EP1784571B1 - High-pressure pump for a fuel injection device of an internal combustion engine - Google Patents

High-pressure pump for a fuel injection device of an internal combustion engine Download PDF

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Publication number
EP1784571B1
EP1784571B1 EP05760887A EP05760887A EP1784571B1 EP 1784571 B1 EP1784571 B1 EP 1784571B1 EP 05760887 A EP05760887 A EP 05760887A EP 05760887 A EP05760887 A EP 05760887A EP 1784571 B1 EP1784571 B1 EP 1784571B1
Authority
EP
European Patent Office
Prior art keywords
bore
valve
pump
valve element
head
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.)
Not-in-force
Application number
EP05760887A
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German (de)
French (fr)
Other versions
EP1784571A1 (en
Inventor
Alessandro De Luca
Vittorio Caroli
Angela Cavallo
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
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Filing date
Publication date
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Publication of EP1784571A1 publication Critical patent/EP1784571A1/en
Application granted granted Critical
Publication of EP1784571B1 publication Critical patent/EP1784571B1/en
Not-in-force legal-status Critical Current
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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
    • 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
    • F04B1/0448—Sealing means, e.g. for shafts or housings
    • 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
    • F02M59/464—Inlet valves of the check valve type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"

Definitions

  • the invention is based on a high-pressure pump for a fuel injection device of an internal combustion engine according to the preamble of claim 1.
  • Such a high-pressure pump is through the DE 197 44 577 A1 known.
  • This high-pressure pump has at least one pump element, with a driven in a stroke, in a cylinder bore of a pump housing part slidably guided pump piston which limits a pump working space in the cylinder bore.
  • the pump working chamber is filled with fuel from a fuel feed via a suction valve, and during the delivery stroke of the pump piston, fuel is expelled from the pump working chamber via an outlet valve.
  • the suction valve has a piston-shaped valve member which cooperates with a valve seat formed in a valve housing for controlling the connection of the pump working chamber with the fuel inlet with a sealing surface formed thereon.
  • valve member On the valve member engages in the closing direction acting on this closing spring.
  • the valve member has a shaft and a diameter in relation to this enlarged head, wherein the shaft is guided displaceably in a bore of the valve housing. It has been found that the valve member can tilt during its closing movement with its longitudinal axis, whereby an initially one-sided contact of the sealing surface is effected on the valve seat. This tilting is caused by the insufficient guidance of the valve member with its shaft in the bore of the valve housing.
  • a high-pressure pump for a fuel injection device which has a suction valve with a piston-shaped valve member.
  • the valve member has a cylindrical shaft and a head enlarged in cross-section with respect to the shaft.
  • the shaft of the valve member is slidably guided in a guide bore of a valve housing, wherein the shaft has fürströmabête which are reduced compared to the guide portions of the shaft in cross section.
  • an annular throttle gap is present. Also with this suction valve is therefore due to the leadership of the valve member only on the shaft tilting possible with corresponding effects on wear and function.
  • the high-pressure pump according to the invention with the features of claim 1 has the advantage that the leadership of the valve member of the suction valve is improved, whereby the wear is reduced and the durability of the suction valve and thus the high pressure pump is improved.
  • the embodiment according to claim 4 allows a quick closing of the suction valve, as can build up in the room no increased pressure.
  • the embodiments according to claims 5 and 6 allow in a simple way the fuel supply to the suction valve and the connection of the valve member limited space with the fuel inlet.
  • FIG. 1 a high-pressure pump for a fuel injection device of an internal combustion engine in a longitudinal section
  • FIG. 2 a suction valve of the high pressure pump in an enlarged view in a longitudinal section according to a first embodiment
  • FIG. 3 the suction valve in a cross section along line III-III in FIG. 2
  • FIG. 4 a valve housing of the suction valve in an enlarged view in a longitudinal section
  • FIG. 5 a valve member of the suction valve
  • FIG. 6 the valve member in a view in the direction of arrow VI in FIG. 5
  • FIG. 7 the suction valve according to a second embodiment.
  • a high pressure pump 10 is shown for a fuel injector of an internal combustion engine, which is preferably a self-igniting internal combustion engine.
  • fuel is conveyed under high pressure into a memory 12, is taken from the fuel for injection to the internal combustion engine by injectors 13.
  • the high-pressure pump 10 is supplied by a feed pump 14 fuel.
  • the high-pressure pump 10 has at least one pump element 16 which has a pump piston 20 driven at least indirectly by a drive shaft 18 of the high-pressure pump 10 in a lifting movement.
  • the pump piston 20 is tightly guided in a cylinder bore 22 extending at least approximately radially to the drive shaft 18 and delimits a pump working space 24 in the outer end region of the cylinder bore 22 facing away from the drive shaft 18.
  • the drive shaft 18 has a cam or a shaft section 26 eccentric to its axis of rotation 19 , via which during the rotational movement of the drive shaft 18, the lifting movement of the pump piston 20 is effected.
  • the pump piston 20 is held by a return spring 28 directly or via a support member 29 in abutment with the shaft portion 26.
  • the pump working chamber 24 is provided with a fuel inlet from a suction valve 30 which opens into the pump working chamber 24 and is designed as a check valve the delivery pump 14 connectable ago.
  • the pump working chamber 24 can also be connected to the accumulator 12 via a discharge valve 32, which opens out of the pump working chamber 24 and is designed as a check valve, with a fuel outlet.
  • the suction valve 30 When suction stroke of the pump piston 20, the suction valve 30 is opened because of the existing pressure difference, as of the feed pump 14, a higher pressure is generated than the pressure prevailing in the pump working chamber 24, so that funded by the feed pump 14 fuel is sucked into the pump working chamber 24.
  • the outlet valve 32 is closed during the suction stroke of the pump piston 20, as in the memory 12, a higher pressure than in the pump working chamber 24 prevails.
  • the suction valve 30 based on the FIGS. 2 to 6 described in more detail, in which the suction valve 30 is shown according to a first embodiment.
  • the suction valve 30 is as in FIG. 2 represented in a radially outwardly adjoining the cylinder bore 22 bore 34 of a housing part 36 of the high-pressure pump 10 is inserted.
  • the bore 34 is formed larger in diameter relative to the cylinder bore 22.
  • the housing part 36 may for example be a cylinder head which is connected to another housing part in which the drive shaft 18 is mounted, or a housing part, in which the drive shaft 18 is mounted.
  • a fuel inlet channel 38 which is connected to the feed pump 14.
  • a fuel inlet channel 38 which is connected to the feed pump 14.
  • the suction valve 30 has as in the Figures 2 and 4 illustrated a valve housing 42 which is formed approximately pot-shaped.
  • the valve housing 42 has at its annular shoulder 40 facing inner end on an enlarged outer diameter flange 44. Subsequently, the outer diameter of the valve housing is lower on the flange 44 and may be reduced to the outer end of the valve housing 42 facing away from the annular shoulder 40, for example approximately frusto-conically.
  • the valve housing 42 has a through hole 46, which is formed multi-stepped in diameter.
  • the bore 46 has in the outer end region of the valve housing 42 on a small diameter first portion 46 a, to which the inner end of the valve housing 42 is followed by a larger diameter second bore portion 46 b.
  • the second bore section 46b is adjoined by a third bore section 46c, whose diameter increases at least approximately in the shape of a truncated cone towards the inner end of the valve housing 42 and whose lateral surface is inclined at an angle ⁇ to the longitudinal axis 47 of the bore 46.
  • the third bore portion 46c forms a valve seat.
  • the third bore section 46c is adjoined by a fourth bore section 46d, whose diameter increases at least approximately in the shape of a truncated cone towards the inner end of the valve housing 42 and whose lateral surface is inclined at an angle ⁇ to the longitudinal axis 47 of the bore 46.
  • the angle ⁇ of the fourth bore portion 46d is greater than the angle ⁇ of the third bore portion 46c.
  • the fourth bore portion 46d is followed by a fifth bore portion 46e of constant diameter toward the inner end of the valve housing 42.
  • a chamfer may be provided at the transition between the second bore portion 46b and the third bore portion 46c.
  • a chamfer may be provided at the transition between the second bore portion 46b and the third bore portion 46c.
  • the Transition between the fourth bore portion 46d and the fifth bore portion 46e may be rounded.
  • At least one inlet channel 50 is introduced, which opens on the one hand on the outer surface of the valve housing 42 and on the other hand in the second bore portion 46b.
  • a plurality of, for example, three over the circumference of the valve housing 42 evenly distributed feed channels 50 are provided.
  • the inlet channels 50 can open into the bore section 46b such that their longitudinal axes 51 intersect with the longitudinal axis 47 of the bore section 46b.
  • the inlet channels 50 may also open into the second bore section 46b such that their longitudinal axes 51 do not intersect the longitudinal axis 47 of the bore 46 and the inlet channels 50 open at least approximately tangentially into the bore section 46b, as shown in FIG FIG. 3 is shown.
