EP1121531A1 - Radial piston pump for supplying fuel at high pressure - Google Patents

Radial piston pump for supplying fuel at high pressure

Info

Publication number
EP1121531A1
EP1121531A1 EP99939926A EP99939926A EP1121531A1 EP 1121531 A1 EP1121531 A1 EP 1121531A1 EP 99939926 A EP99939926 A EP 99939926A EP 99939926 A EP99939926 A EP 99939926A EP 1121531 A1 EP1121531 A1 EP 1121531A1
Authority
EP
European Patent Office
Prior art keywords
pump
valve
piston
spring
radial piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP99939926A
Other languages
German (de)
French (fr)
Other versions
EP1121531B1 (en
Inventor
Rüdiger BAUER
Gerd LÖSCH
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1121531A1 publication Critical patent/EP1121531A1/en
Application granted granted Critical
Publication of EP1121531B1 publication Critical patent/EP1121531B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • F04B1/0408—Pistons
    • 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
    • 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
    • F04B53/102—Disc valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/50—Arrangements of springs for valves used in fuel injectors or fuel injection pumps
    • F02M2200/505—Adjusting spring tension by sliding spring seats
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/442—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston means preventing fuel leakage around pump plunger, e.g. fluid barriers

Definitions

  • the invention relates to a radial piston pump according to the preamble of claim 1.
  • Valve closing spring is seated. This acts on the one hand on the shaft and on the other hand indirectly on the pump housing. When the suction valve is opened, the closing force of the spring increases with the stroke.
  • the radial piston pump according to the invention with the features of claim 1 has the advantage that the opening of the suction valve at low pressure of the supplied fuel is supported by the fact that the closing force of the valve closing spring is reduced with increasing suction stroke of the pump piston.
  • opening of all suction valves is thus reliably achieved and a relatively high degree of equal delivery is achieved. Therefore an opening pressure setting of the suction valves is not necessary or is permissible with reduced accuracy.
  • a radial piston pump with axially flowed pump piston in which a suction valve is arranged, the valve closing spring of which acts on the one hand on the closing body of the suction valve and on the other hand on the pump piston.
  • the suction valve is opened, however, the closing force of the spring increases with increasing stroke.
  • Claim 1 given radial piston pump.
  • the measure specified in claim 2 allows the size of the radial piston pump to be reduced, since the valve closing spring is essentially within the overall volume of the pump piston is arranged. This arrangement also results in guidance of the valve closing spring.
  • a non-adjustable radial piston pump 10 shown in Figure 1 is for the
  • the radial piston pump 10 has a housing 11 in which a drive shaft 12 with an eccentric section 13 is mounted. A cam ring 14 is guided on the eccentric section 13.
  • a piston foot 15 can be moved longitudinally in the pump housing 11 with respect to the drive shaft 12 on the cam ring 14 guided pump piston 16 supported.
  • a piston spring 17 which is arranged coaxially with the pump piston 16 and which acts on the one hand on the piston foot 15 and on the other hand on the pump housing 11, the piston foot 15 is always held in contact with the cam ring 14.
  • a suction valve 18 and a pressure valve 19 are also assigned to the pump piston 16.
  • Fuel for example diesel oil
  • Fuel can be supplied to the suction valve 18 through a channel 20 of the pump housing 11 under low pressure.
  • a channel 21 of the pump housing 11 extends from the pressure valve 19 and discharges fuel delivered by the pump piston 16 under high pressure.
  • the pump piston 16 with piston foot 15, piston spring 17, suction valve 18 and pressure valve 19 form a pump element 22 of the radial piston pump 10.
