EP0347581B1 - Injection pump for internal-combustion engines - Google Patents

Injection pump for internal-combustion engines Download PDF

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Publication number
EP0347581B1
EP0347581B1 EP89108890A EP89108890A EP0347581B1 EP 0347581 B1 EP0347581 B1 EP 0347581B1 EP 89108890 A EP89108890 A EP 89108890A EP 89108890 A EP89108890 A EP 89108890A EP 0347581 B1 EP0347581 B1 EP 0347581B1
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EP
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Prior art keywords
accumulator chamber
pressure
valve
fuel
injection pump
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EP89108890A
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German (de)
French (fr)
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EP0347581A1 (en
Inventor
Jaroslaw Dipl.-Ing. Hlousek
Gerhard Dr. Dipl.-Ing. Lehner
Theodor Dr. Dipl.-Ing. Stipek
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/005—Pressure relief 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/001—Pumps with means for preventing erosion on fuel discharge
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/04—Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
    • 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

Definitions

  • the invention relates to an injection pump for internal combustion engines, with a pump piston sleeve and a pump piston guided therein with control edges for controlling the start and end of an injection process, which interact with control holes provided in the wall of the pump piston sleeve, which open into a collecting space surrounding the pump piston sleeve. into which fuel can be supplied under pressure and from which excess fuel or fuel that overflows at the end of an injection process can be derived, a suction valve opening to the collecting chamber being connected to the collecting chamber for the fuel supply and an organ influencing the flow being connected to the collecting chamber for fuel discharge is.
  • the invention now aims to achieve the control of the injection pressure at the end of delivery against the highest possible pressure without complex design measures.
  • the invention essentially consists in the collecting space being designed as a storage space with a pressure-maintaining valve opening away from the storage space. Because the collecting space or suction space is now not open to the inlet as in the known measures, but is designed as a storage space closed by valves and a check valve is arranged as a pressure-maintaining valve, a predetermined and relatively high pressure can be ensured as the control pressure. The pressure in the working chamber of the piston then drops further and only when the pressure has dropped to a pressure level sufficient that the pump pressure can be used to refill the working chamber, is the filling again carried out with the much lower pump pressure.
  • the training is so made that the storage space concentric with a suction space Control holes of the pump piston liner is connected, which results in a particularly simple design.
  • the training can be carried out in such a way that the pressure-maintaining valve opening away from the storage space and the suction valve opening toward the storage space are jointly connected on the side facing away from the storage space to the suction space supplied with fuel and are formed by check valves.
  • the suction valve which is designed as a non-return valve and opens to the storage chamber, causes fuel to be sucked in again when the pressure in the pump chamber drops below the set pressure of the suction valve.
  • the low pressure suction frame i.e. the space under pre-pump pressure, fuel sucked in to fill the injection pump.
  • the design can advantageously be such that the pressure-maintaining valve opening away from the storage space is connected to the storage space via a throttle point known per se.
  • the pressure to be maintained in the storage space is hereby defined by the check valve and kept at an exactly predetermined level, such additional throttle bores allowing short-term peak pressures to be reduced.
  • the pressure level remains constant after the predetermined pressure level has been reached and that the corresponding pressure level can be ensured in a simple manner by dimensioning or adjusting the pressure control valve.
  • the arrangement is such that the axes of the mouths of the check valves on the storage space side are arranged offset with respect to the axes of the control bores.
  • Impact protection rings of this type are not suitable for preventing cavitation phenomena, but only serve to provide materials which are particularly wear-resistant in the place of particularly high wear and tear and to create an easily replaceable wear part which can be replaced in the event of excessive wear .
  • Impact protection devices of the usual type in particular, can in no way counteract cavitation phenomena on the outer wall of the pump piston.
  • the design within the scope of the present invention can advantageously be made such that at the mouth on the storage space side At least one impact valve is arranged axially with a control bore check valve.
  • the design is such that a baffle plate that closes the bore is arranged in front of an axial bore of the check valve, on the rear side of which a transverse bore intersecting the axial bore of the check valve is provided with open ends, which in turn rinses or flushes away of any bubbles that may arise.