  • the inlet channels 50 may extend with their longitudinal axes 51 at least approximately perpendicular to the longitudinal axis 47 of the bore 46 or as in FIG. 2 and 4 illustrated such that the longitudinal axis 51 of the inlet channels 50 form with the longitudinal axis 47 of the bore 46 to the end of the valve housing 42 with the flange 44 toward an acute angle.
  • an annular space 52 is present, into which the fuel inlet channel 38 opens.
  • the valve housing 42 is held in the bore 34 of the housing part 36 by an inserted into the bore 34 holding member 54 which is preferably formed as a screwed into an internal thread of the bore 34 retaining screw.
  • an elastic sealing ring 56 is clamped, through which the bore 34 is sealed to the outside.
  • the valve housing 42 is replaced by the retaining screw 54th pressed with its flange 44 against the annular shoulder 40 of the housing part 36.
  • the flange 44 and / or the annular shoulder 40 may have a raised web 58 which is elastically and / or plastically deformed by the pressure of the valve housing 42 against the annular shoulder 40 and thereby ensures a seal of the pump working chamber 24 to the bore 34.
  • a separate sealing element for sealing can be arranged between the flange 44 and the annular shoulder 40.
  • the retaining screw 54 may have on its side facing the bore 34 side a recess 55 having a non-circular cross-section into which a suitably trained tool for screwing or unscrewing the retaining screw 54 can be inserted into the thread of the bore 34.
  • the retaining screw 54 has on its side facing the valve housing 42 a recess 57 into which the valve housing 42 is immersed.
  • the valve housing 42 has in its the screw 54 facing the front side a central depression, into which the bore 46 opens. By lowering the valve housing 42, a space 60 is limited between this and the retaining screw 54, in which the bore 46 opens.
  • the space 60 is connected to the second bore portion 46b through at least one bore 62 in the valve housing 42, the bore 62 being at least approximately parallel to the first bore portion 46a and laterally adjacent thereto.
  • the space 60 is thus constantly connected to the second bore portion 46 b and thus to the fuel inlet passage 38.
  • the suction valve 30 also has as in the Figures 2 . 5 and 6 10 illustrates a piston-shaped valve member 64 which has a cylindrical shaft 66 and a head 68 which is larger in cross-section than the shaft 66.
  • a sealing surface 70 is arranged at its edge facing the shaft 66, which is formed at least approximately frusto-conical and whose lateral surface is inclined at an angle ⁇ to the longitudinal axis 65 of the valve member 64.
  • the sealing surface 70 is adjoined by a cylindrical or at least approximately frusto-conical widening in cross section to the end of the head 68 facing away from the shaft 66.
  • a plurality of distributed over the circumference of the head 68 and spaced apart guide portions 74 are arranged, whose outer contours lie on a common diameter.
  • the guide sections 74 may be part of the truncated cone of the region of the head 68. However, the guide portions 74 may also have an at least approximately cylindrical outer contour. Between the guide portions 74 are present in cross-section with respect to these reduced portions 76, which are formed for example by bevels or flats on the periphery of the head 68. From the shaft 66 facing away from the end face of the head 68 of the valve member 64 is at least approximately coaxially to the longitudinal axis 65, a short pin 78 out.
  • an undercut can be provided in each case to simplify the manufacturability of the valve member 64.
  • an annular groove 72 is preferably provided between the sealing surface 70 and the head 68 with the guide portions 74.
  • the opening behavior of the valve member 64 is improved by the pressure acting in the opening direction can act on the sealing surface 70, and thus improves the filling of the pump working chamber 24.
  • the wear behavior of the sealing surface 70 is improved by the annular groove 72 by the wear of the sealing surface 70 is stopped at the annular groove 72.
  • the valve member 64 is slidably guided with its shaft 66 in the first bore portion 46 a of the valve housing 42 with a small clearance.
  • the first bore portion 46a thus forms a guide bore for the shaft 66 of the valve member 64.
  • the valve member 64 is guided over its guide portions 74 with greater clearance in the fifth bore portion 46e of the valve housing 42.
  • the possible tilting of the longitudinal axis 65 of the valve member 64 with respect to the longitudinal axis 47 of the bore 46 is limited by the guide portions 74, for example to a maximum of about 0.5 °, preferably to a maximum of about 0.25 °.
  • the angle ⁇ under which the lateral surface of the valve seat 46c is inclined to the longitudinal axis 47, deviates from the angle ⁇ , under which the lateral surface of the sealing surface 70 of the valve member 64 is inclined to the longitudinal axis 47.
  • the angle ⁇ can be slightly larger than the angle ⁇ , wherein the difference can be relatively small and, for example, can be only a few degrees or only about 1 °.
  • FIG. 2 1 shows a closing spring 80 acting in the closing direction, which is supported on the pump piston 20 on the one hand and on the end face of the head 68 of the valve member 64 facing the pump piston 20 on the other hand.
  • the closing spring 80 is formed, for example, as a helical compression spring and is placed on the pin 78 on the valve member 64 and is centered by this.
  • valve member 64 is acted upon in its opening direction by the pressure supplied via the inlet channels 50 to the second bore section 46b, generated by the feed pump 14.
  • a higher pressure generated by the feed pump 14 prevails in the fuel feed than in the pump working chamber 24, so that the valve member 64 opens against the force of the closing spring 80 and lifts off with its sealing surface 70 from the valve seat 46c and thereby an annular flow cross-section into the pump working space 24 releases.
  • a sufficiently large flow cross section is released to allow filling of the pump working chamber 24 with fuel.
  • the inflow of the fuel from the inlet channels 50 into the second bore section 46b takes place as a result of the tangential mouth of the inlet channels 50 into the bore section 46b with low flow losses. Due to the tangential mouth of the inlet bores 50, the incoming fuel receives a twist. The outlet of the inlet channels 50 in the bore section 46b can be rounded. Thus, a good filling of the pump working space 24 is made possible.
  • the space 60 between the valve housing 42 and the retaining screw 54 is connected via the bore 62 with the fuel inlet 38, so that in the closing movement of the valve member 64 of this from the space 60 fuel can be displaced into the fuel inlet 38, whereby a rapid closing of the Suction valve 30 is reached and a pressure increase in the space 60 is avoided.
  • the suction valve opens 30, as caused by the pressure acting on the valve member 64 in the opening direction in the fuel inlet 38 pressure opening force is greater than the force of the closing spring 80 and the force generated by the pressure prevailing in the pump working chamber 24 in the closing direction on the valve member 64.
  • the delivery stroke of the pump piston 20 in which it moves away from the drive shaft 18 to the outside, closes the suction valve 30, since the sum of the force generated by the pressure prevailing in the pump working chamber 24 and the force of the closing spring 80 is greater than the opening force on the Valve member 64.
  • FIG. 7 the suction valve 30 is shown according to a second embodiment, in which the basic structure is the same as in the first embodiment, but the valve housing and the retaining screw are integrally formed as a valve housing 142.
  • the valve member 64 of the suction valve 30 is formed identical to the first embodiment and will therefore not be described again in more detail below.
  • the bore 46 with the bore portions 46a, 46b, 46c, 46d and 46e is arranged, wherein the bore 46 is formed as a blind bore.
  • the valve member 64 is guided with its shaft 66 with little play in the guide bore 46a and guided with greater play with its head 68 via the guide portions 74 in the bore portion 46e.
  • the valve housing 142 is provided with an external thread, with which it is screwed into a corresponding internal thread of the bore 34 in the housing part 36 of the high-pressure pump, wherein the sealing of the bore 34 takes place to the outside by the sealing ring 56.
  • the seal between the valve housing 142 and the annular shoulder 40 at the transition of the bore 34 to the cylinder bore 22 is the same as in the first embodiment.
  • the fuel inlet channel 38 opens into The bore 34 in the valve housing 142 surrounding annular space 52.
  • a plurality of circumferentially distributed fuel inlet channels 150 are formed, which open on the one hand on the outer surface of the valve housing 142 and on the other hand in the second bore portion 46 b.
  • the course of the inlet channels 150 is analogous to the first exemplary embodiments, so that they preferably open at least approximately tangentially into the second bore section 46b.
  • the inlet channels 150 may extend with their longitudinal axes 151 at least approximately perpendicular to the longitudinal axis 47 of the bore 46 or as in FIG. 7 illustrated such that the longitudinal axis 151 of the inlet channels 150 with the longitudinal axis 47 of the bore 46 to the outer end of the valve housing 142 form an acute angle.
  • the valve housing 142 also has a bore 162 is introduced, which opens on the one hand on the outer surface of the valve housing 142 in the annular space 52 and the other part in the first bore portion 46 a in the limited space by the shaft 66 of the valve member 64 space 160.
  • the space 160 is thus permanently connected to the fuel inlet channel 38.
  • the valve housing 142 and the bore 34 of the housing part 36 of the sealing ring 56 is clamped to seal the annular space 52, in which the fuel supply pressure generated by the feed pump 14, to the outside.
  • the sealing against the pressure prevailing in the pump working chamber 24 high pressure takes place as in the first embodiment between the housing part 36 and the valve housing 142 by a raised web on one of these parts or by a separate sealing ring.

