EP1716332A1 - High pressure pump, in particular for a fuel injection device in an internal combustion engine - Google Patents

High pressure pump, in particular for a fuel injection device in an internal combustion engine

Info

Publication number
EP1716332A1
EP1716332A1 EP05701509A EP05701509A EP1716332A1 EP 1716332 A1 EP1716332 A1 EP 1716332A1 EP 05701509 A EP05701509 A EP 05701509A EP 05701509 A EP05701509 A EP 05701509A EP 1716332 A1 EP1716332 A1 EP 1716332A1
Authority
EP
European Patent Office
Prior art keywords
valve
valve member
lateral surface
section
sealing surface
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.)
Withdrawn
Application number
EP05701509A
Other languages
German (de)
French (fr)
Inventor
Nestor Rodriguez-Amaya
Michael Mennicken
Peter Brendle
Falko Bredow
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
Priority claimed from DE102004027825A external-priority patent/DE102004027825A1/en
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1716332A1 publication Critical patent/EP1716332A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/06—Check valves with guided rigid valve members with guided stems
    • F16K15/063—Check valves with guided rigid valve members with guided stems the valve being loaded by a spring
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • 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
    • 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
    • F04B53/10—Valves; Arrangement of 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
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/1002—Ball valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/04—Check valves with guided rigid valve members shaped as balls
    • F16K15/044—Check valves with guided rigid valve members shaped as balls spring-loaded
    • 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

Definitions

  • High-pressure pump in particular for a fuel injection device of an internal combustion engine
  • the invention is based on a high-pressure pump, in particular for a fuel injection device of an internal combustion engine according to the preamble of claim 1.
  • Such a high pressure pump is known from DE 198 60 672 AI.
  • This high-pressure pump has at least one pump element with a pump piston which is driven in a lifting movement and delimits a pump working space.
  • fuel is drawn in from a fuel inlet via an inlet valve, and during the delivery stroke of the pump piston, fuel is displaced from the pump work space via an outlet valve.
  • the inlet valve has a valve member with a sealing surface inclined to its longitudinal axis, with which it cooperates with a valve seat arranged in a valve housing.
  • the outlet valve has a spherical valve member which interacts with a valve seat arranged in a valve housing.
  • a flow cross-section between the valve member and the valve housing is released by the respective valve member in the open state, when the sealing surface is lifted off the valve seat.
  • the smallest flow cross-section is arranged between the valve member and the valve housing in the area of the sealing surface of the valve member, as a result of which there is a high flow velocity and correspondingly a low static pressure in the area of the sealing area and consequently only a small in Force acting in the opening direction of the valve member.
  • even forces in the closing direction can act on the valve member.
  • the high pressure pump according to the invention with the features according to claim 1 has the advantage that the
  • FIG. 1 shows a high pressure pump for a fuel injection device of an internal combustion engine
  • FIG. 2 shows an inlet valve of the high pressure pump in an enlarged illustration in a longitudinal section
  • FIG. 3 shows a modified embodiment of the inlet valve
  • FIG. 4 shows an outlet valve of the high pressure pump in a longitudinal section.
  • the high-pressure pump 10 for a fuel injection device of an internal combustion engine, which is preferably a self-igniting internal combustion engine.
  • the high-pressure pump 10 delivers fuel under high pressure into a reservoir 12, from which fuel is taken for injection at the internal combustion engine.
  • the high-pressure pump 10 is supplied with fuel by a feed pump 14.
  • the high-pressure pump 10 has at least one pump element 16, which is driven at least indirectly by a drive shaft 18 of the high-pressure pump 10 in a lifting movement Has pump piston 20.
  • the pump piston 20 is tightly guided in a cylinder bore 22 that extends at least approximately radially to the drive shaft 18 and delimits a pump work chamber 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 that is eccentric to its axis of rotation 19 , via which the stroke movement of the pump piston 20 is effected during the rotary movement of the drive shaft 18.
  • the pump working space 24 is via a opening in the pump working space 24 as
  • Check valve designed inlet valve 30 can be connected to a fuel supply from the feed pump 14.
  • the pump work chamber 24 can also be connected to a fuel outlet to the reservoir 12 via an outlet valve 32 that opens out of the pump work chamber 24 and is designed as a check valve.
  • Inlet valve 30 opened because the feed pump 14 generates a higher pressure than the pressure prevailing in the pump work chamber 24, so that fuel delivered by the feed pump 14 is drawn into the pump work chamber 24.
  • the outlet valve 32 is at the suction stroke of the
  • the inlet valve 30 is described in more detail by way of example with reference to FIG. 2.
  • the inlet valve 30 is inserted, for example, into a bore 34 of a housing part 36 of the high-pressure pump 10 that adjoins the cylinder bore 22 radially outward.
  • the bore 34 is larger in diameter than the cylinder bore 22.
  • the housing part 36 can be, for example, a cylinder head which is connected to a other housing part, in which the drive shaft 18 is mounted, is connected or a housing part in which the drive shaft 18 is also mounted.
  • a fuel feed channel 38 which is connected to the feed pump 14, opens into the bore 34 near its end region facing the cylinder bore 22, for example approximately radially to the axis of the bore 34.
  • the inlet valve 30 has a valve housing 40 in which there is a bore 42 which is stepped several times in diameter.
  • the bore 42 has a section 42a with a small diameter, a section 42b with a larger diameter adjoining the section 42a to the pump work chamber 24, a section 42c adjoining the section 42b to the pump work chamber 24 and a section 42c to the pump work chamber 24 on subsequent section 42d.
  • the inlet valve 30 has a piston-shaped valve member 44, which is displaceably guided with a cylindrical shaft 44a in the bore section 42a.
  • the valve member 44 also has a head 46 adjoining the shaft 44a and enlarged in diameter compared to the shaft 44a, a sealing surface 48 being arranged on the valve member 44 at the transition from the head 46 to the shaft 44a.
  • the sealing surface 48 extends at an angle ⁇ inclined to the longitudinal axis 45 of the valve member 44 in such a way that the sealing surface 48 approaches the longitudinal axis 45 towards the stem 44a.
  • the sealing surface 48 is preferably at least approximately frustoconical.
  • the head 46 of the valve member 44 can be at least approximately cylindrical.
  • the head 46 of the valve member 44 faces the pump working chamber 24.
  • the end 44a of the valve member 44 protrudes from the bore section 42a with its end facing away from the head 46 and a prestressed closing spring 43 engages it.
  • At least one inlet channel 50 is introduced into the valve housing 40 and opens into the bore section 42b.
  • several, for example three, inlet channels 50 are provided which are uniformly distributed over the circumference of the valve housing 40.
  • the bore section 42c is designed such that its diameter widens away from the bore section 42b towards the bore section 42d.
  • the lateral surface of the bore section 42c is preferably frustoconical, but can also be shaped in any other way, for example concave or convex.
  • the lateral surface of the bore section 42c is inclined at an angle ⁇ to the longitudinal axis 45 of the valve member 44.
  • the angle of inclination ⁇ of the lateral surface of the bore section 42c is preferably somewhat larger than the angle ⁇ at which the sealing surface 48 of the valve member 44 is inclined, but can also be somewhat smaller than the angle ⁇ .
  • the bore section 42c forms a valve seat with which the sealing surface 48 of the valve member 44 cooperates. In the closed state, the valve member 44 rests with its sealing surface 48 on the bore section 42c, the sealing surface 48 being in contact with the edge of the bore section 42c facing the bore section 42b due to the difference between the inclination angles ⁇ and ⁇ .
  • the bore section 42d is designed such that its diameter moves away from the bore section 42c
  • the lateral surface of the bore section 42d is preferably frustoconical, but can also be shaped in any other way, for example concave or convex.