  • the baffle plate can be formed in one piece with the housing of the check valve, which considerably simplifies the installation of the check valve.
  • a known design of such an impact protection body is that it is frustoconical in cross-section and is rounded on the side facing the bore.
  • Such designs of impact protection bodies are characterized by particularly high wear resistance and with such a design, the arrangement of the check valve or pressure-maintaining valve opening to the storage space is advantageously made such that the control bore has a section that is frustoconically enlarged to the storage space such that the housing of the opening to the storage space
  • Non-return valve has a conical end part with a rounded tip which projects into the frustoconically widened section, leaving a space free, and that the outlet channel of the non-return valve opens off-center in the region of the conical jacket of the end part. The flow path resulting in this way in turn leads to a flushing out of particularly critical points.
  • FIG. 1 shows a partial section through the upper part of an injection pump for large diesel engines
  • 2 shows a development of a detail of the injection pump according to FIG. 1
  • 3 shows a diagram of the course of pump chamber pressure and storage chamber pressure over the cam angle
  • FIGS. 4, 5 and 6 in a representation similar to that of FIG. 1, variants of the construction of an injection pump with direct supply and discharge of fuel into and from the Storage space and training of an impact protection.
  • a pump piston 2 is moved up and down in a pump piston liner 1 by a cam drive, not shown.
  • the pump piston liner 1 is supported in a housing 3 which has a suction space 4, into which fuel is supplied via a pipe screw connection 5 or from which excess fuel is derived.
  • When going up the pump piston 2 closes with its upper edge 6 control bores 7.
  • a throttle 13 can be installed in the inlet of the pressure-maintaining valve 11, which causes a quantity-dependent increase in the storage space pressure, so that a further reduction in the risk of cavity formation in the fuel is achieved with larger delivery quantities and / or higher speeds or piston speeds.
  • the suction valve 10 and the pressure holding valve 11 are accommodated in a sleeve 14 which also contains the storage space 9.
  • a pressure seal of the storage space 9 and the suction space 4 is carried out by means of sealing rings 15, 16 and 17 down between pump piston 2 and pump piston liner 1, returned to the storage space 9.
  • valves 10, 11 or their flow openings are arranged in a sectional plane with the control bores 7 in the pump cylinder, but rather to arrange them rotated by 90 °, for example.
  • two or more pressure-maintaining or suction valves can also be arranged in the sleeve 14 if required.
  • FIG. 3 shows the curves of pump chamber pressure p P and storage chamber pressure p S over the cam angle, the start of delivery of the injection pump being designated FB and the end of delivery being FE. From the diagram it can be seen that the pressure p S in the storage space 9 already reaches the holding value of the valve 11 at the start of delivery and that a short-term dynamic pressure increase occurs in the storage space 9 immediately after the end of the delivery due to the deactivated fuel which shoots out of the control bores 7, after which Filling the pump chamber 8, the pressure initially drops to the delivery pressure of the backing pump, and then increases again after the upward gear of the pump piston 2 begins.
  • a throttle bore in front of the pressure-maintaining valve can also achieve a dependency of the storage space pressure on the delivery volume and the speed of the pump, different diameters of the throttle 13 resulting in different pressure profiles in the region of the pressure increase, as indicated in FIG. 3.
  • the axes of the bores towards the valves 10 and 11 are offset relative to the control bores 7, so that any cavities formed in the fuel can be quickly washed away by the jet emerging from the control bore 7 and any corrosion that may occur is kept away from hazardous areas.
  • feed 19 and discharge line 20 of the fuel lie coaxially with the control bores 7, but the bore of each of the valves 10, 11 facing the control bore 7 is connected upstream of a baffle plate 21 or 22, each of which with the Armature of the associated valve is integrally formed.
  • the suction valve 10 is installed on both sides in an impact protection which has a conical shape and projects far into the control bore 7.
  • the fuel is conveyed through a bore 23 coming from the suction valve 10 into the gap between the cone 24 of the impact protection and the conical extension 25 of the control bore.
  • the bore 23 is positioned in such a way that it allows the fuel to exit at the highest part of the gap, so that the cavities in the fuel are hit directly by the flushing stream and conveyed into the storage space 9.
  • a pressure control valve not shown, ensures the maintenance of an increased standing pressure in the storage space 9 after the end of the control process until it is sucked in again.
  • the fuel is advantageously supplied at a pressure of 5 to 20 bar, in order to achieve a sufficient flushing effect in the control bores 7.
  • a pressure accumulator in the fuel line between the feed pump and suction valve 10 appears to be useful for making the inlet pressure more uniform.