Abstract

The high-pressure pump has at least one pump element with a pump piston driven in a reciprocating motion and guided displaceably in a cylinder bore of a pump housing part which piston defines a pump work chamber that can be filled with fuel from a fuel inlet via a suction valve in the intake stroke. The suction valve has a pistonlike valve member which has a cylindrical shaft and a head of larger cross section at least the shaft is guided displaceably in a guide bore of a valve housing. The head of the valve member is also guided displaceably in a bore of the valve housing, via guide portions embodied on the valve member and spaced apart from one another in the circumferential direction; between the guide portions, flowthrough portions of reduced cross section compared to the guide portions provide for fuel flow out of the fuel inlet into the pump work chamber.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine nach der Gattung des Anspruchs 1.The invention is based on a high-pressure pump for a fuel injection device of an internal combustion engine according to the preamble of claim 1.

Eine solche Hochdruckpumpe ist durch die DE 197 44 577 A1 bekannt. Diese Hochdruckpumpe weist wenigstens ein Pumpenelement auf, mit einem in einer Hubbewegung angetriebenen, in einer Zylinderbohrung eines Pumpengehäuseteils verschiebbar geführten Pumpenkolben, der in der Zylinderbohrung einen Pumpenarbeitsraum begrenzt. Beim Saughub des Pumpenkolbens wird der Pumpenarbeitsraum über ein Saugventil mit Kraftstoff aus einem Kraftstoffzulauf befüllt und beim Förderhub des Pumpenkolbens wird Kraftstoff aus dem Pumpenarbeitsraum über ein Auslassventil verdrängt. Das Saugventil weist ein kolbenförmiges Ventilglied auf, das zur Steuerung der Verbindung des Pumpenarbeitsraums mit dem Kraftstoffzulauf mit einer an diesem ausgebildeten Dichtfläche mit einem in einem Ventilgehäuse ausgebildeten Ventilsitz zusammenwirkt. Am Ventilglied greift eine in Schließrichtung auf dieses wirkende Schließfeder an. Das Ventilglied weist einen Schaft und einen im Durchmesser gegenüber diesem vergrößerten Kopf auf, wobei der Schaft in einer Bohrung des Ventilgehäuses verschiebbar geführt ist. Es wurde festgestellt, dass sich das Ventilglied bei seiner Schließbewegung mit seiner Längsachse verkippen kann, wodurch eine zunächst einseitige Anlage der Dichtfläche am Ventilsitz bewirkt wird. Dieses Verkippen wird durch die unzureichende Führung des Ventilglieds mit seinem Schaft in der Bohrung des Ventilgehäuses verursacht. Insbesondere bei Kraftstoffen mit schlechten Schmiereigenschaften führt dieses Verkippen des Ventilglieds und die dadurch verursachte einseitige Anlage der Dichtfläche des Ventilglieds am Ventilsitz zu einem großen Verschleiß am Ventilglied und/oder am Ventilsitz und damit zu einer Funktionsverschlechterung und unter Umständen zum Ausfall des Saugventils und damit der Hochdruckpumpe.Such a high-pressure pump is through the DE 197 44 577 A1 known. This high-pressure pump has at least one pump element, with a driven in a stroke, in a cylinder bore of a pump housing part slidably guided pump piston which limits a pump working space in the cylinder bore. During the suction stroke of the pump piston, the pump working chamber is filled with fuel from a fuel feed via a suction valve, and during the delivery stroke of the pump piston, fuel is expelled from the pump working chamber via an outlet valve. The suction valve has a piston-shaped valve member which cooperates with a valve seat formed in a valve housing for controlling the connection of the pump working chamber with the fuel inlet with a sealing surface formed thereon. On the valve member engages in the closing direction acting on this closing spring. The valve member has a shaft and a diameter in relation to this enlarged head, wherein the shaft is guided displaceably in a bore of the valve housing. It has been found that the valve member can tilt during its closing movement with its longitudinal axis, whereby an initially one-sided contact of the sealing surface is effected on the valve seat. This tilting is caused by the insufficient guidance of the valve member with its shaft in the bore of the valve housing. Especially with fuels with poor lubricating properties of this tilting of the valve member and the resulting unilateral contact the sealing surface of the valve member on the valve seat to a large wear on the valve member and / or the valve seat and thus to a deterioration in function and possibly to the failure of the suction valve and thus the high-pressure pump.

Durch die DE-A-679 246 ist eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung bekannt, die ein Saugventil mit einem kolbenförmigen Ventilglied aufweist. Das Ventilglied weist einen zylindrischen Schaft und einen im Querschnitt gegenüber dem Schaft vergrößerten Kopf auf. Der Schaft des Ventilglieds ist in einer Führungsbohrung eines Ventilgehäuses verschiebbar geführt, wobei der Schaft Durchströmabschnitte aufweist, die gegenüber den Führungsabschnitten des Schafts im Querschnitt verringert sind. Zwischen dem Kopf des Ventilglieds und dem Ventilgehäuse ist ein ringförmiger Drosselspalt vorhanden. Auch bei diesem Saugventil ist somit wegen der Führung des Ventilglieds nur an dessen Schaft ein Verkippen möglich mit entsprechenden Auswirkungen auf Verschleiß und Funktion.By the DE-A-679 246 a high-pressure pump for a fuel injection device is known, which has a suction valve with a piston-shaped valve member. The valve member has a cylindrical shaft and a head enlarged in cross-section with respect to the shaft. The shaft of the valve member is slidably guided in a guide bore of a valve housing, wherein the shaft has Durchströmabschnitte which are reduced compared to the guide portions of the shaft in cross section. Between the head of the valve member and the valve housing an annular throttle gap is present. Also with this suction valve is therefore due to the leadership of the valve member only on the shaft tilting possible with corresponding effects on wear and function.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Hochdruckpumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass die Führung des Ventilglieds des Saugventils verbessert ist, wodurch der Verschleiß reduziert und die Haltbarkeit des Saugventils und damit der Hochdruckpumpe verbessert ist.The high-pressure pump according to the invention with the features of claim 1 has the advantage that the leadership of the valve member of the suction valve is improved, whereby the wear is reduced and the durability of the suction valve and thus the high pressure pump is improved.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Hochdruckpumpe angegeben. Die Ausbildung gemäß Anspruch 4 ermöglicht ein schnelles Schließen des Saugventils, da sich in dem Raum kein erhöhter Druck aufbauen kann. Die Ausbildungen gemäß den Ansprüchen 5 und 6 ermöglichen auf einfache Weise die Kraftstoffzuführung in das Saugventil und die Verbindung des vom Ventilglied begrenzten Raums mit dem Kraftstoffzulauf.In the dependent claims advantageous refinements and developments of the high pressure pump according to the invention are given. The embodiment according to claim 4 allows a quick closing of the suction valve, as can build up in the room no increased pressure. The embodiments according to claims 5 and 6 allow in a simple way the fuel supply to the suction valve and the connection of the valve member limited space with the fuel inlet.

Zeichnungdrawing

Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine in einem Längsschnitt, Figur 2 ein Saugventil der Hochdruckpumpe in vergrößerter Darstellung in einem Längsschnitt gemäß einem ersten Ausführungsbeispiel, Figur 3 das Saugventil in einem Querschnitt entlang Linie III-III in Figur 2, Figur 4 ein Ventilgehäuse des Saugventils in vergrößerter Darstellung in einem Längsschnitt, Figur 5 ein Ventilglied des Saugventils, Figur 6 das Ventilglied in einer Ansicht in Pfeilrichtung VI in Figur 5 und Figur 7 das Saugventil gemäß einem zweiten Ausführungsbeispiel.Two embodiments of the invention are illustrated in the drawing and explained in more detail in the following description. Show it FIG. 1 a high-pressure pump for a fuel injection device of an internal combustion engine in a longitudinal section, FIG. 2 a suction valve of the high pressure pump in an enlarged view in a longitudinal section according to a first embodiment, FIG. 3 the suction valve in a cross section along line III-III in FIG. 2 . FIG. 4 a valve housing of the suction valve in an enlarged view in a longitudinal section, FIG. 5 a valve member of the suction valve, FIG. 6 the valve member in a view in the direction of arrow VI in FIG. 5 and FIG. 7 the suction valve according to a second embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist eine Hochdruckpumpe 10 für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine dargestellt, die vorzugsweise eine selbstzündende Brennkraftmaschine ist. Durch die Hochdruckpumpe 10 wird Kraftstoff unter Hochdruck in einen Speicher 12 gefördert, aus dem Kraftstoff zur Einspritzung an der Brennkraftmaschine durch Injektoren 13 entnommen wird. Der Hochdruckpumpe 10 wird durch eine Förderpumpe 14 Kraftstoff zugeführt. Die Hochdruckpumpe 10 weist wenigstens ein Pumpenelement 16 auf, das einen zumindest mittelbar durch eine Antriebswelle 18 der Hochdruckpumpe 10 in einer Hubbewegung angetriebenen Pumpenkolben 20 aufweist. Der Pumpenkolben 20 ist in einer zumindest annähernd radial zur Antriebswelle 18 verlaufenden Zylinderbohrung 22 dicht geführt und begrenzt in dem der Antriebswelle 18 abgewandten äusseren Endbereich der Zylinderbohrung 22 einen Pumpenarbeitsraum 24. Die Antriebswelle 18 weist einen Nocken oder einen zu ihrer Drehachse 19 exzentrischen Wellenabschnitt 26 auf, über den bei der Drehbewegung der Antriebswelle 18 die Hubbewegung des Pumpenkolbens 20 bewirkt wird. Der Pumpenkolben 20 wird durch eine Rückstellfeder 28 direkt oder über ein Stützelement 29 in Anlage am Wellenabschnitt 26 gehalten.In FIG. 1 a high pressure pump 10 is shown for a fuel injector of an internal combustion engine, which is preferably a self-igniting internal combustion engine. By the high-pressure pump 10 fuel is conveyed under high pressure into a memory 12, is taken from the fuel for injection to the internal combustion engine by injectors 13. The high-pressure pump 10 is supplied by a feed pump 14 fuel. The high-pressure pump 10 has at least one pump element 16 which has a pump piston 20 driven at least indirectly by a drive shaft 18 of the high-pressure pump 10 in a lifting movement. The pump piston 20 is tightly guided in a cylinder bore 22 extending at least approximately radially to the drive shaft 18 and delimits a pump working space 24 in the outer end region of the cylinder bore 22 facing away from the drive shaft 18. The drive shaft 18 has a cam or a shaft section 26 eccentric to its axis of rotation 19 , via which during the rotational movement of the drive shaft 18, the lifting movement of the pump piston 20 is effected. The pump piston 20 is held by a return spring 28 directly or via a support member 29 in abutment with the shaft portion 26.