  • This is equipped with further, for example a total of three pump elements 22 which (not visible in the drawing) are offset by 120 ° in one Radial plane to the axis of the drive shaft 12 are arranged in the pump housing 11.
  • the further pump elements 22 are also connected to the channels 20 and 21.
  • the following description of the pump element 22 with reference to FIG. 2 thus applies equally to the other pump elements.
  • the suction valve 18 is arranged radially on the pump piston 16 following in the pump housing 11 with respect to the drive shaft 12.
  • the suction valve has a valve plate 24 which is held down in a bore 25 of the pump housing 11 with a screw plug 26.
  • a hollow cone-shaped valve seat 27 is formed on the valve plate 24.
  • the valve seat 27 is thus arranged fixed with respect to the housing and is in a conductive connection with the channel 20 carrying the fuel under low pressure.
  • the suction valve 18 has a closing body 28 with a conical valve plate 29 which cooperates with the valve seat 27 of the valve plate 24. When closed Suction valve 18 closes valve plate 29 of closing body 28 approximately flush with the end face of valve plate 24 on the pump piston side.
  • the in a cylinder space (displacement space) 32 des
  • Pump piston 16 arranged in the pump housing 11 has a longitudinal bore 33 designed as a blind bore, which ends in a flat bore base 34.
  • a valve closing spring 35 designed as a helical compression spring is accommodated in the longitudinal bore 33 which is arranged coaxially with the pump piston 16. Since the pump piston 16 located in its top dead center position in FIG. 2 extends close to the valve plate 24 delimiting the cylinder chamber 22, the valve closing spring 35 is located for the most part in its length in the longitudinal bore 33 of the pump piston.
  • the valve closing spring 35 has an outer diameter largely adapted to the diameter of the longitudinal bore 33 of the pump piston 16 and engages on the one hand on the bore base 34 and on the other hand on the valve plate 29.
  • the closing body 28 of the suction valve 18 is provided with a pin-shaped shaft 36 which is guided through the interior of the valve closing spring 35 and, in the illustrated dead center position of the pump piston 16 and the closing position of the suction valve 18, extends close to the bottom 34 of the bore.
  • valve closing spring 35 exerts a maximum closing force on the valve plate 29 of the suction valve 18 and keeps it closed.
  • the valve closing spring 35 experiences a reduction in its closing force.
  • the fuel supplied to the suction valve 18 through the channel 20 under low pressure exerts an opening force against the spring force on the valve plate 29.
  • the suction valve 18 is opened, that is to say the valve plate 29 lifts off the valve seat 27 and moves a small amount into the cylinder space 32.
  • the opening of the suction valve 18 is dependent on the pressure of the fuel supplied: at high pressure, the opening of the suction valve 18 takes place even with a slight suction stroke of the pump piston 16; at low pressure, the suction valve is opened when the pump piston 16 has covered a larger suction stroke.
  • the valve closing spring 35 is, however, designed such that, at low pressures of the supplied fuel, the suction valve 18 opens securely with a large suction stroke of the pump piston 16 and the cylinder space 32 is partially filled. Due to the ensured opening of the suction valve 18, the partial filling of the remaining pump elements 22 of the radial piston pump 10 is also given in a corresponding manner.

Abstract

The inventive piston pump has a longitudinally moveable pump piston (16) in a cylinder chamber (32), which is connected to a suction valve (18). A closing body (28) of the suction valve (18) is subjected to the effect of a valve-closing spring (35) which acts in the direction of a valve seat (27) that is fixed in relation to the housing. The valve-closing spring (35) is supported on the pump piston (16). The inventive radial piston pump can be used in fuel injection systems of internal combustion engines, especially in a common rail injection system.