  • the lateral surface of the bore section 42d is inclined at an angle ⁇ to the longitudinal axis 45 of the valve member 44.
  • the angle ⁇ , at which the lateral surface of the bore section 42d is inclined to the longitudinal axis 45, is smaller than the angle ⁇ , at which the lateral surface of the bore section 42c
  • Longitudinal axis 45 extends inclined.
  • the undercut 42e preferably has a lateral surface running at least approximately parallel to the longitudinal axis 45.
  • the outer diameter of the head 46 of the valve member 44 is slightly smaller than the diameter of the undercut 42e, so that the edge at the transition from the head 46 to the sealing surface 48 can dip somewhat into the undercut 42e in the closed state. The undercut 42e thus avoids a collision between the head 46 of the valve member 44 and the valve housing 40.
  • Valve housing 40 with the bore sections 42c and 42d, the angles of inclination ⁇ and ⁇ of which are different, is achieved in that in the open state, when the valve member 44 is raised with its sealing surface 48 from the bore section 42c forming the valve seat, the area 52 of the smallest flow cross section between the cylindrical portion of the head 46 of the valve member 44 and the bore portion 42d. In this area 52 of the smallest flow cross section, the highest is when the inlet valve 30 is open
  • the region 52 is thus arranged downstream of the sealing surface 48 of the valve member 44 in the flow direction of the fuel from the inlet channel 50 into the pump work chamber 24.
  • This static pressure acting on the sealing surface 48 of the valve member 44 generates a force acting on the valve member 44 in the opening direction and thus supports the Opening movement of the valve member 44 and the stable arrangement of the valve member 44 in its open state.
  • the inlet valve 30 opens when the force generated in the opening direction on the valve member 44 by the pressure prevailing in the fuel inlet 38, which acts on the part of the sealing surface 48 arranged within the valve seat 42c, is greater than the sum is the force generated by the pressure on the valve member 44 in the pump working space 24 and the force generated by the closing spring 43.
  • the valve member 44 with its sealing surface 48 is lifted off the valve seat 42c, the entire sealing surface 48 is pressurized, the area 52 having the smallest being arranged
  • FIG. 3 shows a modified embodiment of the inlet valve 30, in which the basic structure is the same as in the embodiment according to FIG. 2, but the valve member 44 is modified.
  • the head 46 of the valve member 44 has, toward its end facing the shaft 44a, an area 47 with a reduced diameter compared to the remaining diameter of the head 46.
  • the area 47 of the head 46 of the valve member 44 which has a reduced diameter, is arranged such that, when the valve member 44 is arranged in its closed position, it lies opposite the transition between the first lateral surface 42c and the second lateral surface 42d of the valve housing 40. Due to the reduction in diameter in the area 47, a collision of the head 46 of the Avoided valve member 44 with the valve housing 40.
  • a shoulder is formed on the head 46 of the valve member 44 at its transition to the sealing surface 48.
  • the transition from the area 47 to the remaining part of the head 46 of the valve member 44 with a large diameter can be rounded as shown in FIG.
  • the head 46 of the valve member 44 can be approximately cylindrical as shown in FIG. 2 or approximately frustoconical as shown in FIG. 3, the diameter of the head 46 increasing
  • Exhaust valve 32 is described in more detail below by way of example with reference to FIG. 4.
  • the outlet valve 32 is inserted, for example, into a bore 54 in the housing part 36.
  • a fuel drain channel 56 which is connected to the accumulator 12, opens into the bore 54 approximately radially to its longitudinal axis.
  • the housing part 36 forms a valve housing for the outlet valve 32, alternatively a separate valve housing for the outlet valve 32 inserted into the housing part 36 can also be provided.
  • the bore 54 in the housing part 36 has a multiple stepped diameter and has a small-diameter section 54a opening into the pump working space 24.
  • a further bore portion 54b adjoins the bore portion 54a away from the pump workspace 24, the diameter of which increases away from the pump workspace 24.
  • the bore section 54b is preferably at least approximately frustoconical, but can alternatively also have a concave or convex curved surface.
  • the lateral surface of the bore section 54b extends at an angle ⁇ inclined to the longitudinal axis 55 of the bore 54.
  • a further bore section 54c adjoins the bore section 54b away from the pump working space 24, the latter Diameter increases away from the pump working space 24.
  • the bore section 54c is preferably at least approximately frustoconical, but can alternatively also have a concave or convex curved surface.
  • the outer surface of the bore section 54b is preferably at least approximately frustoconical, but can alternatively also have a concave or convex curved surface.
  • the outer surface of the bore section 54b is preferably at least approximately frustoconical, but can alternatively also have a concave or convex curved surface.
  • Bore section 54c extends at an angle ⁇ inclined to the longitudinal axis 55 of the bore 54, the angle ⁇ being smaller than the angle ⁇ .
  • a further bore portion 54d with a constant diameter can be connected to the bore portion 54c and extends to the outside of the housing part 36.
  • a closure element 58 is inserted, for example screwed, into the bore section 54d from the outside of the housing part 36.
  • the outlet valve 32 has a valve member 60 which is at least approximately spherical.
  • a closing spring 62 can be provided, which is clamped between the valve member 60 and the closure element 58 and through which the valve member 60 is pressed toward the pump working space 24.
  • the valve member 60 cooperates with a sealing surface 64, which is formed by part of its surface, with the bore section 54b, which forms a valve seat for the valve member 60.
  • the valve member 60 is held by the closing spring 62 with its sealing surface 64 in contact with the valve seat 54b.
  • the outlet valve 32 opens because the force generated by the pressure acting on the valve member 60 in the opening direction is greater than the force of the closing spring 62.
  • a flow cross section is released between the sealing surface 64 of the valve member 60 and the valve seat 54b.
  • a region 66 with a released flow cross section is likewise arranged between the circumference of the valve member 60 and the bore section 54c, the flow cross section when the valve is open is smaller in the region 66 than the flow cross section released between the sealing surface 64 and the valve seat 54b. Throttling of the fuel flow when flowing through the opened outlet valve 32 thus takes place in the area 66 with the smallest flow cross-section and not in the area of the sealing surface 64 of the valve member 60. In the area of the sealing surface 64 of the valve member 60 there is therefore a lower flow velocity than in the area 66 of the smallest flow cross-section and therefore a higher static pressure than in area 66.
  • valve member 60 When the outlet valve 32 is opened, when its valve member 60 lifts with its sealing surface 64 from the valve seat 54b, the surface area of the valve member 60 under pressure is increased, since then it is no longer only the surface lying inside the valve seat 54b that is pressurized but the larger surface with the area 66 out. A large compressive force therefore acts on the valve member 60
  • Opening direction that holds the valve member 60 stably in its open state even when a large amount of fuel flows through the exhaust valve 32 at a high flow rate.
  • both the flow cross-section released between its sealing surface 64 and the valve seat 54b and the flow cross-section released in the region 66 increase, the flow cross-section released in the region 66 always being smaller than that between the sealing surface 64 and the valve seat 54b approved flow cross-section.
  • the angle ⁇ at which the valve seat 54b is inclined to the longitudinal axis 55 of the bore 54, can be chosen large, so that the valve seat 54b is relatively flat and thus has a high wear resistance.
  • the outlet valve 32 is designed as described above for FIG. 4, while the inlet valve 30 can be designed as a simple conical seat or ball valve.
  • a valve as described with reference to FIG. 4 as an outlet valve with a spherical valve member can also be used as an inlet valve on a high-pressure pump.
  • a valve as described with reference to FIG. 2 or 3 as an inlet valve with a valve member with a conical sealing surface can also be used as an outlet valve on a high-pressure pump.
  • both the inlet valve 30 and the outlet valve 32 are preferably designed as described above for FIGS. 2 or 3 and 4.