Der Pumpenarbeitsraum 24 ist über ein in den Pumpenarbeitsraum 24 öffnendes, als Rückschlagventil ausgebildetes Saugventil 30 mit einem Kraftstoffzulauf von der Förderpumpe 14 her verbindbar. Der Pumpenarbeitsraum 24 ist außerdem über ein aus dem Pumpenarbeitsraum 24 öffnendes, als Rückschlagventil ausgebildetes Auslassventil 32 mit einem Kraftstoffablauf zum Speicher 12 hin verbindbar. Beim Saughub bewegt sich der Pumpenkolben 20 in der Zylinderbohrung 22 radial nach innen, so dass das Volumen des Pumpenarbeitsraums 24 vergrößert wird. Beim Saughub des Pumpenkolbens 20 ist wegen der dabei bestehenden Druckdifferenz das Saugventil 30 geöffnet, da von der Förderpumpe 14 ein höherer Druck erzeugt wird als der im Pumpenarbeitsraum 24 herrschende Druck, so dass von der Förderpumpe 14 geförderter Kraftstoff in den Pumpenarbeitsraum 24 angesaugt wird. Das Auslassventil 32 ist beim Saughub des Pumpenkolbens 20 geschlossen, da im Speicher 12 ein höherer Druck als im Pumpenarbeitsraum 24 herrscht.The pump working chamber 24 is provided with a fuel inlet from a suction valve 30 which opens into the pump working chamber 24 and is designed as a check valve the delivery pump 14 connectable ago. The pump working chamber 24 can also be connected to the accumulator 12 via a discharge valve 32, which opens out of the pump working chamber 24 and is designed as a check valve, with a fuel outlet. During the suction stroke, the pump piston 20 in the cylinder bore 22 moves radially inwards, so that the volume of the pump working chamber 24 is increased. When suction stroke of the pump piston 20, the suction valve 30 is opened because of the existing pressure difference, as of the feed pump 14, a higher pressure is generated than the pressure prevailing in the pump working chamber 24, so that funded by the feed pump 14 fuel is sucked into the pump working chamber 24. The outlet valve 32 is closed during the suction stroke of the pump piston 20, as in the memory 12, a higher pressure than in the pump working chamber 24 prevails.

Nachfolgend wird das Saugventil 30 anhand der Figuren 2 bis 6 näher beschrieben, in denen das Saugventil 30 gemäß einem ersten Ausführungsbeispiel dargestellt ist. Das Saugventil 30 ist wie in Figur 2 dargestellt in eine sich radial nach aussen an die Zylinderbohrung 22 anschliessende Bohrung 34 eines Gehäuseteils 36 der Hochdruckpumpe 10 eingesetzt. Die Bohrung 34 ist dabei im Durchmesser gegenüber der Zylinderbohrung 22 größer ausgebildet. Das Gehäuseteil 36 kann beispielsweise ein Zylinderkopf sein, der mit einem andere Gehäuseteil, in dem die Antriebswelle 18 gelagert ist, verbunden ist oder ein Gehäuseteil sein, in dem auch die Antriebswelle 18 gelagert ist. In die Bohrung 34 mündet nahe deren der Zylinderbohrung 22 zugewandtem Endbereich beispielsweise etwa radial zur Achse der Bohrung 34 ein Kraftstoffzulaufkanal 38, der mit der Förderpumpe 14 verbunden ist. Am Übergang zwischen der Bohrung 34 und der Zylinderbohrung 22 ist am Gehäuseteil 36 eine zur Außenseite des Gehäuseteils 36 weisende Ringschulter 40 gebildet.Subsequently, the suction valve 30 based on the FIGS. 2 to 6 described in more detail, in which the suction valve 30 is shown according to a first embodiment. The suction valve 30 is as in FIG. 2 represented in a radially outwardly adjoining the cylinder bore 22 bore 34 of a housing part 36 of the high-pressure pump 10 is inserted. The bore 34 is formed larger in diameter relative to the cylinder bore 22. The housing part 36 may for example be a cylinder head which is connected to another housing part in which the drive shaft 18 is mounted, or a housing part, in which the drive shaft 18 is mounted. In the bore 34 opens near the cylinder bore 22 facing end portion, for example, approximately radially to the axis of the bore 34, a fuel inlet channel 38 which is connected to the feed pump 14. At the transition between the bore 34 and the cylinder bore 22 is on the housing part 36 to the outside of the housing part 36 facing annular shoulder 40 is formed.

Das Saugventil 30 weist wie in den Figuren 2 und 4 dargestellt ein Ventilgehäuse 42 auf, das annähernd topfförmig ausgebildet ist. Das Ventilgehäuse 42 weist dabei an seinem der Ringschulter 40 zugewandten inneren Ende einen im Außendurchmesser vergrößerten Flansch 44 auf. An den Flansch 44 anschließend ist der Außendurchmesser des Ventilgehäuses geringer und kann sich zum der Ringschulter 40 abgewandten äußeren Ende des Ventilgehäuses 42 hin beispielsweise etwa kegelstumpfförmig verringern. Das Ventilgehäuse 42 weist eine Durchgangsbohrung 46 auf, die im Durchmesser mehrfach gestuft ausgebildet ist. Die Bohrung 46 weist im äußeren Endbereich des Ventilgehäuses 42 einen im Durchmesser kleinen ersten Abschnitt 46a auf, an den sich zum inneren Ende des Ventilgehäuses 42 hin ein im Durchmesser größerer zweiter Bohrungsabschnitt 46b anschließt. An den zweiten Bohrungsabschnitt 46b schließt sich ein dritter Bohrungsabschnitt 46c an, dessen Durchmesser sich zum inneren Ende des Ventilgehäuses 42 hin zumindest annähernd kegelstumpfförmig vergrößert und dessen Mantelfläche unter einem Winkel α zur Längsachse 47 der Bohrung 46 geneigt ist. Der dritte Bohrungsabschnitt 46c bildet einen Ventilsitz. An den dritten Bohrungsabschnitt 46c schließt sich ein vierter Bohrungsabschnitt 46d an, dessen Durchmesser sich zum inneren Ende des Ventilgehäuses 42 hin zumindest annähernd kegelstumpfförmig vergrößert und dessen Mantelfläche unter einem Winkel β zur Längsachse 47 der Bohrung 46 geneigt ist. Der Winkel β des vierten Bohrungsabschnitts 46d ist dabei größer als der Winkel α des dritten Bohrungsabschnitts 46c. An den vierten Bohrungsabschnitt 46d schließt sich schließlich zum inneren Ende des Ventilgehäuses 42 hin ein fünfter Bohrungsabschnitt 46e mit konstantem Durchmesser an. Am Übergang zwischen dem zweiten Bohrungsabschnitt 46b und dem dritten Bohrungsabschnitt 46c kann eine Fase vorgesehen sein. Der Übergang zwischen dem vierten Bohrungsabschnitt 46d und dem fünften Bohrungsabschnitt 46e kann gerundet ausgebildet sein.The suction valve 30 has as in the Figures 2 and 4 illustrated a valve housing 42 which is formed approximately pot-shaped. The valve housing 42 has at its annular shoulder 40 facing inner end on an enlarged outer diameter flange 44. Subsequently, the outer diameter of the valve housing is lower on the flange 44 and may be reduced to the outer end of the valve housing 42 facing away from the annular shoulder 40, for example approximately frusto-conically. The valve housing 42 has a through hole 46, which is formed multi-stepped in diameter. The bore 46 has in the outer end region of the valve housing 42 on a small diameter first portion 46 a, to which the inner end of the valve housing 42 is followed by a larger diameter second bore portion 46 b. The second bore section 46b is adjoined by a third bore section 46c, whose diameter increases at least approximately in the shape of a truncated cone towards the inner end of the valve housing 42 and whose lateral surface is inclined at an angle α to the longitudinal axis 47 of the bore 46. The third bore portion 46c forms a valve seat. The third bore section 46c is adjoined by a fourth bore section 46d, whose diameter increases at least approximately in the shape of a truncated cone towards the inner end of the valve housing 42 and whose lateral surface is inclined at an angle β to the longitudinal axis 47 of the bore 46. The angle β of the fourth bore portion 46d is greater than the angle α of the third bore portion 46c. Finally, the fourth bore portion 46d is followed by a fifth bore portion 46e of constant diameter toward the inner end of the valve housing 42. At the transition between the second bore portion 46b and the third bore portion 46c, a chamfer may be provided. Of the Transition between the fourth bore portion 46d and the fifth bore portion 46e may be rounded.