Description

Radialkolbenpumpe für KraftstoffhochdruckerzeugungRadial piston pump for high-pressure fuel generation
Stand der TechnikState of the art
Die Erfindung geht aus von einer Radialkolbenpumpe nach der Gattung des Patentanspruchs 1.The invention relates to a radial piston pump according to the preamble of claim 1.
Es ist schon eine solche Radialkolbenpumpe bekannt (DE 23 38 489 B2 ) , bei welcher das Saugventil einen von seinem Schließkörper achsgleich zum Pumpenkolben ausgehenden Schaft hat, auf dem außerhalb des Zylinderraums dieSuch a radial piston pump is already known (DE 23 38 489 B2), in which the suction valve has a shaft extending from its closing body in the same axis as the pump piston, on which the outside of the cylinder chamber
Ventilschließfeder sitzt. Diese greift einerseits am Schaft und andererseits mittelbar am Pumpengehäuse an. Beim Öffnen des Saugventils steigt daher mit dem Hub die Schließkraft der Feder an.Valve closing spring is seated. This acts on the one hand on the shaft and on the other hand indirectly on the pump housing. When the suction valve is opened, the closing force of the spring increases with the stroke.
Bei derartigen Radialkolbenpumpen mit mehreren Pumpenkolben (Pumpenelementen) werden hohe Anforderungen an die Gleichförderung gestellt: bei niedriger Fördermenge sollen alle Pumpenelemente fördern, und die Fördermenge der einzelnen Pumpenelemente soll in engen Grenzen differieren. Bei niedrigem Druck des der Radialkolbenpumpe zugeführten Kraftstoffs ergeben sich bereits bei geringen Öffnungsdruckunterschieden der Saugventile der Pumpenelemente Schwierigkeiten, diese Anforderungen zu erfüllen. Bei der eingangs genannten Radialkolbenpumpe soll der ÖffnungsVorgang des Saugventils dadurch unterstützt werden, daß der im Zylinderraum befindliche Schließkörper des Ventils im oberen Totpunkt des Pumpenkolbens von diesem weitgehend umschlossen ist und demzufolge der Kolben beim Saughub eine Saugwirkung auf den Schließkörper ausübt.In radial piston pumps of this type with several pump pistons (pump elements), high demands are placed on equal delivery: at a low delivery rate, all pump elements should deliver, and the delivery rate of the individual pump elements should differ within narrow limits. At low pressure of the fuel supplied to the radial piston pump, difficulties arise in meeting these requirements even with small differences in the opening pressure of the suction valves of the pump elements. In the radial piston pump mentioned at the outset, the opening process of the suction valve is to be supported by the fact that the closing body of the valve located in the cylinder chamber is largely enclosed by the pump piston at the top dead center and consequently the piston exerts a suction effect on the closing body during the suction stroke.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Radialkolbenpumpe mit den Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß das Öffnen des Saugventils bei niedrigem Druck des zugeführten Kraftstoffs dadurch unterstützt wird, daß sich mit zunehmendem Saughub des Pumpenkolbens die Schließkraft der Ventilschließfeder verringert. Bei einer Mehrkolbenpumpe wird somit ein Öffnen aller Saugventile sicher erreicht und ein relativ hoher Grad an Gleichförderung erzielt. Deshalb ist eine Öffnungsdruckeinstellung der Saugventile entbehrlich oder mit verminderter Genauigkeit zulässig.The radial piston pump according to the invention with the features of claim 1 has the advantage that the opening of the suction valve at low pressure of the supplied fuel is supported by the fact that the closing force of the valve closing spring is reduced with increasing suction stroke of the pump piston. With a multi-piston pump, opening of all suction valves is thus reliably achieved and a relatively high degree of equal delivery is achieved. Therefore an opening pressure setting of the suction valves is not necessary or is permissible with reduced accuracy.