Landscapes

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

Abstract

The invention concerns a high pressure pump comprising at least one pump component (16) wherein, upon the suction stroke of a pump piston (20), fuel from the fuel supply conduit (50) is sucked by an intake valve (30), the fuel being delivered by a delivery valve (32) upon the delivery stroke of the pump piston (20). The intake valve (30) comprises a component (44) whereof one sealing surface (48) inclined towards its longitudinal axis (45) co-operates with a valve seat (42c) arranged in a valve cage (40). Said valve component (44) enables, in an open state, when the sealing surface (48) of the valve component (44) is released from the valve seat (42c), a flow cross-section between the fuel supply conduit (50) and the pump working space (24) to be cleared between said valve component (44) and the valve cage (40). The valve component (44) being opened, a zone (52) provided with the smallest flow cross-section between the valve component (44) and the valve cage (40), in the direction of the flow circulating from the fuel supply conduit (50) towards the pump working space (24), is provided downstream of the flow and the sealing surface (48) of the valve component (44).

Description

Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer BrennkraftmaschineHigh-pressure pump, in particular for a fuel injection device of an internal combustion engine
Stand der TechnikState of the art
Die Erfindung geht aus von einer Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine nach der Gattung des Anspruchs 1.The invention is based on a high-pressure pump, in particular for a fuel injection device of an internal combustion engine according to the preamble of claim 1.
Eine solche Hochdruckpumpe ist durch die DE 198 60 672 AI bekannt. Diese Hochdruckpumpe weist wenigstens ein Pumpenelement auf mit einem in einer Hubbewegung angetriebenen Pumpenkolben, der einen Pumpenarbeitsraum begrenzt. Beim Saughub des Pumpenkolbens wird über ein Einlassventil Kraftstoff aus einem KraftstoffZulauf angesaugt und beim Förderhub des Pumpenkolbens wird über ein Auslassventil Kraftstoff aus dem Pumpenarbeitsraum verdrängt. Das Einlassventil weist ein Ventilglied mit einer zu seiner Längsachse geneigten Dichtfläche auf, mit der dieses mit einem in einem Ventilgehäuse angeordneten Ventilsitz zusammenwirkt. Das Auslassventil weist ein kugelförmiges Ventilglied auf, das mit einem in einem Ventilgehäuse angeordneten Ventilsitz zusammenwirkt. Durch das jeweilige Ventilglied wird in geöffnetem Zustand, wenn dieses mit seiner Dichtfläche vom Ventilsitz abgehoben ist, zwischen dem Ventilglied und dem Ventilgehäuse ein Durchflussquerschnitt freigegeben. In geöffnetem Zustand des Ventils ist dabei der kleinste Durchflussquerschnitt zwischen dem Ventilglied und dem Ventilgehäuse im Bereich der Dichtfläche des Ventilglieds angeordnet, wodurch sich dort eine hohe Strömungsgeschwindigkeit und entsprechend ein geringer statischer Druck im Bereich der Dichtfläche ergeben und infolgedessen nur eine geringe in Öffnungsrichtung des Ventilglieds wirkende Kraft. Es können je nach Hub des Venitlglieds und Druckdifferenz sogar Kräfte in Schließrichtung auf das Ventilglied wirken. Zum Offenhalten des Einlassventils ist daher eine große Druckdifferenz zwischen dem Kraftstoffzulauf und demSuch a high pressure pump is known from DE 198 60 672 AI. This high-pressure pump has at least one pump element with a pump piston which is driven in a lifting movement and delimits a pump working space. During the suction stroke of the pump piston, fuel is drawn in from a fuel inlet via an inlet valve, and during the delivery stroke of the pump piston, fuel is displaced from the pump work space via an outlet valve. The inlet valve has a valve member with a sealing surface inclined to its longitudinal axis, with which it cooperates with a valve seat arranged in a valve housing. The outlet valve has a spherical valve member which interacts with a valve seat arranged in a valve housing. A flow cross-section between the valve member and the valve housing is released by the respective valve member in the open state, when the sealing surface is lifted off the valve seat. When the valve is open, the smallest flow cross-section is arranged between the valve member and the valve housing in the area of the sealing surface of the valve member, as a result of which there is a high flow velocity and correspondingly a low static pressure in the area of the sealing area and consequently only a small in Force acting in the opening direction of the valve member. Depending on the stroke of the valve member and pressure difference, even forces in the closing direction can act on the valve member. To keep the inlet valve open, there is therefore a large pressure difference between the fuel inlet and the
Pumpenarbeitsraum erforderlich, was wiederum einen hohen Druck im Kraftstoffzulauf und damit eine entsprechend groß dimensionierte Förderpumpe zur Erzeugung dieses Drucks erfordert. Bei der Durchströmung des Einlassventils tritt darüberhinaus ein großer Druckverlust auf, wodurch die Befüllung des Pumpenarbeitsraums erschwert wird. Dieser Druckverlust entspricht der erforderlichen Druckdifferenz zur Befüllung des Pumpenarbeitsraums. Das Auslassventil neigt durch die entstehenden hydraulischen Kräfte zum Schwingen, so dass das Auslassventil ständig öffnet und schließt, wodurch das Betriebsverhalten der Hochdruckpumpe beeinträchtigt wird und eine hohe Belastung der Hochdruckpumpe infolge von im Pumpenarbeitsraum bei geschlossenem Auslassventil auftretenden Druckspitzen verursacht wird.Pump work space required, which in turn requires a high pressure in the fuel supply and thus a correspondingly large feed pump to generate this pressure. In addition, when the inlet valve flows through, there is a large pressure loss, which makes it difficult to fill the pump work space. This pressure loss corresponds to the pressure difference required to fill the pump work space. The outlet valve tends to vibrate due to the hydraulic forces that arise, so that the outlet valve constantly opens and closes, which impairs the operating behavior of the high-pressure pump and causes a high load on the high-pressure pump as a result of pressure peaks occurring in the pump work space when the outlet valve is closed.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Hochdruckpumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass zumThe high pressure pump according to the invention with the features according to claim 1 has the advantage that the
Offenhalten des Einlassventils und/oder des Auslassventils nur eine geringe Druckdifferenz vor und nach dem Ventil erforderlich ist, da durch die Verlagerung des kleinsten Durchflussquerschnitts von der Dichtfläche weg nach außen sich im Bereich der Dichtfläche ein höherer statischerKeeping the inlet valve and / or the outlet valve open requires only a small pressure difference before and after the valve, since the displacement of the smallest flow cross-section away from the sealing surface leads to a higher static area in the region of the sealing surface
Druck ergibt, durch den eine große in Öffnungsrichtung auf das Ventilglied wirkende Kraft erzeugt wird. Der Druck im Kraftstoffzulauf kann dadurch relativ gering gehalten werden, was eine entsprechend kleiner dimensionierte Förderpumpe ermöglicht, und infolge der geringerenPressure results, by which a large force acting in the opening direction on the valve member is generated. As a result, the pressure in the fuel feed can be kept relatively low, which enables a correspondingly smaller delivery pump, and as a result of the lower
Druckverluste bei der Durchströmung des Einlassventils wird die Befüllung des Pumpenarbeitsraums verbessert. Beim Auslassventil wird durch die Verlagerung des kleinsten Durchflussquerschnitts ein stabiles Öffnen sichergestellt, so dass die Belastung der Hochdruckpumpe verringert ist.Pressure loss in the flow through the inlet valve the filling of the pump workspace improved. With the outlet valve, the shifting of the smallest flow cross-section ensures stable opening, so that the load on the high-pressure pump is reduced.