Im Mantel des Ventilgehäuses 42 ist wenigstens ein Zulaufkanal 50 eingebracht, der einerseits am Aussenmantel des Ventilgehäuses 42 und andererseits im zweiten Bohrungsabschnitt 46b mündet. Vorzugsweise sind mehrere, beispielsweise drei über den Umfang des Ventilgehäuses 42 gleichmäßig verteilte Zulaufkanäle 50 vorgesehen. Die Zulaufkanäle 50 können dabei in den Bohrungsabschnitt 46b derart münden, dass sich ihre Längsachsen 51 mit der Längsachse 47 des Bohrungsabschnitts 46b schneiden. Alternativ können die Zulaufkanäle 50 auch derart in den zweiten Bohrungsabschnitt 46b münden, dass deren Längsachsen 51 die Längsachse 47 der Bohrung 46 nicht schneiden und die Zulaufkanäle 50 zumindest annähernd tangential in den Bohrungsabschnitt 46b münden, wie dies in Figur 3 dargestellt ist. Die Zulaufkanäle 50 können mit ihren Längsachsen 51 zumindest annähernd senkrecht zur Längsachse 47 der Bohrung 46 verlaufen oder wie in Figur 2 und 4 dargestellt derart, dass die Längsachse 51 der Zulaufkanäle 50 mit der Längsachse 47 der Bohrung 46 zum Ende des Ventilgehäuses 42 mit dem Flansch 44 hin einen spitzen Winkel bilden. Zwischen dem Mantel des Ventilgehäuses 42 im Bereich der Mündungen der Zulaufkanäle 50 und der Bohrung 34 im Gehäuseteil 36 ist ein Ringraum 52 vorhanden, in den der Kraftstoffzulaufkanal 38 mündet. Das Ventilgehäuse 42 ist in der Bohrung 34 des Gehäuseteils 36 durch ein in die Bohrung 34 eingesetztes Halteelement 54 gehalten, das vorzugsweise als eine in ein Innengewinde der Bohrung 34 eingeschraubte Halteschraube ausgebildet ist. Zwischen der Halteschraube 54 und der Bohrung 34 ist ein elastischer Dichtring 56 eingespannt, durch den die Bohrung 34 nach außen abgedichtet wird. Das Ventilgehäuse 42 wird durch die Halteschraube 54 mit seinem Flansch 44 gegen die Ringschulter 40 des Gehäuseteils 36 gepresst. Der Flansch 44 und/oder die Ringschulter 40 kann dabei einen erhöhten Steg 58 aufweisen, der durch die Pressung des Ventilgehäuses 42 gegen die Ringschulter 40 elastisch und/oder plastisch verformt wird und dabei eine Abdichtung des Pumpenarbeitsraums 24 zur Bohrung 34 sicherstellt. Alternativ kann zwischen dem Flansch 44 und der Ringschulter 40 auch ein separates Dichtelement zur Abdichtung angeordnet werden.In the jacket of the valve housing 42 at least one inlet channel 50 is introduced, which opens on the one hand on the outer surface of the valve housing 42 and on the other hand in the second bore portion 46b. Preferably, a plurality of, for example, three over the circumference of the valve housing 42 evenly distributed feed channels 50 are provided. The inlet channels 50 can open into the bore section 46b such that their longitudinal axes 51 intersect with the longitudinal axis 47 of the bore section 46b. Alternatively, the inlet channels 50 may also open into the second bore section 46b such that their longitudinal axes 51 do not intersect the longitudinal axis 47 of the bore 46 and the inlet channels 50 open at least approximately tangentially into the bore section 46b, as shown in FIG FIG. 3 is shown. The inlet channels 50 may extend with their longitudinal axes 51 at least approximately perpendicular to the longitudinal axis 47 of the bore 46 or as in FIG. 2 and 4 illustrated such that the longitudinal axis 51 of the inlet channels 50 form with the longitudinal axis 47 of the bore 46 to the end of the valve housing 42 with the flange 44 toward an acute angle. Between the jacket of the valve housing 42 in the region of the mouths of the inlet channels 50 and the bore 34 in the housing part 36, an annular space 52 is present, into which the fuel inlet channel 38 opens. The valve housing 42 is held in the bore 34 of the housing part 36 by an inserted into the bore 34 holding member 54 which is preferably formed as a screwed into an internal thread of the bore 34 retaining screw. Between the retaining screw 54 and the bore 34, an elastic sealing ring 56 is clamped, through which the bore 34 is sealed to the outside. The valve housing 42 is replaced by the retaining screw 54th pressed with its flange 44 against the annular shoulder 40 of the housing part 36. The flange 44 and / or the annular shoulder 40 may have a raised web 58 which is elastically and / or plastically deformed by the pressure of the valve housing 42 against the annular shoulder 40 and thereby ensures a seal of the pump working chamber 24 to the bore 34. Alternatively, between the flange 44 and the annular shoulder 40, a separate sealing element for sealing can be arranged.

Die Halteschraube 54 kann auf ihrer zur Außenseite der Bohrung 34 weisenden Seite eine Vertiefung 55 mit einem nichtkreisförmigen Querschnitt aufweisen, in die ein entsprechend ausgebildetes Werkzeug zum Eindrehen bzw. Herausdrehen der Halteschraube 54 in das Gewinde der Bohrung 34 eingesetzt werden kann. Die Halteschraube 54 weist auf ihrer dem Ventilgehäuse 42 zugewandten Seite eine Vertiefung 57 auf, in die das Ventilgehäuse 42 eintaucht. Das Ventilgehäuse 42 weist in seiner der Halteschraube 54 zugewandten Stirnseite eine mittige Absenkung auf, in die die Bohrung 46 mündet. Durch die Absenkung des Ventilgehäuses 42 ist zwischen diesem und der Halteschraube 54 ein Raum 60 begrenzt, in den die Bohrung 46 mündet. Der Raum 60 ist durch wenigstens eine Bohrung 62 im Ventilgehäuse 42 mit dem zweiten Bohrungsabschnitt 46b verbunden, wobei die Bohrung 62 zumindest annähernd parallel zum ersten Bohrungsabschnitt 46a und seitlich neben diesem verläuft. Der Raum 60 ist somit ständig mit dem zweiten Bohrungsabschnitt 46b und damit mit dem Kraftstoffzulaufkanal 38 verbunden.The retaining screw 54 may have on its side facing the bore 34 side a recess 55 having a non-circular cross-section into which a suitably trained tool for screwing or unscrewing the retaining screw 54 can be inserted into the thread of the bore 34. The retaining screw 54 has on its side facing the valve housing 42 a recess 57 into which the valve housing 42 is immersed. The valve housing 42 has in its the screw 54 facing the front side a central depression, into which the bore 46 opens. By lowering the valve housing 42, a space 60 is limited between this and the retaining screw 54, in which the bore 46 opens. The space 60 is connected to the second bore portion 46b through at least one bore 62 in the valve housing 42, the bore 62 being at least approximately parallel to the first bore portion 46a and laterally adjacent thereto. The space 60 is thus constantly connected to the second bore portion 46 b and thus to the fuel inlet passage 38.