Zwar ist aus DE 44 06 803 AI eine Radialkolbenpumpe mit axial durchströmten Pumpenkolben bekannt, in dem ein Saugventil angeordnet ist, dessen Ventilschließfeder einerseits am Schließkörper des Saugventils und andererseits am Pumpenkolben angreift. Beim Öffnen des Saugventils steigt jedoch mit zunehmendem Hub die Schließkraft der Feder an.From DE 44 06 803 AI a radial piston pump with axially flowed pump piston is known, in which a suction valve is arranged, the valve closing spring of which acts on the one hand on the closing body of the suction valve and on the other hand on the pump piston. When the suction valve is opened, however, the closing force of the spring increases with increasing stroke.
Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der imThe measures listed in the dependent claims are advantageous further developments and improvements in
Patentanspruch 1 angegebenen Radialkolbenpumpe gegeben.Claim 1 given radial piston pump.
Die im Anspruch 2 angegebene Maßnahme erlaubt es, die Baugröße der Radialkolbenpumpe zu verringern, da die Ventilschließfeder im wesentlichen innerhalb des Bauvolumens des Pumpenkolbens angeordnet ist. Durch diese Anordnung wird zugleich eine Führung der Ventilschließfeder erzielt.The measure specified in claim 2 allows the size of the radial piston pump to be reduced, since the valve closing spring is essentially within the overall volume of the pump piston is arranged. This arrangement also results in guidance of the valve closing spring.
Mit der Ausgestaltung der Radialkolbenpumpe nach Anspruch 3 ist aufbauend auf die Maßnahme gemäß Anspruch 2 ebenfalls eine ausreichende Führung des Schließkörperschafts unter gleichzeitiger Verringerung des Totvolumens der Pumpe geschaffen.With the design of the radial piston pump according to claim 3, based on the measure according to claim 2, sufficient guidance of the closing body shaft is also created while simultaneously reducing the dead volume of the pump.
Die Weiterbildung der Erfindung nach Anspruch 4 zeichnet aus durch unmittelbare Einleitung der Federkraft in die der Ventilsteuerung dienenden Bauteile. Deshalb wirken sich nur die Maßabweichungen weniger Bauteile auf die Einstellung des Saugventils aus.The development of the invention according to claim 4 is characterized by the direct introduction of the spring force into the valve control components. Therefore, only the dimensional deviations of a few components affect the setting of the suction valve.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eineAn embodiment of the invention is shown in simplified form in the drawing and explained in more detail in the following description. 1 shows a
Radialkolbenpumpe im Schnitt und Figur 2 als Einzelheit II in Figur 1 ein Saugventil der Pumpe in größerem Maßstab.Radial piston pump in section and Figure 2 as detail II in Figure 1, a suction valve of the pump on a larger scale.
Beschreibung des AusführungsbeispielsDescription of the embodiment
Eine in Figur 1 dargestellte, nicht verstellbare Radialkolbenpumpe 10 ist für dieA non-adjustable radial piston pump 10 shown in Figure 1 is for the