In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Hochdruckpumpe angegeben. Durch die Ausbildung gemäß Anspruch 2 ist die Anordnung des kleinsten Durchflussquerschnitts stromabwärts nach der Dichtfläche des Ventilglieds auf einfache Weise ermöglicht.Advantageous refinements and developments of the high-pressure pump according to the invention are specified in the dependent claims. The arrangement according to claim 2 enables the arrangement of the smallest flow cross-section downstream after the sealing surface of the valve member in a simple manner.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine, Figur 2 ein Einlassventil der Hochdruckpumpe in vergrößerter Darstellung in einem Längsschnitt, Figur 3 eine modifizierte Ausführung des Einlassventils und Figur 4 ein Auslassventil der Hochdruckpumpe in einem Längsschnitt.An embodiment of the invention is shown in the drawing and explained in more detail in the following description. 1 shows a high pressure pump for a fuel injection device of an internal combustion engine, FIG. 2 shows an inlet valve of the high pressure pump in an enlarged illustration in a longitudinal section, FIG. 3 shows a modified embodiment of the inlet valve and FIG. 4 shows an outlet valve of the high pressure pump in a longitudinal section.
Beschreibung des AusführungsbeispielsDescription of the embodiment
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 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 Pumpenarbeitsraum 24 ist über ein in den Pumpenarbeitsraum 24 öffnendes, als1 shows a high-pressure pump 10 for a fuel injection device of an internal combustion engine, which is preferably a self-igniting internal combustion engine. The high-pressure pump 10 delivers fuel under high pressure into a reservoir 12, from which fuel is taken for injection at the internal combustion engine. The high-pressure pump 10 is supplied with fuel by a feed pump 14. The high-pressure pump 10 has at least one pump element 16, which is driven at least indirectly by a drive shaft 18 of the high-pressure pump 10 in a lifting movement Has pump piston 20. The pump piston 20 is tightly guided in a cylinder bore 22 that extends at least approximately radially to the drive shaft 18 and delimits a pump work chamber 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 that is eccentric to its axis of rotation 19 , via which the stroke movement of the pump piston 20 is effected during the rotary movement of the drive shaft 18. The pump working space 24 is via a opening in the pump working space 24 as
Rückschlagventil ausgebildetes Einlassventil 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 dasCheck valve designed inlet valve 30 can be connected to a fuel supply from the feed pump 14. The pump work chamber 24 can also be connected to a fuel outlet to the reservoir 12 via an outlet valve 32 that opens out of the pump work chamber 24 and is designed as a check valve. During the suction stroke, the pump piston 20 moves radially inward in the cylinder bore 22, so that the volume of the pump working space 24 is increased. During the suction stroke of the pump piston 20, this is due to the pressure difference that exists
Einlassventil 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 desInlet valve 30 opened because the feed pump 14 generates a higher pressure than the pressure prevailing in the pump work chamber 24, so that fuel delivered by the feed pump 14 is drawn into the pump work chamber 24. The outlet valve 32 is at the suction stroke of the
Pumpenkolbens 20 geschlossen, da im Speicher 12 ein höherer Druck als im Pumpenarbeitsraum 24 herrscht.Pump piston 20 closed, since there is a higher pressure in the accumulator 12 than in the pump work chamber 24.
Nachfolgend wird beispielhaft das Einlassventil 30 anhand der Figur 2 näher beschrieben. Das Einlassventil 30 ist beispielsweise 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 anderen 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. Das Einlassventil 30 weist ein Ventilgehäuse 40 auf, in dem eine im Durchmesser mehrfach gestufte Bohrung 42 vorhanden ist. Die Bohrung 42 weist einen im Durchmesser kleinen Abschnitt 42a auf, einen sich an den Abschnitt 42a zum Pumpenarbeitsraum 24 anschließenden Abschnitt 42b mit größerem Durchmesser, einen sich an den Abschnitt 42b zum Pumpenarbeitsraum 24 hin anschließenden Abschnitt 42c und einen sich an den Abschnitt 42c zum Pumpenarbeitsraum 24 hin anschließenden Abschnitt 42d auf. Das Einlassventil 30 weist ein kolbenförmiges Ventilglied 44 auf, das mit einem zylindrischen Schaft 44a im Bohrungsabschnitt 42a verschiebbar geführt ist. Das Ventilglied 44 weist außerdem einen an den Schaft 44a anschließenden, im Durchmesser gegenüber dem Schaft 44a vergrößerten Kopf 46 auf, wobei am Übergang vom Kopf 46 zum Schaft 44a eine Dichtfläche 48 am Ventilglied 44 angeordnet ist. Die Dichtfläche 48 verläuft unter einem Winkel γ geneigt zur Längsachse 45 des Ventilglieds 44, derart, dass sich die Dichtfläche 48 der Längsachse 45 zum Schaft 44a hin annähert. Die Dichtfläche 48 ist vorzugsweise zumindest annähernd kegelstumpfförmig ausgebildet. An die Dichtfläche 48 anschließend kann der Kopf 46 des Ventilglieds 44 zumindest annähernd zylinderförmig ausgebildet sein. Der Kopf 46 des Ventilglieds 44 weist zum Pumpenarbeitsraum 24. Der Schaft 44a des Ventilglieds 44 ragt mit seinem dem Kopf 46 abgewandten Ende aus dem Bohrungsabschnitt 42a heraus und an diesem greift eine vorgespannte Schließfeder 43 an.In the following, the inlet valve 30 is described in more detail by way of example with reference to FIG. 2. The inlet valve 30 is inserted, for example, into a bore 34 of a housing part 36 of the high-pressure pump 10 that adjoins the cylinder bore 22 radially outward. The bore 34 is larger in diameter than the cylinder bore 22. The housing part 36 can be, for example, a cylinder head which is connected to a other housing part, in which the drive shaft 18 is mounted, is connected or a housing part in which the drive shaft 18 is also mounted. A fuel feed channel 38, which is connected to the feed pump 14, opens into the bore 34 near its end region facing the cylinder bore 22, for example approximately radially to the axis of the bore 34. The inlet valve 30 has a valve housing 40 in which there is a bore 42 which is stepped several times in diameter. The bore 42 has a section 42a with a small diameter, a section 42b with a larger diameter adjoining the section 42a to the pump work chamber 24, a section 42c adjoining the section 42b to the pump work chamber 24 and a section 42c to the pump work chamber 24 on subsequent section 42d. The inlet valve 30 has a piston-shaped valve member 44, which is displaceably guided with a cylindrical shaft 44a in the bore section 42a. The valve member 44 also has a head 46 adjoining the shaft 44a and enlarged in diameter compared to the shaft 44a, a sealing surface 48 being arranged on the valve member 44 at the transition from the head 46 to the shaft 44a. The sealing surface 48 extends at an angle γ inclined to the longitudinal axis 45 of the valve member 44 in such a way that the sealing surface 48 approaches the longitudinal axis 45 towards the stem 44a. The sealing surface 48 is preferably at least approximately frustoconical. Following the sealing surface 48, the head 46 of the valve member 44 can be at least approximately cylindrical. The head 46 of the valve member 44 faces the pump working chamber 24. The end 44a of the valve member 44 protrudes from the bore section 42a with its end facing away from the head 46 and a prestressed closing spring 43 engages it.