Das Saugventil 30 weist außerdem wie in den Figuren 2, 5 und 6 dargestellt ein kolbenförmiges Ventilglied 64 auf, das einen zylindrischen Schaft 66 und einen im Querschnitt gegenüber dem Schaft 66 größeren Kopf 68 aufweist. Am Kopf 68 ist an dessen dem Schaft 66 zugewandtem Rand eine Dichtfläche 70 angeordnet, die zumindest annähernd kegelstumpfförmig ausgebildet ist und deren Mantelfläche unter einem Winkel δ zur Längsachse 65 des Ventilglieds 64 geneigt ist. An die Dichtfläche 70 schließt sich zu dem dem Schaft 66 abgewandten Ende des Kopfes 68 hin ein zylindrischer oder sich zumindest annähernd kegelstumpfförmig im Querschnitt erweiternder Bereich an. In diesem Bereich des Kopfes 68 sind mehrere über den Umfang des Kopfes 68 verteilte und voneinander beabstandete Führungsabschnitte 74 angeordnet, deren Außenkonturen auf einem gemeinsamen Durchmesser liegen. Die Führungsabschnitte 74 können dabei Teil des Kegelstumpfs des Bereichs des Kopfes 68 sein. Die Führungsabschnitte 74 können jedoch auch eine zumindest annähernd zylindrische Außenkontur aufweisen. Zwischen den Führungsabschnitten 74 sind im Querschnitt gegenüber diesen verringerter Abschnitte 76 vorhanden, die beispielsweise durch Anschliffe oder Abflachungen am Umfang des Kopfs 68 gebildet sind. Von der dem Schaft 66 abgewandten Stirnseite des Kopfes 68 des Ventilglieds 64 steht zumindest annähernd koaxial zu dessen Längsachse 65 ein kurzer Zapfen 78 hervor. Zwischen dem Schaft 66 und der Dichtfläche 70 sowie zwischen der Dichtfläche 70 und dem Kopf 68 mit den Führungsabschnitten 74 kann jeweils ein Freistich vorgesehen sein, um die Herstellbarkeit des Ventilglieds 64 zu vereinfachen. Zwischen der Dichtfläche 70 und dem Kopf 68 mit den Führungsabschnitten 74 ist vorzugsweise eine Ringnut 72 vorgesehen. Durch die Ringnut 72 wird das Öffnungsverhalten des Ventilglieds 64 verbessert, indem der in Öffnungsrichtung wirkende Druck auf die Dichtfläche 70 wirken kann, und damit die Befüllung des Pumpenarbeitsraums 24 verbessert. Außerdem wird das Verschleißverhalten der Dichtfläche 70 durch die Ringnut 72 verbessert, indem der Verschleiß der Dichtfläche 70 an der Ringnut 72 gestopt wird.The suction valve 30 also has as in the Figures 2 . 5 and 6 10 illustrates a piston-shaped valve member 64 which has a cylindrical shaft 66 and a head 68 which is larger in cross-section than the shaft 66. At the head 68, a sealing surface 70 is arranged at its edge facing the shaft 66, which is formed at least approximately frusto-conical and whose lateral surface is inclined at an angle δ to the longitudinal axis 65 of the valve member 64. The sealing surface 70 is adjoined by a cylindrical or at least approximately frusto-conical widening in cross section to the end of the head 68 facing away from the shaft 66. In this region of the head 68 a plurality of distributed over the circumference of the head 68 and spaced apart guide portions 74 are arranged, whose outer contours lie on a common diameter. The guide sections 74 may be part of the truncated cone of the region of the head 68. However, the guide portions 74 may also have an at least approximately cylindrical outer contour. Between the guide portions 74 are present in cross-section with respect to these reduced portions 76, which are formed for example by bevels or flats on the periphery of the head 68. From the shaft 66 facing away from the end face of the head 68 of the valve member 64 is at least approximately coaxially to the longitudinal axis 65, a short pin 78 out. Between the shaft 66 and the sealing surface 70 and between the sealing surface 70 and the head 68 with the guide portions 74, an undercut can be provided in each case to simplify the manufacturability of the valve member 64. Between the sealing surface 70 and the head 68 with the guide portions 74, an annular groove 72 is preferably provided. By the annular groove 72, the opening behavior of the valve member 64 is improved by the pressure acting in the opening direction can act on the sealing surface 70, and thus improves the filling of the pump working chamber 24. In addition, the wear behavior of the sealing surface 70 is improved by the annular groove 72 by the wear of the sealing surface 70 is stopped at the annular groove 72.

Das Ventilglied 64 ist mit seinem Schaft 66 im ersten Bohrungsabschnitt 46a des Ventilgehäuses 42 mit geringem Spiel verschiebbar geführt. Der erste Bohrungsabschnitt 46a bildet somit eine Führungsbohrung für den Schaft 66 des Ventilglieds 64. Außerdem ist das Ventilglied 64 über seine Führungsabschnitte 74 mit größerem Spiel im fünften Bohrungsabschnitt 46e des Ventilgehäuses 42 geführt. Durch die Führung des Ventilglieds 64 über seine Führungsabschnitte 74 im fünften Bohrungsabschnitt 46e wird sichergestellt, dass sich das Ventilglied 64 bei seiner Bewegung, insbesondere bei seiner Schließbewegung, mit seiner Längsachse 65 bezüglich der Längsachse 47 der Bohrung 46 und damit des Ventilsitzes 46c nur sehr gering verkippen kann, so dass eine gleichmäßige Anlage der Dichtfläche 70 des Ventilglieds 64 am Ventilsitz 46c bei der Schließbewegung sichergestellt ist. Die mögliche Verkippung der Längsachse 65 des Ventilglieds 64 bezüglich der Längsachse 47 der Bohrung 46 ist durch die Führungsabschnitte 74 beispielsweise auf maximal etwa 0,5°, vorzugsweise auf maximal etwa 0,25° begrenzt. Der Winkel α, unter dem die Mantelfläche des Ventilsitzes 46c zur Längsachse 47 geneigt ist, weicht ab von dem Winkel δ, unter dem die Mantelfläche der Dichtfläche 70 des Ventilglieds 64 zur Längsachse 47 geneigt ist. Der Winkel α kann dabei etwas größer sein als der Winkel δ, wobei die Differenz relativ gering sein kann und beispielsweise nur einige Winkelgrade oder nur etwa 1° betragen kann.The valve member 64 is slidably guided with its shaft 66 in the first bore portion 46 a of the valve housing 42 with a small clearance. The first bore portion 46a thus forms a guide bore for the shaft 66 of the valve member 64. In addition, the valve member 64 is guided over its guide portions 74 with greater clearance in the fifth bore portion 46e of the valve housing 42. By guiding the valve member 64 via its guide portions 74 in the fifth bore portion 46e it is ensured that the valve member 64 during its movement, in particular during its closing movement, with its longitudinal axis 65 with respect to the longitudinal axis 47 of the bore 46 and thus of the valve seat 46c only very small can tilt, so that a uniform contact of the sealing surface 70 of the valve member 64 is secured to the valve seat 46c during the closing movement. The possible tilting of the longitudinal axis 65 of the valve member 64 with respect to the longitudinal axis 47 of the bore 46 is limited by the guide portions 74, for example to a maximum of about 0.5 °, preferably to a maximum of about 0.25 °. The angle α, under which the lateral surface of the valve seat 46c is inclined to the longitudinal axis 47, deviates from the angle δ, under which the lateral surface of the sealing surface 70 of the valve member 64 is inclined to the longitudinal axis 47. The angle α can be slightly larger than the angle δ, wherein the difference can be relatively small and, for example, can be only a few degrees or only about 1 °.

Am Ventilglied 64 greift wie in Figur 2 dargestellt eine in Schließrichtung auf dieses wirkende Schließfeder 80 an, die sich einerseits am Pumpenkolben 20 und andererseits an der dem Pumpenkolben 20 zugewandten Stirnseite des Kopfes 68 des Ventilglieds 64 abstützt. Die Schließfeder 80 ist beispielsweise als Schraubendruckfeder ausgebildet und ist auf den Zapfen 78 am Ventilglied 64 aufgesteckt und wird durch diesen zentriert.On the valve member 64 engages as in FIG. 2 1 shows a closing spring 80 acting in the closing direction, which is supported on the pump piston 20 on the one hand and on the end face of the head 68 of the valve member 64 facing the pump piston 20 on the other hand. The closing spring 80 is formed, for example, as a helical compression spring and is placed on the pin 78 on the valve member 64 and is centered by this.