Kraftstoffhochdruckerzeugung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen, insbesondere bei einem Common-Rail- Einspritzsystem, vorgesehen. Die Radialkolbenpumpe 10 hat ein Gehäuse 11, in dem eine Antriebswelle 12 mit einem Exzenterabschnitt 13 gelagert ist . Auf dem Exzenterabschnitt 13 ist ein Hubring 14 geführt. In Figur 1 der Zeichnung ist an dem Hubring 14 ein Kolbenfuß 15 eines bezüglich der Antriebswelle 12 radial im Pumpengehäuse 11 längsbewegbar geführten Pumpenkolbens 16 abgestützt . * Der Kolbenfuß 15 ist aufgrund der Wirkung einer achsgleich zum Pumpenkolben 16 angeordneten Kolbenfeder 17, welche einerseits am Kolbenfuß 15 und andererseits am Pumpengehäuse 11 angreift, stets in Anlage am Hubring 14 gehalten. Dem Pumpenkolben 16 ist ferner ein Saugventil 18 und ein Druckventil 19 zugeordnet. Dem Saugventil 18 ist Kraftstoff, beispielsweise Dieselöl, durch einen Kanal 20 des Pumpengehäuses 11 unter Niederdruck zuführbar. Vom Druckventil 19 geht ein Kanal 21 des Pumpengehäuses 11 aus, welcher vom Pumpenkolben 16 geförderten Kraftstoff unter Hochdruck ableitet. Der Pumpenkolben 16 mit Kolbenfuß 15, Kolbenfeder 17, Saugventil 18 und Druckventil 19 bilden ein Pumpenelement 22 der Radialkolbenpumpe 10. Diese ist mit weiteren, beispielsweise insgesamt drei Pumpenelementen 22 ausgestattet, welche (in der Zeichnung nicht sichtbar) um 120° gegeneinander versetzt in einer Radialebene zur Achse der Antriebswelle 12 im Pumpengehäuse 11 angeordnet sind. Die weiteren Pumpenelemente 22 stehen gleichfalls mit den Kanälen 20 und 21 in Verbindung. Die nachfolgende Beschreibung des Pumpenelements 22 anhand der Figur 2 gilt somit gleichermaßen für die übrigen Pumpenelemente.High-pressure fuel generation in fuel injection systems of internal combustion engines, in particular in a common rail injection system, is provided. The radial piston pump 10 has a housing 11 in which a drive shaft 12 with an eccentric section 13 is mounted. A cam ring 14 is guided on the eccentric section 13. In FIG. 1 of the drawing, a piston foot 15 can be moved longitudinally in the pump housing 11 with respect to the drive shaft 12 on the cam ring 14 guided pump piston 16 supported. * Due to the effect of a piston spring 17 which is arranged coaxially with the pump piston 16 and which acts on the one hand on the piston foot 15 and on the other hand on the pump housing 11, the piston foot 15 is always held in contact with the cam ring 14. A suction valve 18 and a pressure valve 19 are also assigned to the pump piston 16. Fuel, for example diesel oil, can be supplied to the suction valve 18 through a channel 20 of the pump housing 11 under low pressure. A channel 21 of the pump housing 11 extends from the pressure valve 19 and discharges fuel delivered by the pump piston 16 under high pressure. The pump piston 16 with piston foot 15, piston spring 17, suction valve 18 and pressure valve 19 form a pump element 22 of the radial piston pump 10. This is equipped with further, for example a total of three pump elements 22 which (not visible in the drawing) are offset by 120 ° in one Radial plane to the axis of the drive shaft 12 are arranged in the pump housing 11. The further pump elements 22 are also connected to the channels 20 and 21. The following description of the pump element 22 with reference to FIG. 2 thus applies equally to the other pump elements.
Das Saugventil 18 ist bezüglich der Antriebswelle 12 radial auf dem Pumpenkolben 16 folgend im Pumpengehäuse 11 angeordnet. Das Saugventil hat eine Ventilplatte 24, welche in einer Bohrung 25 des Pumpengehäuses 11 mit einer Verschlußschraube 26 niedergehalten ist. An der Ventilplatte 24 ist ein hohlkegelförmiger Ventilsitz 27 ausgebildet. Der Ventilsitz 27 ist somit bezüglich des Gehäuses festliegend angeordnet und steht mit dem Kraftstoff unter Niederdruck führenden Kanal 20 in leitender Verbindung. Das Saugventil 18 besitzt einen Schließkörper 28 mit einem kegelförmigen Ventilteller 29, welcher mit dem Ventilsitz 27 der Ventilplatte 24 zusammenarbeitet. Bei geschlossenem Saugventil 18 schließt der Ventilteller 29 des Schließkörpers 28 etwa bündig mit