Im Ventilgehäuse 40 ist wenigstens ein Zulaufkanal 50 eingebracht, der in den Bohrungsabschnitt 42b mündet. Vorzugsweise sind mehrere, beispielsweise drei über den Umfang des Ventilgehäuses 40 gleichmäßig verteilte Zulaufkanäle 50 vorgesehen. Der Bohrungsabschnitt 42c ist derart ausgebildet, dass sich dessen Durchmesser vom Bohrungsabschnitt 42b weg zum Bohrungsabschnitt 42d hin erweitert. Die Mantelfläche des Bohrungsabschnitts 42c ist dabei vorzugsweise kegelstumpfförmig ausgebildet, kann jedoch auch beliebig anders geformt sein, beispielsweise konkav oder konvex gewölbt. Die Mantelfläche des Bohrungsabschnitts 42c verläuft unter einem Winkel α zur Längsachse 45 des Ventilglieds 44 geneigt. Der Neigungswinkel α der Mantelfläche des Bohrungsabschnitts 42c ist vorzugsweise etwas größer als der Winkel γ, unter dem die Dichtfläche 48 des Ventilglieds 44 geneigt ist, kann jedoch auch etwas kleiner als der Winkel γ sein. Der Bohrungsabschnitt 42c bildet einen Ventilsitz, mit dem die Dichtfläche 48 des Ventilglieds 44 zusammenwirkt. In geschlossenem Zustand liegt das Ventilglied 44 mit seiner Dichtfläche 48 am Bohrungsabschnitt 42c an, wobei die Anlage der Dichtfläche 48 infolge der Differenz zwischen den Neigungswinkeln α und γ an dem dem Bohrungsabschnitt 42b zugewandten Rand des Bohrungsabschnitts 42c erfolgt.At least one inlet channel 50 is introduced into the valve housing 40 and opens into the bore section 42b. Preferably, several, for example three, inlet channels 50 are provided which are uniformly distributed over the circumference of the valve housing 40. The bore section 42c is designed such that its diameter widens away from the bore section 42b towards the bore section 42d. The lateral surface of the bore section 42c is preferably frustoconical, but can also be shaped in any other way, for example concave or convex. The lateral surface of the bore section 42c is inclined at an angle α to the longitudinal axis 45 of the valve member 44. The angle of inclination α of the lateral surface of the bore section 42c is preferably somewhat larger than the angle γ at which the sealing surface 48 of the valve member 44 is inclined, but can also be somewhat smaller than the angle γ. The bore section 42c forms a valve seat with which the sealing surface 48 of the valve member 44 cooperates. In the closed state, the valve member 44 rests with its sealing surface 48 on the bore section 42c, the sealing surface 48 being in contact with the edge of the bore section 42c facing the bore section 42b due to the difference between the inclination angles α and γ.
Der Bohrungsabschnitt 42d ist derart ausgebildet, dass sich dessen Durchmesser vom Bohrungsabschnitt 42c weg zumThe bore section 42d is designed such that its diameter moves away from the bore section 42c
Pumpenarbeitsräum 24 hin vergrößert. Die Mantelfläche des Bohrungsabschnitts 42d ist dabei vorzugsweise kegelstumpfförmig ausgebildet, kann jedoch auch beliebig anders geformt sein, beispielsweise konkav oder konvex gewölbt. Die Mantelfläche des Bohrungsabschnitts 42d verläuft unter einem Winkel ß zur Längsachse 45 des Ventilglieds 44 geneigt. Der Winkel ß, unter dem die Mantelfläche des Bohrungsabschnitts 42d zur Längsachse 45 geneigt verläuft ist dabei kleiner als der Winkel α, unter dem die Mantelfläche des Bohrungsabschnitts 42c zurPump work room 24 enlarged. The lateral surface of the bore section 42d is preferably frustoconical, but can also be shaped in any other way, for example concave or convex. The lateral surface of the bore section 42d is inclined at an angle β to the longitudinal axis 45 of the valve member 44. The angle β, at which the lateral surface of the bore section 42d is inclined to the longitudinal axis 45, is smaller than the angle α, at which the lateral surface of the bore section 42c
Längsachse 45 geneigt verläuft. Am Übergang zwischen den Bohrungsabschnitten 42c und 42d ist vorzugsweise ein Freistich 42e vorgesehen, um eine einfache Herstellung der beiden Bohrungsabschnitte 42c und 42d mit den unterschiedlichen Neigungswinkeln α und ß zu ermöglichen. Der Freistich 42e weist vorzugsweise eine zumindest annähernd parallel zur Längsachse 45 verlaufende Mantelfläche auf. Der Außendurchmesser des Kopfs 46 des Ventilglieds 44 ist etwas kleiner als der Durchmesser des Freistichs 42e, dass dieser mit der Kante am Übergang vom Kopf 46 zur Dichtfläche 48 in geschlossenem Zustand etwas in den Freistich 42e eintauchen kann. Durch den Freistich 42e wird somit eine Kollision zwischen dem Kopf 46 des Ventilglieds 44 und dem Ventilgehäuse 40 vermieden.Longitudinal axis 45 extends inclined. At the transition between the Bore sections 42c and 42d are preferably provided with an undercut 42e in order to enable simple manufacture of the two bore sections 42c and 42d with the different inclination angles α and β. The undercut 42e preferably has a lateral surface running at least approximately parallel to the longitudinal axis 45. The outer diameter of the head 46 of the valve member 44 is slightly smaller than the diameter of the undercut 42e, so that the edge at the transition from the head 46 to the sealing surface 48 can dip somewhat into the undercut 42e in the closed state. The undercut 42e thus avoids a collision between the head 46 of the valve member 44 and the valve housing 40.
Durch die vorstehend beschriebene Ausbildung desThrough the above-described training of
Ventilgehäuses 40 mit den Bohrungsabschnitten 42c und 42d, deren Neigungswinkel α und ß unterschiedlich sind, wird erreicht, dass in geöffnetem Zustand, wenn das Ventilglied 44 mit seiner Dichtfläche 48 von dem den Ventilsitz bildenden Bohrungsabschnitt 42c abgehoben ist, der Bereich 52 des kleinsten Durchflussquerschnitts zwischen dem zylindrischen Abschnitt des Kopfs 46 des Ventilglieds 44 und dem Bohrungsabschnitt 42d vorhanden ist. In diesem Bereich 52 des geringsten Durchflussquerschnitts ist bei geöffnetem Einlassventil 30 die höchsteValve housing 40 with the bore sections 42c and 42d, the angles of inclination α and β of which are different, is achieved in that in the open state, when the valve member 44 is raised with its sealing surface 48 from the bore section 42c forming the valve seat, the area 52 of the smallest flow cross section between the cylindrical portion of the head 46 of the valve member 44 and the bore portion 42d. In this area 52 of the smallest flow cross section, the highest is when the inlet valve 30 is open
Strömungsgeschwindigkeit vorhanden und damit ein geringer statischer Druck. Der Bereich 52 ist somit in Strömungsrichtung des Kraftstoffs vom Zulaufkanal 50 in den Pumpenarbeitsraum 24 stromabwärts nach der Dichtfläche 48 des Ventilglieds 44 angeordnet. Im Bereich der Dichtfläche 48 des Ventilglieds 44 ist somit eine geringere Strömungsgeschwindigkeit vorhanden als im Bereich 52 und entsprechend ein relativ hoher statischer Druck. Dieser auf die Dichtfläche 48 des Ventilglieds 44 wirkende statische Druck erzeugt eine in Öffnungsrichtung auf das Ventilglied 44 wirkende Kraft und unterstützt somit die Öffnungsbewegung des Ventilglieds 44 und die stabile Anordnung des Ventilglieds 44 in seinem geöffneten Zustand.Flow velocity available and therefore a low static pressure. The region 52 is thus arranged downstream of the sealing surface 48 of the valve member 44 in the flow direction of the fuel from the inlet channel 50 into the pump work chamber 24. In the area of the sealing surface 48 of the valve member 44 there is therefore a lower flow velocity than in the area 52 and, accordingly, a relatively high static pressure. This static pressure acting on the sealing surface 48 of the valve member 44 generates a force acting on the valve member 44 in the opening direction and thus supports the Opening movement of the valve member 44 and the stable arrangement of the valve member 44 in its open state.