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

Description

Die Erfindung bezieht sich auf eine Einspritzpumpe für Brennkraftmaschinen, mit einer Pumpenkolbenbüchse und einem in dieser geführten Pumpenkolben mit Steuerkanten zur Steuerung von Beginn und Ende eines Einspritzvorganges, welche mit in der Wand der Pumpenkolbenbüchse vorgesehenen Steuerbohrungen zusammenwirken, die in einen die Pumpenkolbenbüchse umgebenden Sammelraum münden, in welchen Brennstoff unter Druck zuführbar ist und aus welchem überschüssiger Brennstoff bzw. bei Beendigung eines Einspritzvorganges überströmender Brennstoff ableitbar ist, wobei für die Brennstoffzuführung ein zum Sammelraum öffnendes Saugventil an den Sammelraum angeschlossen ist und für die Brennstoffableitung ein die Strömung beeinflussendes Organ an den Sammelraum angeschlossen ist.The invention relates to an injection pump for internal combustion engines, with a pump piston sleeve and a pump piston guided therein with control edges for controlling the start and end of an injection process, which interact with control holes provided in the wall of the pump piston sleeve, which open into a collecting space surrounding the pump piston sleeve. into which fuel can be supplied under pressure and from which excess fuel or fuel that overflows at the end of an injection process can be derived, a suction valve opening to the collecting chamber being connected to the collecting chamber for the fuel supply and an organ influencing the flow being connected to the collecting chamber for fuel discharge is.

Beim Betrieb von Einspritzpumpen unter hohem Druck bestehen beim Absteuern an der Niederdruckseite Korrosionsprobleme, welche auf Kavitationserscheinungen zurückgeführt werden. Beim Absteuern des Hochdruckbrennstoffes aus dem Pumpenraum in den Saugraum der Einspritzpumpe im Augenblick des Förderendes entstehen Druckschwingungen mit hohen Spitzenwerten. Im Saugraum befindliche Hohlräume, welche vom vorhergehenden Zusteuervorgang herrühren, können dabei implodieren und zu Kavitationsschäden am Kolbenumfang, in der Steuerbohrung und im Saugraum führen. Weiters erzeugt der Absteuerstrahl in seinen Rand- und Auftreffzonen sekundäre Hohlräume, die beim anschließenden Implodieren ebenfalls Schäden an den genannten Stellen bewirken können. Aus der CH-PS 594 134 ist es bereits bekannt geworden, den abgesteuerten Brennstoff, welcher in den Saugraum rückgeführt wird, über Drosseln abzufördern, um auf diese Weise ein gewisses Ausmaß einer Druckerhöhung zu erzielen. Das Ausmaß der erzielbaren Druckerhöhung mit derartigen Maßnahmen ist relativ gering und ein entscheidender Vorteil könnte erst dann erreicht werden, wenn ein entsprechend hoher Pumpenvordruck gewählt wird. Dies erfordert aber wiederum einen hohen Aufwand an Pumpenenergie und eine entsprechend aufwendige Abdichtung der Pumpe im Saugraumbereich.When operating injection pumps under high pressure, there are corrosion problems on the low-pressure side, which are attributed to cavitation phenomena. When the high-pressure fuel is diverted from the pump chamber into the suction chamber of the injection pump at the moment of delivery, pressure fluctuations with high peak values occur. Cavities in the suction chamber, which result from the previous actuation process, can implode and lead to cavitation damage to the piston circumference, in the control bore and in the suction chamber. In addition, the diverter jet creates secondary cavities in its edge and impact zones, which can also cause damage at the points mentioned when subsequently imploded. From CH-PS 594 134 it has already become known to discharge the deactivated fuel, which is returned to the suction chamber, via throttles in order to achieve a certain degree of pressure increase in this way. The extent The achievable pressure increase with such measures is relatively small and a decisive advantage could only be achieved if a correspondingly high pump admission pressure is selected. However, this in turn requires a high expenditure of pump energy and a correspondingly complex sealing of the pump in the suction area.