der pumpenkolbenseitigen Stirnfläche der Ventilplatte 24 ab.The suction valve 18 is arranged radially on the pump piston 16 following in the pump housing 11 with respect to the drive shaft 12. The suction valve has a valve plate 24 which is held down in a bore 25 of the pump housing 11 with a screw plug 26. A hollow cone-shaped valve seat 27 is formed on the valve plate 24. The valve seat 27 is thus arranged fixed with respect to the housing and is in a conductive connection with the channel 20 carrying the fuel under low pressure. The suction valve 18 has a closing body 28 with a conical valve plate 29 which cooperates with the valve seat 27 of the valve plate 24. When closed Suction valve 18 closes valve plate 29 of closing body 28 approximately flush with the end face of valve plate 24 on the pump piston side.
Der in einem Zylinderraum (Verdrängerraum) 32 desThe in a cylinder space (displacement space) 32 des
Pumpengehäuses 11 angeordnete Pumpenkolben 16 weist eine als Sacklochbohrung ausgebildete Längsbohrung 33 auf, welche in einem ebenen Bohrungsgrund 34 endet. In der achsgleich zum Pumpenkolben 16 angeordneten Längsbohrung 33 ist eine als Schraubendruckfeder ausgebildete Ventilschließfeder 35 aufgenommen. Da sich der in Figur 2 in seiner oberen TotpunktStellung befindliche Pumpenkolben 16 bis nahe an die den Zylinderraum 22 begrenzende Ventilplatte 24 erstreckt, befindet sich die Ventilschließfeder 35 zum überwiegenden Teil ihrer Länge in der Längsbohrung 33 des Pumpenkolbens. Die Ventilschließfeder 35 hat einen weitgehend dem Durchmesser der Längsbohrung 33 des Pumpenkolbens 16 angepaßten Außendurchmesser und greift einerseits am Bohrungsgrund 34 und andererseits am Ventilteller 29 an. Der Schließkörper 28 des Saugventils 18 ist mit einem stiftförmigen Schaft 36 versehen, welcher durch das Innere der Ventilschließfeder 35 geführt ist und in der gezeichneten Totpunktstellung des Pumpenkolbens 16 und Schließstellung des Saugventils 18 bis nahe an den Bohrungsgrund 34 reicht. Der mit seinem Außendurchmesser nahezu dem Innendurchmesser der Ventilschließfeder 35 entsprechende Schaft 36 des Schließkörpers 28 ist über den Ventilteller 29 hinaus um ein geringes Maß verlängert und in der Ventilplatte 24 längsbewegbar geführt. Da der achsgleich zum Pumpenkolben 16 verlaufende Schaft 36 des Schließkörpers 28 zusammen mit der VentilSchließfeder 35 weitgehend das Volumen der Längsbohrung 33 des Pumpenkolbens 16 ausfüllen, ist, wie Figur 2 zeigt, das Totvolumen der Pumpe gering. Wie Figur 2 ebenfalls zeigt, ist der Zylinderraum 32 saugventilseitig im Durchmesser gegenüber dem Pumpenkolben 16 geringfügig vergrößert und steht in diesem vergrößerten Abschnitt mit dem Druckventil 19 in Verbindung.Pump piston 16 arranged in the pump housing 11 has a longitudinal bore 33 designed as a blind bore, which ends in a flat bore base 34. A valve closing spring 35 designed as a helical compression spring is accommodated in the longitudinal bore 33 which is arranged coaxially with the pump piston 16. Since the pump piston 16 located in its top dead center position in FIG. 2 extends close to the valve plate 24 delimiting the cylinder chamber 22, the valve closing spring 35 is located for the most part in its length in the longitudinal bore 33 of the pump piston. The valve closing spring 35 has an outer diameter largely adapted to the diameter of the longitudinal bore 33 of the pump piston 16 and engages on the one hand on the bore base 34 and on the other hand on the valve plate 29. The closing body 28 of the suction valve 18 is provided with a pin-shaped shaft 36 which is guided through the interior of the valve closing spring 35 and, in the illustrated dead center position of the pump piston 16 and the closing