Beim Saughub des Pumpenkolbens 20 öffnet das Einlassventil 30, wenn die durch den im Kraftstoffzulauf 38 herrschenden Druck, der auf den innerhalb des Ventilsitzes 42c angeordneten Teil der Dichtfläche 48 des Ventilglieds 44 wirkt, in Öffnungsrichtung auf das Ventilglied 44 erzeugte Kraft größer ist als die Summe der durch den im Pumpenarbeitsraum 24 herrschenden Druck auf das Ventilglied 44 erzeugte Kraft und die durch die Schließfeder 43 erzeugten Kraft ist. Wenn das Ventilglied 44 mit seiner Dichtfläche 48 vom Ventilsitz 42c abgehoben ist, so ist die gesamte Dichtfläche 48 druckbeaufschlagt, wobei durch die Anordnung des Bereichs 52 mit dem kleinstenDuring the suction stroke of the pump piston 20, the inlet valve 30 opens when the force generated in the opening direction on the valve member 44 by the pressure prevailing in the fuel inlet 38, which acts on the part of the sealing surface 48 arranged within the valve seat 42c, is greater than the sum is the force generated by the pressure on the valve member 44 in the pump working space 24 and the force generated by the closing spring 43. When the valve member 44 with its sealing surface 48 is lifted off the valve seat 42c, the entire sealing surface 48 is pressurized, the area 52 having the smallest being arranged
Durchflussquerschnitt stromabwärts nach der Dichtfläche 48 auf die Dichtfläche 48 ein relativ hoher statischer Druck wirkt, der das Ventilglied 44 in seinem geöffneten Zustand hält. Beim Förderhub des Pumpenkolbens 20 wird durch diesen im Pumpenarbeitsraum 24 ein erhöhter Druck erzeugt, durch den das Einlassventil 30 geschlossen wird.Flow cross section downstream of the sealing surface 48 acts on the sealing surface 48, a relatively high static pressure which holds the valve member 44 in its open state. During the delivery stroke of the pump piston 20, an increased pressure is generated by the latter in the pump work chamber 24, by means of which the inlet valve 30 is closed.
In Figur 3 ist eine modifizierte Ausführung des Einlassventils 30 dargestellt, bei der der grundsätzliche Aufbau gleich ist wie bei der Ausführung gemäß Figur 2, jedoch das Ventilglied 44 modifiziert ist. Der Kopf 46 des Ventilglieds 44 weist dabei zu dessen dem Schaft 44a zugewandtem Ende hin einen im Durchmesser gegenüber dem übrigen Durchmesser des Kopfes 46 verringerten Bereich 47 auf. Der im Durchmesser verringerte Bereich 47 des Kopfes 46 des Ventilglieds 44 ist derart angeordnet, dass dieser bei in seiner Schließstellung angeordnetem Ventilglied 44 dem Übergang zwischen der ersten Mantelfläche 42c und der zweiten Mantelfläche 42d des Ventilgehäuses 40 gegenüberliegt. Durch die Durchmesserverringerung im Bereich 47 wird eine Kollision des Kopfes 46 des Ventilglieds 44 mit dem Ventilgehäuse 40 vermieden. Durch die Durchmesserverringerung im Bereich 47 ist am Kopf 46 des Ventilglieds 44 an dessen Übergang zur Dichtfläche 48 ein Absatz gebildet. Der Übergang vom Bereich 47 zum übrigen Teil des Kopfes 46 des Ventilglieds 44 mit großem Durchmesser kann wie in Figur 3 dargestellt gerundet ausgebildet sein. Der Kopf 46 des Ventilglieds 44 kann wie in Figur 2 dargestellt etwa zylinderförmig ausgebildet sein oder wie in Figur 3 dargestellt etwa kegelstumpfförmig, wobei sich der Durchmesser des Kopfes 46 zumFIG. 3 shows a modified embodiment of the inlet valve 30, in which the basic structure is the same as in the embodiment according to FIG. 2, but the valve member 44 is modified. The head 46 of the valve member 44 has, toward its end facing the shaft 44a, an area 47 with a reduced diameter compared to the remaining diameter of the head 46. The area 47 of the head 46 of the valve member 44, which has a reduced diameter, is arranged such that, when the valve member 44 is arranged in its closed position, it lies opposite the transition between the first lateral surface 42c and the second lateral surface 42d of the valve housing 40. Due to the reduction in diameter in the area 47, a collision of the head 46 of the Avoided valve member 44 with the valve housing 40. Due to the reduction in diameter in the area 47, a shoulder is formed on the head 46 of the valve member 44 at its transition to the sealing surface 48. The transition from the area 47 to the remaining part of the head 46 of the valve member 44 with a large diameter can be rounded as shown in FIG. The head 46 of the valve member 44 can be approximately cylindrical as shown in FIG. 2 or approximately frustoconical as shown in FIG. 3, the diameter of the head 46 increasing
Pumpenarbeitsraum 24 hin vergrößert, wodurch die Umströmung des Kopfes 46 des Ventilglieds 44 verbessert wird.Pump working space 24 increases, whereby the flow around the head 46 of the valve member 44 is improved.
Nachfolgend wird beispielhaft das Auslassventil 32 anhand der Figur 4 näher beschrieben. Das Auslassventil 32 ist beispielsweise in eine Bohrung 54 des Gehäuseteils 36 eingesetzt. In die Bohrung 54 mündet beispielsweise etwa radial zu deren Längsachse ein Kraftstoffablaufkanal 56, der mit dem Speicher 12 verbunden ist. Das Gehäuseteil 36 bildet ein Ventilgehäuse für das Auslassventil 32, wobei alternativ auch ein separates, in das Gehäuseteil 36 eingesetztes Ventilgehäuse für das Auslassventil 32 vorgesehen sein kann. Die Bohrung 54 im Gehäuseteil 36 ist im Durchmesser mehrfach gestuft ausgebildet und weist einen in den Pumpenarbeitsraum 24 mündenden Abschnitt 54a mit kleinem Durchmesser auf. An den Bohrungsabschnitt 54a schließt sich vom Pumpenarbeitsraum 24 weg ein weiterer Bohrungsabschnitt 54b an, dessen Durchmesser sich vom Pumpenarbeitsraum 24 weg vergrößert. Der Bohrungsabschnitt 54b ist vorzugsweise zumindest annähernd kegelstumpfförmig ausgebildet, kann jedoch alternativ auch eine konkav oder konvex gewölbte Mantelfläche aufweisen. Die Mantelfläche des Bohrungsabschnitts 54b verläuft unter einem Winkel α geneigt zur Längsachse 55 der Bohrung 54. An den Bohrungsabschnitt 54b schließt sich vom Pumpenarbeitsraum 24 weg ein weiterer Bohrungsabschnitt 54c an, dessen Durchmesser sich vom Pumpenarbeitsraum 24 weg vergrößert. Der Bohrungsabschnitt 54c ist vorzugsweise zumindest annähernd kegelstumpfförmig ausgebildet, kann jedoch alternativ auch eine konkav oder konvex gewölbte Mantelfläche aufweisen. Die Mantelfläche desExhaust valve 32 is described in more detail below by way of example with reference to FIG. 4. The outlet valve 32 is inserted, for example, into a bore 54 in the housing part 36. For example, a fuel drain channel 56, which is connected to the accumulator 12, opens into the bore 54 approximately radially to its longitudinal axis. The housing part 36 forms a valve housing for the outlet valve 32, alternatively a separate valve housing for the outlet valve 32 inserted into the housing part 36 can also be provided. The bore 54 in the housing part 36 has a multiple stepped diameter and has a small-diameter section 54a opening into the pump working space 24. A further bore portion 54b adjoins the bore portion 54a away from the pump workspace 24, the diameter of which increases away from the pump workspace 24. The bore section 54b is preferably at least approximately frustoconical, but can alternatively also have a concave or convex curved surface. The lateral surface of the bore section 54b extends at an angle α inclined to the longitudinal axis 55 of the bore 54. A further bore section 54c adjoins the bore section 54b away from the pump working space 24, the latter Diameter increases away from the pump working space 24. The bore section 54c is preferably at least approximately frustoconical, but can alternatively also have a concave or convex curved surface. The outer surface of the
Bohrungsabschnitts 54c verläuft unter einem Winkel ß geneigt zur Längsachse 55 der Bohrung 54, wobei der Winkel ß kleiner ist als der Winkel α. An den Bohrungsabschnitt 54c kann sich ein weiterer Bohrungsabschnitt 54d mit konstantem Durchmesser anschließen, der bis zur Außenseite des Gehäuseteils 36 verläuft. In den Bohrungsabschnitt 54d ist von der Außenseite des Gehäuseteils 36 her ein Verschlußelement 58 eingesetzt, beispielsweise eingeschraubt .Bore section 54c extends at an angle β inclined to the longitudinal axis 55 of the bore 54, the angle β being smaller than the angle α. A further bore portion 54d with a constant diameter can be connected to the bore portion 54c and extends to the outside of the housing part 36. A closure element 58 is inserted, for example screwed, into the bore section 54d from the outside of the housing part 36.
