilanordnung (47) nach einem der Ansprüche 2 bis 5, dadurch gekennzeichnet, dass ein Übergangsbereich zwischen dem ersten Kanalabschnitt (34) und dem zweiten Kanalabschnitt (36) mittels elektrochemischen Materialabtrags bearbeitet ist.6. Valve arrangement (47) according to one of claims 2 to 5, characterized in that a transition region between the first channel section (34) and the second channel section (36) is machined by means of electrochemical material removal.
7. Ventilanordnung (47) nach Anspruch 6, dadurch gekennzeichnet, dass der Übergangsbereich eine vom ersten (34) zum zweiten Kanalabschnitt (36) gekrümmte Wand (41) umfasst.7. Valve arrangement (47) according to claim 6, characterized in that the transition region comprises a wall (41) curved from the first (34) to the second channel section (36).
8. Ventilanordnung (47) nach einem der Ansprüche 2 bis 7, dadurch gekennzeichnet, dass sich der erste Kanalabschnitt (34) axial nicht oder nicht wesentlich über den zweiten Kanalabschnitt (36) hinaus erstreckt.8. Valve arrangement (47) according to one of claims 2 to 7, characterized in that the first channel section (34) does not extend axially or not substantially beyond the second channel section (36).
9. Ventilanordnung (47) nach einem der vorhergehenden Ansprüche dadurch gekennzeichnet, dass die Längsachse des ersten Kanalabschnitts (34) und die Längsachse des zweiten Kanalabschnitts (36) einen Winkel > 90° einschließen. 9. Valve arrangement (47) according to one of the preceding claims, characterized in that the longitudinal axis of the first channel section (34) and the longitudinal axis of the second channel section (36) enclose an angle> 90 °.
EP04802632A 2003-12-10 2004-10-21 Valve arrangement in particular inlet valve for a high pressure fuel pump Active EP1700028B1 (en)

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Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITMI20080288A1 (en) * 2008-02-22 2009-08-23 Bosch Gmbh Robert HIGH PRESSURE PUMP FOR HIGH PRESSURE FUEL SUPPLY TO AN INTERNAL COMBUSTION ENGINE
DE102009000945A1 (en) * 2009-02-18 2010-08-19 Robert Bosch Gmbh fuel pump
DE102016220610A1 (en) * 2016-10-20 2018-04-26 Robert Bosch Gmbh High pressure pump for a fuel injection system
JP6988196B2 (en) * 2017-06-27 2022-01-05 株式会社Soken Fuel injection device

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US712929A (en) * 1901-10-28 1902-11-04 George M Hendee Valve for internal-combustion engines.
US1105134A (en) * 1913-11-12 1914-07-28 Engelbert Hanemann Carbureter.
US1517598A (en) * 1921-09-01 1924-12-02 Stevenson John William Apparatus for spraying fluids and mixing the same
US3220517A (en) * 1962-10-30 1965-11-30 Best available copy
US3797510A (en) * 1971-10-28 1974-03-19 Purolator Inc Crashworthy valve
US3854468A (en) * 1972-01-17 1974-12-17 Rheem Mfg Co Vortex humidifier for forced flow hot air furnace
US3921656A (en) * 1974-06-20 1975-11-25 Spectrum Ass Inc Self-closing breakaway valve assemblies
US4131134A (en) * 1977-05-04 1978-12-26 Owen, Wickersham & Erickson Fluid flow regulator
US4157281A (en) * 1977-07-14 1979-06-05 Systems Technology Corp Method and apparatus for reclaiming solvents from solvent-bearing sludge material
US4574451A (en) * 1982-12-22 1986-03-11 General Electric Company Method for producing an article with a fluid passage
US4827961A (en) * 1987-10-13 1989-05-09 Helix Enterprises, Inc. High velocity fluid swivel joint coupling
DE3804843A1 (en) * 1988-02-17 1989-08-31 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE3843819A1 (en) * 1988-09-09 1990-03-22 Bosch Gmbh Robert PRESSURE VALVE
DE3937707A1 (en) * 1988-12-24 1991-05-16 Bosch Gmbh Robert Pressure valve for engine fuel line - has control collar with helical recess formed in valve closure
DE19500690B4 (en) * 1995-01-12 2004-05-19 Robert Bosch Gmbh Fuel supply system and method for operating a fuel supply system
DE19541507A1 (en) * 1995-11-08 1997-05-15 Bosch Gmbh Robert Fuel injection device for internal combustion engines
JP2001246216A (en) * 1999-12-28 2001-09-11 Denso Corp Gas-liquid separator
US7082955B2 (en) * 2001-12-04 2006-08-01 Ecotechnology, Ltd. Axial input flow development chamber
US6659118B2 (en) * 2001-12-04 2003-12-09 Ecotechnology, Ltd. Flow development chamber
JP2006513367A (en) * 2003-05-22 2006-04-20 ローベルト　ボツシユ　ゲゼルシヤフト　ミツト　ベシユレンクテル　ハフツング Check valve for high pressure pump of internal combustion engine high pressure injector
JP4260697B2 (en) * 2004-06-29 2009-04-30 三菱電機株式会社 solenoid valve

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2005057004A1 *

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EP1700028B1 (en) 2008-03-05

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