position of the suction valve 18, extends close to the bottom 34 of the bore. The outer diameter of the shaft 36 of the closing body 28, which corresponds almost to the inner diameter of the valve closing spring 35, is extended by a small amount beyond the valve plate 29 and is longitudinally movable in the valve plate 24. Since the shaft 36 of the closing body 28, which runs coaxially with the pump piston 16, together with the valve closing spring 35 largely fill the volume of the longitudinal bore 33 of the pump piston 16, the dead volume of the pump is low, as shown in FIG. As FIG. 2 also shows, the diameter of the cylinder space 32 on the suction valve side is opposite that of the pump piston 16 slightly enlarged and is in this enlarged section with the pressure valve 19 in connection.
In der gezeichneten Stellung des Pumpenkolbens 16 übt die Ventilschließfeder 35 eine maximale Schließkraft auf den Ventilteller 29 des Saugventils 18 aus und hält dieses geschlossen. Beim Saughub des Pumpenkolbens 16 wird dieser aus der gezeichneten Stellung in Richtung auf den Exzenterabschnitt 13 der Antriebswelle 12 bewegt. Dabei erfährt die Ventilschließfeder 35 eine Verringerung ihrer Schließkraft. Der durch den Kanal 20 dem Saugventil 18 zugeführte Kraftstoff unter Niederdruck übt eine der Federkraft entgegengerichtete Öffnungskraft auf den Ventilteller 29 aus. Bei Überwiegen der Öffnungskraft wird das Saugventil 18 geöffnet, das heißt der Ventilteller 29 hebt vom Ventilsitz 27 ab und bewegt sich um ein geringes Maß in den Zylinderraum 32 hinein. Das Öffnen des Saugventils 18 erfolgt in Abhängigkeit vom Druck des zugeführten Kraftstoffs: bei hohem Druck findet das Öffnen des Saugventils 18 bereits bei geringem Saughub des Pumpenkolbens 16 statt; bei niedrigem Druck wird das Saugventil geöffnet, wenn der Pumpenkolben 16 einen größeren Saughub zurückgelegt hat. Die Ventilschließfeder 35 ist jedoch so ausgelegt, daß bei geringen Drücken des zugeführten Kraftstoffs das Saugventil 18 bei großem Saughub des Pumpenkolbens 16 sicher öffnet und eine Teilbefüllung des Zylinderraums 32 erfolgt. Aufgrund des sichergestellten Öffnens des Saugventils 18 ist in entsprechender Weise auch die Teilbefüllung der übrigen Pumpenelemente 22 der Radialkolbenpumpe 10 gegeben. In the drawn position of the pump piston 16, the valve closing spring 35 exerts a maximum closing force on the valve plate 29 of the suction valve 18 and keeps it closed. During the suction stroke of the pump piston 16, the latter is moved from the position shown in the direction of the eccentric section 13 of the drive shaft 12. The valve closing spring 35 experiences a reduction in its closing force. The fuel supplied to the suction valve 18 through the channel 20 under low pressure exerts an opening force against the spring force on the valve plate 29. When the opening force predominates, the suction valve 18 is opened, that is to say the valve plate 29 lifts off the valve seat 27 and moves a small amount into the cylinder space 32. The opening of the suction valve 18 is dependent on the pressure of the fuel supplied: at high pressure, the opening of the suction valve 18 takes place even with a slight suction stroke of the pump piston 16; at low pressure, the suction valve is opened when the pump piston 16 has covered a larger suction stroke. The valve closing spring 35 is, however, designed such that, at low pressures of the supplied fuel, the suction valve 18 opens securely with a large suction stroke of the pump piston 16 and the cylinder space 32 is partially filled. Due to the ensured opening of the suction valve 18, the partial filling of the remaining pump elements 22 of the radial piston pump 10 is also given in a corresponding manner.