Das Auslassventil 32 weist ein Ventilglied 60 auf, das zumindest annähernd kugelförmig ausgebildet ist. Es kann eine Schließfeder 62 vorgesehen sein, die zwischen dem Ventilglied 60 und dem Verschlußelement 58 eingespannt ist und durch die das Ventilglied 60 zum Pumpenarbeitsraum 24 hin gedrückt wird. Das Ventilglied 60 wirkt mit einer Dichtfläche 64, die durch einen Teil seiner Oberfläche gebildet ist, mit dem Bohrungsabschnitt 54b zusammen, der einen Ventilsitz für das Ventilglied 60 bildet. Bei geringem Druck im Pumpenarbeitsraum 24 wird das Ventilglied 60 durch die Schließfeder 62 mit seiner Dichtfläche 64 in Anlage am Ventilsitz 54b gehalten. Am Ventilglied 60 ist in geschlossenem Zustand nur ein relativ kleiner Teil der Oberfläche entsprechend etwa dem Durchmesser des Bohrungsabschnitts 54a von dem im Pumpenarbeitsraum 24 herrschenden Druck beaufschlagt. Wenn der Druck im Pumpenarbeitsraum 24 steigt, so öffnet das Auslassventil 32, da die durch den auf das Ventilglied 60 wirkenden Druck erzeugte Kraft in Öffnungsrichtung größer ist als die Kraft der Schließfeder 62. Beim Öffnen des Auslassventils 32 wird zwischen der Dichtfläche 64 des Ventilglieds 60 und dem Ventilsitz 54b ein Durchflussquerschnitt freigegeben. Zwischen dem Umfang des Ventilglieds 60 und dem Bohrungsabschnitt 54c ist ebenfalls ein Bereich 66 mit einem freigegebenen Durchflussquerschnitt angeordnet, wobei der Durchflussquerschnitt bei geöffnetem Ventil im Bereich 66 kleiner ist als der zwischen der Dichtfläche 64 und dem Ventilsitz 54b freigegebene Durchflussquerschnitt. Eine Drosselung der KraftstoffStrömung bei der Durchströmung des geöffneten Auslassventils 32 erfolgt somit im Bereich 66 mit dem geringesten Durchflussquerschnitt und nicht im Bereich der Dichtfläche 64 des Ventilglieds 60. Im Bereich der Dichtfläche 64 des Ventilglieds 60 ist somit eine geringere Strömungsgeschwindigkeit vorhanden als im Bereich 66 des kleinsten Durchflussquerschnitts und daher ein höherer statischer Druck als im Bereich 66.The outlet valve 32 has a valve member 60 which is at least approximately spherical. A closing spring 62 can be provided, which is clamped between the valve member 60 and the closure element 58 and through which the valve member 60 is pressed toward the pump working space 24. The valve member 60 cooperates with a sealing surface 64, which is formed by part of its surface, with the bore section 54b, which forms a valve seat for the valve member 60. At low pressure in the pump work chamber 24, the valve member 60 is held by the closing spring 62 with its sealing surface 64 in contact with the valve seat 54b. When the valve member 60 is closed, only a relatively small part of the surface corresponding to approximately the diameter of the bore section 54a is acted upon by the pressure prevailing in the pump work chamber 24. When the pressure in the pump working chamber 24 increases, the outlet valve 32 opens because the force generated by the pressure acting on the valve member 60 in the opening direction is greater than the force of the closing spring 62. When the outlet valve 32 is opened, a flow cross section is released between the sealing surface 64 of the valve member 60 and the valve seat 54b. A region 66 with a released flow cross section is likewise arranged between the circumference of the valve member 60 and the bore section 54c, the flow cross section when the valve is open is smaller in the region 66 than the flow cross section released between the sealing surface 64 and the valve seat 54b. Throttling of the fuel flow when flowing through the opened outlet valve 32 thus takes place in the area 66 with the smallest flow cross-section and not in the area of the sealing surface 64 of the valve member 60. In the area of the sealing surface 64 of the valve member 60 there is therefore a lower flow velocity than in the area 66 of the smallest flow cross-section and therefore a higher static pressure than in area 66.
Beim Öffnen des Auslassventils 32, wenn dessen Ventilglied 60 mit seiner Dichtfläche 64 vom Ventilsitz 54b abhebt, wird die druckbeaufschlagte Oberfläche des Ventilglieds 60 vergrößert, da dann nicht mehr nur die innerhalb des Ventilsitzes 54b liegende Oberfläche druckbeaufschlagt ist sondern die größere Oberfläche mit zum Bereich 66 hin. Auf das Ventilglied 60 wirkt daher eine große Druckraft inWhen the outlet valve 32 is opened, when its valve member 60 lifts with its sealing surface 64 from the valve seat 54b, the surface area of the valve member 60 under pressure is increased, since then it is no longer only the surface lying inside the valve seat 54b that is pressurized but the larger surface with the area 66 out. A large compressive force therefore acts on the valve member 60
Öffnungsrichtung, die das Ventilglied 60 stabil in seinem geöffneten Zustand hält, auch wenn eine große Kraftstoffmenge mit hoher Strömungsgeschwindigkeit das Auslassventil 32 durchströmt. Mit zunehmendem Hub des Ventilglieds 60 in Öffnungsrichtung vergrößert sich sowohl der zwischen dessen Dichtfläche 64 und dem Ventilsitz 54b freigegebene Durchflussquerschnitt als auch der im Bereich 66 freigegebene Durchlussquerschnitt, wobei der im Bereich 66 freigegebene Durchflussquerschnitt stets kleiner ist als der zwischen der Dichtfläche 64 und dem Ventilsitz 54b freigegebene Durchflussquerschnitt. Der Winkel α, unter dem der Ventilsitz 54b zur Längsachse 55 der Bohrung 54 geneigt ist, kann groß gewählt werden, so dass der Ventilsitz 54b relativ flach ist und damit eine hohe Verschleißbeständigkeit aufweist .Opening direction that holds the valve member 60 stably in its open state even when a large amount of fuel flows through the exhaust valve 32 at a high flow rate. With increasing stroke of the valve member 60 in the opening direction, both the flow cross-section released between its sealing surface 64 and the valve seat 54b and the flow cross-section released in the region 66 increase, the flow cross-section released in the region 66 always being smaller than that between the sealing surface 64 and the valve seat 54b approved flow cross-section. The angle α at which the valve seat 54b is inclined to the longitudinal axis 55 of the bore 54, can be chosen large, so that the valve seat 54b is relatively flat and thus has a high wear resistance.
Bei einer Hochdruckpumpe kann vorgesehen sein, dass nur das Einlassventil 30 wie vorstehend zu Figur 2 oder 3 beschrieben ausgebildet ist, während das Auslassventil 32 als einfaches Kugel- oder Kegelventil ausgebildet ist. Alternativ kann auch vorgesehen sein, dass bei einerIn the case of a high-pressure pump, it can be provided that only the inlet valve 30 is designed as described above for FIG. 2 or 3, while the outlet valve 32 is designed as a simple ball or cone valve. Alternatively, it can also be provided that a
Hochdruckpumpe nur das Auslassventil 32 wie vorstehend zu Figur 4 beschrieben ausgebildet ist, während das Einlassventil 30 als einfaches Kegelsitz- oder Kugelventil ausgebildet sein kann. Außerdem kann auch ein wie anhand Figur 4 als Auslassventil beschriebenes Ventil mit einem kugelförmigen Ventilglied als Einlassventil an einer Hochdruckpumpe verwendet werden . Entsprechend kann auch ein wie anhand Figur 2 oder 3 als Einlassventil beschriebenes Ventil mit einem Ventilglied mit kegelförmiger Dichtfläche als Auslassventil an einer Hochdruckpumpe verwendet werden. Vorzugsweise sind bei einer Hochdruckpumpe sowohl das Einlassventil 30 als auch das Auslassventil 32 wie vorstehend zu den Figuren 2 oder 3 und 4 beschrieben ausgebildet. High-pressure pump, only the outlet valve 32 is designed as described above for FIG. 4, while the inlet valve 30 can be designed as a simple conical seat or ball valve. In addition, a valve as described with reference to FIG. 4 as an outlet valve with a spherical valve member can also be used as an inlet valve on a high-pressure pump. Correspondingly, a valve as described with reference to FIG. 2 or 3 as an inlet valve with a valve member with a conical sealing surface can also be used as an outlet valve on a high-pressure pump. In the case of a high-pressure pump, both the inlet valve 30 and the outlet valve 32 are preferably designed as described above for FIGS. 2 or 3 and 4.