Das Ventilglied 64 ist in seiner Öffnungsrichtung von dem über die Zulaufkanäle 50 dem zweiten Bohrungsabschnitt 46b zugeführten, durch die Förderpumpe 14 erzeugten Druck beaufschlagt. Beim Saughub des Pumpenkolbens 20 herrscht im Kraftstoffzulauf ein durch die Förderpumpe 14 erzeugter höherer Druck als im Pumpenarbeitsraum 24, so dass das Ventilglied 64 gegen die Kraft der Schliessfeder 80 öffnet und mit seiner Dichtfläche 70 vom Ventilsitz 46c abhebt und dadurch einen ringförmigen Durchflussquerschnitt in den Pumpenarbeitsraum 24 freigibt. Im Bereich des Kopfes 68 des Ventilglieds 64 ist zwischen den Abschnitten 76 und dem fünften Bohrungsabschnitt 46e ein ausreichend großer Durchflussquerschnitt freigegeben, um ein Befüllen des Pumpenarbeitsraums 24 mit Kraftstoff zu ermöglichen. Das Einströmen des Kraftstoffs von den Zulaufkanälen 50 in den zweiten Bohrungsabschnitt 46b erfolgt dabei infolge der tangentialen Mündung der Zulaufkanäle 50 in den Bohrungsabschnitt 46b mit geringen Strömungsverlusten. Durch die tangentiale Mündung der Zulaufbohrungen 50 erhält der einströmende Kraftstoff einen Drall. Der Auslauf der Zulaufkanäle 50 im Bohrungsabschnitt 46b kann dabei gerundet sein. Somit wird eine gute Befüllung des Pumpenarbeitsraums 24 ermöglicht. Der Raum 60 zwischen dem Ventilgehäuse 42 und der Halteschraube 54 ist über die Bohrung 62 mit dem Kraftstoffzulauf 38 verbunden, so dass bei der Schließbewegung des Ventilgliedes 64 von diesem aus dem Raum 60 Kraftstoff in den Kraftstoffzulauf 38 verdrängt werden kann, wodurch ein schnelles Schließen des Saugventils 30 erreicht und ein Druckanstieg im Raum 60 vermieden wird.The valve member 64 is acted upon in its opening direction by the pressure supplied via the inlet channels 50 to the second bore section 46b, generated by the feed pump 14. During the intake stroke of the pump piston 20, a higher pressure generated by the feed pump 14 prevails in the fuel feed than in the pump working chamber 24, so that the valve member 64 opens against the force of the closing spring 80 and lifts off with its sealing surface 70 from the valve seat 46c and thereby an annular flow cross-section into the pump working space 24 releases. In the region of the head 68 of the valve member 64 between the sections 76 and the fifth bore portion 46 e, a sufficiently large flow cross section is released to allow filling of the pump working chamber 24 with fuel. The inflow of the fuel from the inlet channels 50 into the second bore section 46b takes place as a result of the tangential mouth of the inlet channels 50 into the bore section 46b with low flow losses. Due to the tangential mouth of the inlet bores 50, the incoming fuel receives a twist. The outlet of the inlet channels 50 in the bore section 46b can be rounded. Thus, a good filling of the pump working space 24 is made possible. The space 60 between the valve housing 42 and the retaining screw 54 is connected via the bore 62 with the fuel inlet 38, so that in the closing movement of the valve member 64 of this from the space 60 fuel can be displaced into the fuel inlet 38, whereby a rapid closing of the Suction valve 30 is reached and a pressure increase in the space 60 is avoided.

Beim Saughub des Pumpenkolbens 20, bei dem dieser sich nach innen zur Antriebswelle 18 hin bewegt, öffnet das Saugventil 30, da die durch den auf das Ventilglied 64 in Öffnungsrichtung im Kraftstoffzulauf 38 wirkenden Druck bewirkte Öffnungskraft größer ist als die Kraft der Schließfeder 80 und die durch den im Pumpenarbeitsraum 24 herrschenden geringen Druck in Schließrichtung auf das Ventilglied 64 erzeugte Kraft. Beim Förderhub des Pumpenkolbens 20, bei dem dieser sich nach außen von der Antriebswelle 18 weg bewegt, schließt das Saugventil 30, da die Summe der durch den im Pumpenarbeitsraum 24 herrschenden Druck erzeugten Kraft und der Kraft der Schließfeder 80 größer ist als die Öffnungskraft auf das Ventilglied 64.During the suction stroke of the pump piston 20, in which it moves inwards toward the drive shaft 18, the suction valve opens 30, as caused by the pressure acting on the valve member 64 in the opening direction in the fuel inlet 38 pressure opening force is greater than the force of the closing spring 80 and the force generated by the pressure prevailing in the pump working chamber 24 in the closing direction on the valve member 64. When the delivery stroke of the pump piston 20, in which it moves away from the drive shaft 18 to the outside, closes the suction valve 30, since the sum of the force generated by the pressure prevailing in the pump working chamber 24 and the force of the closing spring 80 is greater than the opening force on the Valve member 64.

In Figur 7 ist das Saugventil 30 gemäß einem zweiten Ausführungsbeispiel dargestellt, bei dem der grundsätzliche Aufbau gleich ist wie beim ersten Ausführungsbeispiel, jedoch das Ventilgehäuse und die Halteschraube einstückig als ein Ventilgehäuse 142 ausgebildet sind. Das Ventilglied 64 des Saugventils 30 ist identisch zum ersten Ausführungsbeispiel ausgebildet und wird daher nachfolgend nicht nochmals näher beschrieben. Im Ventilgehäuse 142 ist wie beim ersten Ausführungsbeispiel beschrieben die Bohrung 46 mit den Bohrungsabschnitten 46a,46b,46c,46d und 46e angeordnet, wobei die Bohrung 46 als Sackbohrung ausgebildet ist. Das Ventilglied 64 mit seinem Schaft 66 mit geringem Spiel in der Führungsbohrung 46a geführt und mit größerem Spiel mit seinem Kopf 68 über die Führungsabschnitte 74 im Bohrungsabschnitt 46e geführt. Das Ventilgehäuse 142 ist mit einem Außengewinde versehen, mit dem es in ein entsprechendes Innengewinde der Bohrung 34 im Gehäuseteil 36 der Hochdruckpumpe eingeschraubt ist, wobei die Abdichtung der Bohrung 34 nach außen durch den Dichtring 56 erfolgt. Die Abdichtung zwischen dem Ventilgehäuse 142 und der Ringschulter 40 am Übergang der Bohrung 34 zur Zylinderbohrung 22 erfolgt gleich wie beim ersten Ausführungsbeispiel. Der Kraftstoffzulaufkanal 38 mündet in die Bohrung 34 in den das Ventilgehäuse 142 umgebenden Ringraum 52. Im Ventilgehäuse 142 sind mehrere über dessen Umfang verteilte Kraftstoffzulaufkanäle 150 ausgebildet, die einerseits am Außenmantel des Ventilgehäuses 142 und andererseits in den zweiten Bohrungsabschnitt 46b münden. Der Verlauf der Zulaufkanäle 150 ist analog zum ersten Ausführungsbeispiele, so dass diese vorzugsweise zumindest annähernd tangential in den zweiten Bohrungsabschnitt 46b münden. Die Zulaufkanäle 150 können mit ihren Längsachsen 151 zumindest annähernd senkrecht zur Längsachse 47 der Bohrung 46 verlaufen oder wie in Figur 7 dargestellt derart, dass die Längsachse 151 der Zulaufkanäle 150 mit der Längsachse 47 der Bohrung 46 zum äußeren Ende des Ventilgehäuses 142 einen spitzen Winkel bilden. Im Ventilgehäuse 142 ist außerdem eine Bohrung 162 eingebracht, die einerseits am Außenmantel des Ventilgehäuses 142 in den Ringraum 52 und andererseits in den ersten Bohrungsabschnitt 46a in den durch den Schaft 66 des Ventilglieds 64 begrenzten Raum 160 mündet. Über die Bohrung 162 ist der Raum 160 somit ständig mit dem Kraftstoffzulaufkanal 38 verbunden. Zwischen dem Ventilgehäuse 142 und der Bohrung 34 des Gehäuseteils 36 ist der Dichtring 56 eingespannt, um den Ringraum 52, in dem der von der Förderpumpe 14 erzeugte Kraftstoffzulaufdruck herrscht, nach außen abzudichten. Die Abdichtung gegen den im Pumpenarbeitsraum 24 herrschenden Hochdruck erfolgt wie beim ersten Ausführungsbeispiel zwischen dem Gehäuseteil 36 und dem Ventilgehäuse 142 durch einen erhöhten Steg an einem dieser Teile oder durch einen separaten Dichtring.In FIG. 7 the suction valve 30 is shown according to a second embodiment, in which the basic structure is the same as in the first embodiment, but the valve housing and the retaining screw are integrally formed as a valve housing 142. The valve member 64 of the suction valve 30 is formed identical to the first embodiment and will therefore not be described again in more detail below. In the valve housing 142 as described in the first embodiment, the bore 46 with the bore portions 46a, 46b, 46c, 46d and 46e is arranged, wherein the bore 46 is formed as a blind bore. The valve member 64 is guided with its shaft 66 with little play in the guide bore 46a and guided with greater play with its head 68 via the guide portions 74 in the bore portion 46e. The valve housing 142 is provided with an external thread, with which it is screwed into a corresponding internal thread of the bore 34 in the housing part 36 of the high-pressure pump, wherein the sealing of the bore 34 takes place to the outside by the sealing ring 56. The seal between the valve housing 142 and the annular shoulder 40 at the transition of the bore 34 to the cylinder bore 22 is the same as in the first embodiment. The fuel inlet channel 38 opens into The bore 34 in the valve housing 142 surrounding annular space 52. In the valve housing 142 a plurality of circumferentially distributed fuel inlet channels 150 are formed, which open on the one hand on the outer surface of the valve housing 142 and on the other hand in the second bore portion 46 b. The course of the inlet channels 150 is analogous to the first exemplary embodiments, so that they preferably open at least approximately tangentially into the second bore section 46b. The inlet channels 150 may extend with their longitudinal axes 151 at least approximately perpendicular to the longitudinal axis 47 of the bore 46 or as in FIG. 7 illustrated such that the longitudinal axis 151 of the inlet channels 150 with the longitudinal axis 47 of the bore 46 to the outer end of the valve housing 142 form an acute angle. In the valve housing 142 also has a bore 162 is introduced, which opens on the one hand on the outer surface of the valve housing 142 in the annular space 52 and the other part in the first bore portion 46 a in the limited space by the shaft 66 of the valve member 64 space 160. Via the bore 162, the space 160 is thus permanently connected to the fuel inlet channel 38. Between the valve housing 142 and the bore 34 of the housing part 36 of the sealing ring 56 is clamped to seal the annular space 52, in which the fuel supply pressure generated by the feed pump 14, to the outside. The sealing against the pressure prevailing in the pump working chamber 24 high pressure takes place as in the first embodiment between the housing part 36 and the valve housing 142 by a raised web on one of these parts or by a separate sealing ring.