Claims

Ansprüche Expectations
1. Radialkolbenpumpe (10) für Kraftstoffhochdruckerzeugung bei Kraftstoffeinspritzsystem von Brennkraftmaschinen, insbesondere bei einem Common-Rail -Einspritzsystem, mit einem längsbewegbaren, federbelasteten Pumpenkolben (16) in einem Zylinderraum (32), welcher mit einem Saugventil (18) in Verbindung steht, dessen wenigstens mittelbar in den Zylinderraum (32) öffnender Schließkörper (28) von einer in Richtung auf seinen gehäusefesten Ventilsitz (27) wirkenden Ventilschließfeder (35) belastet ist, dadurch gekennzeichnet, daß die Ventilschließfeder (35) am Pumpenkolben (16) abgestützt ist.1. Radial piston pump (10) for high-pressure fuel generation in the fuel injection system of internal combustion engines, in particular in a common rail injection system, with a longitudinally movable, spring-loaded pump piston (16) in a cylinder space (32), which is connected to a suction valve (18), the Closing body (28) opening at least indirectly into the cylinder space (32) is loaded by a valve closing spring (35) acting in the direction of its valve seat (27) fixed to the housing, characterized in that the valve closing spring (35) is supported on the pump piston (16).
2. Radialkolbenpumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Ventilschließfeder (35) als2. Radial piston pump according to claim 1, characterized in that the valve closing spring (35) as
Schraubendruckfeder ausgebildet und zum überwiegenden Teil ihrer Länge in einer Längsbohrung (33) des Pumpenkolbens (16) aufgenommen ist.Helical compression spring is formed and for the most part of its length is received in a longitudinal bore (33) of the pump piston (16).
3. Radialkolbenpumpe nach Anspruch 2, dadurch gekennzeichnet, daß ein stiftförmiger Schaft (36) des Schließkörpers (28) innerhalb der Ventilschließfeder (35) geführt ist. 3. Radial piston pump according to claim 2, characterized in that a pin-shaped shaft (36) of the closing body (28) is guided within the valve closing spring (35).
4. Radialkolbenpumpe nach Anspruch 3 , dadurch gekennzeichnet, daß die Ventilschließfeder (35) mit ihrem einen Ende am Grund (34) der als Sacklochbohrung ausgebildeten Längsbohrung (39) des Pumpenkolbens (16) und mit ihrem anderen Ende an einem Ventilteller (29) des Schließkörpers (28) des Saugventils (18) abgestützt ist, von dem der stiftförmige Schaft (36) des Schließkörpers (28) ausgeht . 4. Radial piston pump according to claim 3, characterized in that the valve closing spring (35) with one end at the bottom (34) of the longitudinal bore (39) of the pump piston (16) designed as a blind hole and with its other end on a valve plate (29) of Shutting body (28) of the suction valve (18) is supported, from which the pin-shaped shaft (36) of the closing body (28) extends.
EP99939926A 1998-10-17 1999-06-22 Radial piston pump for supplying fuel at high pressure Expired - Lifetime EP1121531B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19848035 1998-10-17
DE19848035A DE19848035A1 (en) 1998-10-17 1998-10-17 Radial piston pump for high fuel pressure in IC engines with common-rail injection system has suction valve closure spring supported on pump piston and contained in long piston bore
PCT/DE1999/001815 WO2000023711A1 (en) 1998-10-17 1999-06-22 Radial piston pump for supplying fuel at high pressure

Publications (2)

Publication Number Publication Date
EP1121531A1 true EP1121531A1 (en) 2001-08-08
EP1121531B1 EP1121531B1 (en) 2003-01-22

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EP99939926A Expired - Lifetime EP1121531B1 (en) 1998-10-17 1999-06-22 Radial piston pump for supplying fuel at high pressure

Country Status (5)

Country Link
US (1) US6457957B1 (en)
EP (1) EP1121531B1 (en)
JP (1) JP4681119B2 (en)
DE (2) DE19848035A1 (en)
WO (1) WO2000023711A1 (en)

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Also Published As

Publication number Publication date
US6457957B1 (en) 2002-10-01
DE19848035A1 (en) 2000-04-20
WO2000023711A1 (en) 2000-04-27
EP1121531B1 (en) 2003-01-22
JP2003527516A (en) 2003-09-16
JP4681119B2 (en) 2011-05-11
DE59904114D1 (en) 2003-02-27

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