Claims

Ansprüche Expectations
1. Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine, mit wenigstens einem Pumpenelement (16), das einen in einer Hubbewegung angetriebenen Pumpenkolben (20) aufweist, der einen Pumpenarbeitsraum (24) begrenzt, in den beim Saughub des Pumpenkolbens (20) über ein Einlassventil (30) Kraftstoff aus einem Kraftstoffzulauf (50) angesaugt wird und aus dem beim Förderhub des Pumpenkolbens (20) über ein Auslassventil (32) Kraftstoff in einen Hochdruckbereich (56,12) verdrängt wird, wobei das Einlassventil (30) und/oder das Auslassventil (32) ein Ventilglied (44; 60) aufweist, das mit einer Dichtfläche (48; 64) mit einem in einem Ventilgehäuse (40; 36) angeordneten Ventilsitz (42c; 54b) zusammenwirkt, wobei durch das Ventilglied (44; 60) in geöffnetem Zustand, wenn dieses mit seiner Dichtfläche (48; 64) vom Ventilsitz (42c; 54b) abgehoben ist, zwischen dem Ventilglied (44; 60) und dem Ventilgehäuse (40; 36) ein Durchflussquerschnitt freigegeben wird, dadurch gekennzeichnet, dass in geöffnetem Zustand des Ventilglieds (44; 60) ein Bereich (52; 66) mit dem kleinsten Durchflussquerschnitt zwischen dem Ventilglied (44; 60) und dem Ventilgehäuse (40; 36) in Strömungsrichtung des das Ventil (30; 32) durchströmenden Kraftstoffs stromabwärts nach der Dichtfläche (48; 64) des Ventilglieds (44; 60) angeordnet ist.1. High-pressure pump, in particular for a fuel injection device of an internal combustion engine, with at least one pump element (16) which has a pump piston (20) driven in one stroke movement, which delimits a pump working chamber (24) into which the pump piston (20) is sucked when the pump piston (20) is sucked Inlet valve (30) is sucked in fuel from a fuel inlet (50) and from which during the delivery stroke of the pump piston (20) fuel is displaced into a high pressure area (56, 12) via an outlet valve (32), the inlet valve (30) and / or the outlet valve (32) has a valve member (44; 60) which cooperates with a sealing surface (48; 64) with a valve seat (42c; 54b) arranged in a valve housing (40; 36), the valve member (44; 60 ) in the open state, when this is lifted with its sealing surface (48; 64) from the valve seat (42c; 54b), a flow cross-section exposes between the valve member (44; 60) and the valve housing (40; 36) ben, characterized in that in the open state of the valve member (44; 60) an area (52; 66) with the smallest flow cross-section between the valve member (44; 60) and the valve housing (40; 36) in the flow direction of the fuel flowing through the valve (30; 32) downstream after the sealing surface (48; 64) of the valve member (44; 60) is arranged.
2. Hochdruckpumpe nach Anspruch 1, dadurch gekennzeichnet, dass das Ventilgehäuse (40; 36) eine erste zu ihrer2. High-pressure pump according to claim 1, characterized in that the valve housing (40; 36) a first to it
Längsachse (45; 55) geneigte, das Ventilglied (44; 60) umgebende Mantelfläche (42c; 54b) aufweist, die den Ventilsitz bildet, und eine sich an die erste MantelflächeLongitudinal axis (45; 55) inclined, the valve member (44; 60) has the surrounding lateral surface (42c; 54b), which forms the valve seat, and an adjoining the first lateral surface
(42c; 54b) anschließende zweite zu ihrer Längsachse (45; 55) geneigte, das Ventilglied (44; 60) umgebende Mantelfläche (42d;54c) aufweist, dass der Neigungswinkel (ß) der zweiten Mantelfläche (42d;54c) bezüglich der Längsachse (45; 55) geringer ist als der Neigungswinkel (α) der ersten Mantelfläche (42c; 54b) und dass in geöffnetem Zustand des Ventilglieds (44; 60) der Bereich (52; 66) des kleinsten Durchflussquerschnitts zwischen dem Ventilglied (44; 60) und der zweiten Mantelfläche (42d;54c) des Ventilgehäuses(42c; 54b) subsequent second lateral surface (42d; 54c) inclined to its longitudinal axis (45; 55) and surrounding the valve member (44; 60) has that the angle of inclination (β) of the second lateral surface (42d; 54c) with respect to the longitudinal axis (45; 55) is less than the angle of inclination (α) of the first lateral surface (42c; 54b) and that in the opened state of the valve member (44; 60) the area (52; 66) of the smallest flow cross-section between the valve member (44; 60 ) and the second lateral surface (42d; 54c) of the valve housing
(40; 36) angeordnet ist.(40; 36) is arranged.
3. Hochdruckpumpe nach Anspruch 2, dadurch gekennzeichnet, dass die erste Mantelfläche (42c; 54b) und/oder die zweite3. High pressure pump according to claim 2, characterized in that the first lateral surface (42c; 54b) and / or the second
Mantelfläche (42d;54c) des Ventilgehäuses (40; 36) zumindest annähernd kegelstumpfförmig ausgebildet ist.The lateral surface (42d; 54c) of the valve housing (40; 36) is at least approximately frustoconical.
4. Hochdruckpumpe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die Dichtfläche (48) des Ventilglieds4. High-pressure pump according to one of claims 1 to 3, characterized in that the sealing surface (48) of the valve member
(44) zumindest annähernd kegelstumpfförmig ausgebildet ist und vorzugsweise unter einem anderen Winkel (γ) zur Längsachse (45) der ersten Mantelfläche (42c) geneigt ist als der Winkel (α) , unter dem die erste Mantelfläche (42c) des Ventilgehäuses (40) zu ihrer Längsachse (45) geneigt ist.(44) is at least approximately frustoconical and is preferably inclined at a different angle (γ) to the longitudinal axis (45) of the first lateral surface (42c) than the angle (α) at which the first lateral surface (42c) of the valve housing (40) is inclined to its longitudinal axis (45).
5. Hochdruckpumpe nach einem der Ansprüche 2 bis 4, dadurch gekennzeichnet, dass am Übergang zwischen der ersten Mantelfläche (42c) und der zweiten Mantelfläche (42d) des5. High-pressure pump according to one of claims 2 to 4, characterized in that at the transition between the first lateral surface (42c) and the second lateral surface (42d) of the
Ventilgehäuses (40) ein Freistich (42e) vorgesehen ist, der vorzugsweise eine zumindest annähernd parallel zur Längsachse (45) verlaufende Mantelfläche aufweist.An undercut (42e) is provided in the valve housing (40) and preferably has an outer surface that extends at least approximately parallel to the longitudinal axis (45).
6. Hochdruckpumpe nach Anspruch 4 oder 5, dadurch gekennzeichnet, dass die Dichtfläche (48) am Ventilglied (44) am Übergang zwischen einem Schaft (44a) des Ventilglieds (44) und einem im Querschnitt gegenüber dem Schaft (44a) vergrößerten Kopf (46) des Ventilglieds (44) angeordnet ist und dass am Kopf (46) des Ventilglieds (44) ein Bereich (47) mit gegenüber dem übrigen Querschnitt des Kopfes (46) verringertem Querschnitt vorgesehen ist, der dem Übergang zwischen der ersten Mantelfläche (42c) und der zweiten Mantelfläche (42d) im Ventilgehäuse (40) gegenüberliegt .6. High-pressure pump according to claim 4 or 5, characterized in that the sealing surface (48) on the valve member (44) is arranged at the transition between a stem (44a) of the valve member (44) and a head (46) of the valve member (44) which is enlarged in cross section with respect to the stem (44a) and that on the head (46) of the valve member (44) an area (47) with a cross section which is smaller than the remaining cross section of the head (46) is provided, which lies opposite the transition between the first lateral surface (42c) and the second lateral surface (42d) in the valve housing (40).
7. Hochdruckpumpe nach einem der Ansprüche 1 bis 3 oder 5, dadurch gekennzeichnet, dass das Ventilglied (60) zumindest annähernd kugelförmig ausgebildet ist und dass die Dichtfläche (64) durch einen Bereich der Oberfläche des Ventilglieds (60) gebildet ist.7. High-pressure pump according to one of claims 1 to 3 or 5, characterized in that the valve member (60) is at least approximately spherical and that the sealing surface (64) is formed by a region of the surface of the valve member (60).
8. Hochdruckpumpe nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass in geöffnetem Zustand des Ventilglieds (44; 60) im Bereich von dessen Dichtfläche (48; 64) ein höherer statischer Druck herrscht als im8. High-pressure pump according to one of the preceding claims, characterized in that in the open state of the valve member (44; 60) in the area of the sealing surface (48; 64) there is a higher static pressure than in
Bereich (52; 66) des kleinsten Durchflussquerschnitts und dass durch den auf die Dichtfläche (48; 64) wirkenden Druck eine Kraft in Öffnungsrichtung auf das Ventilglied (44; 60) erzeugt wird. Area (52; 66) of the smallest flow cross-section and that a force is generated in the opening direction on the valve member (44; 60) by the pressure acting on the sealing surface (48; 64).
EP05701509A 2004-02-11 2005-01-13 High pressure pump, in particular for a fuel injection device in an internal combustion engine Withdrawn EP1716332A1 (en)

Applications Claiming Priority (3)

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DE102004006700 2004-02-11
DE102004027825A DE102004027825A1 (en) 2004-02-11 2004-06-08 High-pressure pump, especially for fuel injection device for internal combustion engine, has smallest throughflow cross-section region downstream of sealing surface when valve element in open position
PCT/EP2005/050126 WO2005078273A1 (en) 2004-02-11 2005-01-13 High pressure pump, in particular for a fuel injection device in an internal combustion engine

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EP1716332A1 true EP1716332A1 (en) 2006-11-02

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Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006242019A (en) * 2005-03-01 2006-09-14 Jtekt Corp Check valve for fuel pump
DE102005061886A1 (en) * 2005-12-23 2007-07-05 Robert Bosch Gmbh High pressure pump for fuel injection device in internal combustion engine having valve which when open releases first, then second through-flow cross sections in flow direction and lastly third cross-section larger than preceding two
DE102006017037B4 (en) 2006-04-11 2015-09-17 Continental Automotive Gmbh Radial piston pump for high-pressure fuel supply in an internal combustion engine
DE102008040083A1 (en) * 2008-07-02 2010-01-07 Robert Bosch Gmbh high pressure pump
DE102010040617A1 (en) * 2010-09-13 2012-03-15 Robert Bosch Gmbh Valve, in particular a hydraulic piston pump
JP5491425B2 (en) * 2011-01-20 2014-05-14 株式会社デンソー High pressure pump
US9027594B2 (en) 2012-03-30 2015-05-12 Ti Group Automotive Systems, L.L.C. Fuel system valve assembly
DE102013107950A1 (en) 2012-08-01 2014-02-06 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Valve
DE102015201520A1 (en) * 2015-01-29 2016-08-04 Robert Bosch Gmbh Adjustment device and fuel injection system with an adjustment

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3112100A1 (en) * 1981-03-27 1982-10-07 Robert Bosch Gmbh, 7000 Stuttgart "PRESSURE VALVE FOR A FUEL INJECTION PUMP"
JPS5973567U (en) * 1982-11-09 1984-05-18 株式会社ボッシュオートモーティブ　システム Overflow valve of distribution type fuel injection pump
SE465533B (en) * 1990-02-19 1991-09-23 Saab Automobile SILENT BACK VALVE FOR PULSING FLOW
DE19744577A1 (en) * 1997-10-09 1999-04-22 Bosch Gmbh Robert Radial piston pump for high pressure fuel supply in motor vehicles
DE19860672A1 (en) 1998-12-29 2000-07-13 Bosch Gmbh Robert Piston pump for high-pressure fuel generation

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2005078273A1 *

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