Claims (7)

  1. High-pressure pump for a fuel injection device of an internal combustion engine, having at least one pump element (16) which has a pump piston (20) which is driven in a reciprocating movement and which is movably guided in a cylinder bore (22) of a pump housing part (36) and which, in the cylinder bore (22), delimits a pump working space (24) which can be filled with fuel from a fuel supply (38) via a suction valve (30) during the suction stroke of the pump piston (20), with the suction valve (30) having a piston-shaped valve element (64) which interacts with a valve seat (46c) in order to control the connection of the pump working space (24) to the fuel supply (38), with the valve element (64) being acted on in the opening direction by the pressure prevailing in the fuel supply (38) and in the closing direction by the pressure prevailing in the pump working space (24), with the valve element (64) having a cylindrical shank (66) and a head (68) which is larger than the shank (66) in cross section, with at least the shank (66) of the valve element (64) being movably guided in a guide bore (46a) of a valve housing (42; 142), characterized in that, in addition, the head (68) of the valve element (64) is movably guided by means of guide sections (74), which are formed on said head (68) so as to be spaced apart from one another in the circumferential direction, in a bore (46e) of the valve housing (42;142), with throughflow sections (76), which are reduced in cross section in relation to the guide sections (74), being provided between the guide sections (74) on the head (68) of the valve element (64), which throughflow sections (76) serve to enable a fuel flow from the fuel supply (38) into the pump working space (24).
  2. High-pressure pump according to Claim 1, characterized in that the valve element (64) has, on its head (68) at the transition to the shank (66), an at least approximately frustoconical sealing surface (70), by means of which said valve element (64) interacts with the valve seat (46c).
  3. High-pressure pump according to Claim 2, characterized in that an annular groove (72) is arranged at the transition from the sealing surface (70) to the head (68) on the valve element (64).
  4. High-pressure pump according to one of Claims 1 to 3, characterized in that the valve element (64) serves, with the face end of its shank (66) which is guided in the bore (46a), to delimit a space (60;160) in the valve housing (42;142), which space (60;160) is permanently connected to the fuel inflow (38).
  5. High-pressure pump according to Claim 4, characterized in that the shank (66) of the valve element (64) is surrounded, in a region between its region arranged in the guide bore (46a) and the head (68) of the valve element (64), by a bore (46b), which is of greater diameter than the guide bore (46a), of the valve housing (42), in that the fuel supply (38) opens out into the bore (46b), and in that the space (60) which is delimited by the shank (66) of the valve element (64) is connected by means of at least one connecting bore (62) in the valve housing (42) to the bore (46b).
  6. High-pressure pump according to Claim 4, characterized in that the shank (66) of the valve element (64) is surrounded, in a region between its region arranged in the guide bore (46a) and the head (68) of the valve element (64), by a bore (46b), which is of greater diameter than the guide bore (46a), of the valve housing (142), in that an annular space (52) is formed between the valve housing (142) and a bore (34) of a pump housing part (36) into which the valve housing (142) is inserted, into which annular space (52) the fuel supply (38) opens out, and in that the bore (46b) and the space (160) which is delimited by the shank (66) of the valve element (64) are connected by means of in each case at least one connecting bore (150;162) to the annular space (52).
  7. High-pressure pump according to one of Claims 1 to 6, characterized in that a closing spring (80) engages on the valve element (64), which closing spring (80) is preferably supported at least indirectly on the pump piston (20).
EP05760887A 2004-08-28 2005-07-05 High-pressure pump for a fuel injection device of an internal combustion engine Not-in-force EP1784571B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004041764A DE102004041764A1 (en) 2004-08-28 2004-08-28 High-pressure pump for a fuel injection device of an internal combustion engine
PCT/EP2005/053183 WO2006024569A1 (en) 2004-08-28 2005-07-05 High-pressure pump for a fuel injection device of an internal combustion engine

Publications (2)

Publication Number Publication Date
EP1784571A1 EP1784571A1 (en) 2007-05-16
EP1784571B1 true EP1784571B1 (en) 2008-12-10

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EP05760887A Not-in-force EP1784571B1 (en) 2004-08-28 2005-07-05 High-pressure pump for a fuel injection device of an internal combustion engine

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US (1) US7571713B2 (en)
EP (1) EP1784571B1 (en)
JP (1) JP4571980B2 (en)
CN (1) CN100575700C (en)
AT (1) ATE417200T1 (en)
DE (2) DE102004041764A1 (en)
WO (1) WO2006024569A1 (en)

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DE102006017036A1 (en) * 2006-04-11 2007-10-18 Siemens Ag Radial piston pump for fuel high pressure supply in an internal combustion engine
AT503697B1 (en) * 2006-06-02 2008-06-15 Bosch Gmbh Robert PUMP ELEMENT FOR A HIGH PRESSURE PUMP
IT1395606B1 (en) * 2009-09-14 2012-10-16 Bosch Gmbh Robert HIGH PRESSURE PUMP IMPROVED FOR FUEL SUPPLY TO AN INTERNAL COMBUSTION ENGINE AND IMPROVED TREE SEAL RING FOR THE SAME
US9188096B2 (en) * 2011-09-06 2015-11-17 Toyota Jidosha Kabushiki Kaisha Fuel pump and fuel supply system of internal combustion engine
US9816493B2 (en) * 2013-03-21 2017-11-14 Exergy Engineering Llc Fuel injection pump
DE102013210036A1 (en) * 2013-05-29 2014-12-04 Robert Bosch Gmbh High pressure pump for a fuel injection system
CN104061100A (en) * 2014-06-30 2014-09-24 南岳电控(衡阳)工业技术有限公司 Sealing structure used in high-pressure fuel feed pump
IT201700095355A1 (en) * 2017-08-23 2019-02-23 Bosch Gmbh Robert PUMP UNIT FOR FUEL SUPPLY TO AN INTERNAL COMBUSTION ENGINE

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US3338257A (en) * 1964-05-22 1967-08-29 Westinghouse Air Brake Co Double check valve
US4569273A (en) * 1983-07-18 1986-02-11 Dynex/Rivett Inc. Three-way proportional valve
JPH07259696A (en) * 1994-03-18 1995-10-09 Yanmar Diesel Engine Co Ltd Delivery valve of fuel injection pump
US5676169A (en) * 1996-01-24 1997-10-14 Power Team Division Of Spx Corporation Counterbalance valve
US5738142A (en) * 1996-08-09 1998-04-14 Case Corporation Pressure holding directional control valve
DE19744577A1 (en) 1997-10-09 1999-04-22 Bosch Gmbh Robert Radial piston pump for high pressure fuel supply in motor vehicles
DE19848040A1 (en) 1998-10-17 2000-04-20 Bosch Gmbh Robert Radial piston pump for high fuel pressure in IC engines with common-rail injection systems has two plates engaging fully on each other, and second back pressure valve between first plate and pump housing
DE10117600C1 (en) * 2001-04-07 2002-08-22 Bosch Gmbh Robert High-pressure fuel pump for a fuel system of a direct-injection internal combustion engine, fuel system and internal combustion engine
ITTO20011039A1 (en) * 2001-10-30 2003-04-30 Ct Studi Componenti Per Veicol SUCTION VALVE FOR A HIGH PRESSURE PUMP, IN PARTICULAR FOR FUEL OF AN ENDOTHERMAL ENGINE.

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DE102004041764A1 (en) 2006-03-02
JP2008511787A (en) 2008-04-17
CN101010508A (en) 2007-08-01
ATE417200T1 (en) 2008-12-15
US7571713B2 (en) 2009-08-11
US20070251499A1 (en) 2007-11-01
WO2006024569A1 (en) 2006-03-09
CN100575700C (en) 2009-12-30
JP4571980B2 (en) 2010-10-27
EP1784571A1 (en) 2007-05-16
DE502005006224D1 (en) 2009-01-22

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