Durch die DE-C 762 581 ist es ferner bekannt, in die Zuleitung des Saugraums einer Kraftstoffeinspritzpumpe ein zum Saugraum öffnendes Rückschlagventil und in die Ableitung des Saugraumes zum Kraftstoffvorratsbehälter hin ein in Richtung Kraftstoffvorratsbehälter öffnendes Rückschlagventil vorzusehen. Diese Rückschlagventile sind mit einer sehr kleinen Schließkraft belastet und haben bei der bekannten Kraftstoffeinspritzpumpe die Aufgabe, eine gerichtete Strömung durch den Saugraum sicherzustellen, wobei kein wesentlicher Druckunterschied zwischen Saugraum und Kraftstoffleitung stromauf- bzw. stromabwärts der Rückschlagventile vorliegt.From DE-C 762 581 it is also known to provide a non-return valve opening to the suction chamber in the feed line of a fuel injection pump and a non-return valve opening in the direction of the fuel tank in the derivative of the suction chamber to the fuel tank. These check valves are loaded with a very small closing force and, in the known fuel injection pump, have the task of ensuring a directed flow through the suction chamber, with no significant pressure difference between the suction chamber and the fuel line upstream or downstream of the check valves.

Die Erfindung zielt nun darauf ab, die Absteuerung des Einspritzdruckes bei Förderende gegen einen möglichst hohen Druck ohne aufwendige konstruktive Maßnahmen zu erzielen. Zur Lösung dieser Aufgabe besteht die Erfindung im wesentlichen darin, daß der Sammelraum als Speicherraum mit einem vom Speicherraum weg öffnenden Druckhalteventil ausgebildet ist. Dadurch, daß der Sammelraum bzw. Saugraum nunmehr nicht wie bei den bekannten Maßnahmen zum Zulauf hin offen ist, sondern als durch Ventile abgeschlossener Speicherraum ausgebildet ist und ein Rückschlagventil als Druckhalteventil angeordnet ist, läßt sich ein vorgegebener und relativ hoher Druck als Absteuerdruck sicherstellen. Der Druck im Arbeitsraum des Kolbens sinkt in der Folge weiter ab und erst wenn der Druck insgesamt auf ein Druckniveau abgesunken ist, welches ausreicht, daß der Pumpenvordruck für eine neuerliche Füllung des Arbeitsraumes herangezogen werden kann, erfolgt die neuerliche Füllung mit dem wesentlich niedrigeren Pumpenvordruck. Es wird somit die Absteuerung nicht unmittelbar in den zum Zulauf offenen Saugraum vorgenommen, sondern in den Speicherraum und dieser Speicherraum kann mittels des vom Speicherraum weg öffnenden Rückschlagventils bzw. des Druckhalteventils auf einen Druck von bis zu 50 bar oder auch höher gehalten werden, so daß der Ausbildung von Kavitationserscheinungen wirksam entgegengetreten wird. Beim Saugvorgang des Pumpenkolbens wird der Brennstoff zuerst aus diesem Speicherraum entnommen und erst in der Folge beispielsweise unter Verwendung eines Saugventils weiterer Brennstoff angesaugt.The invention now aims to achieve the control of the injection pressure at the end of delivery against the highest possible pressure without complex design measures. To achieve this object, the invention essentially consists in the collecting space being designed as a storage space with a pressure-maintaining valve opening away from the storage space. Because the collecting space or suction space is now not open to the inlet as in the known measures, but is designed as a storage space closed by valves and a check valve is arranged as a pressure-maintaining valve, a predetermined and relatively high pressure can be ensured as the control pressure. The pressure in the working chamber of the piston then drops further and only when the pressure has dropped to a pressure level sufficient that the pump pressure can be used to refill the working chamber, is the filling again carried out with the much lower pump pressure. It is therefore not controlled directly into the suction space open to the inlet, but rather into the storage space and this storage space can be kept at a pressure of up to 50 bar or higher by means of the check valve or pressure-maintaining valve opening away from the storage space, so that the formation of cavitation is effectively counteracted. During the suction process of the pump piston, the fuel is first removed from this storage space and only then is further fuel sucked in, for example using a suction valve.

Mit Vorteil ist die Ausbildung hiebei so getroffen, daß der Speicherraum konzentrisch zu einem Saugraum an die Steuerbohrungen der Pumpenkolbenbüchse angeschlossen ist, wodurch sich eine konstruktiv besonders einfache Ausgestaltung ergibt.Advantageously, the training is so made that the storage space concentric with a suction space Control holes of the pump piston liner is connected, which results in a particularly simple design.

In besonders einfacher Weise kann die Ausbildung hiebei so getroffen werden, daß das vom Speicherraum weg öffnende Druckhalteventil und das zum Speicherraum öffnende Saugventil an der vom Speicherraum abgewendeten Seite gemeinsam an den mit Brennstoff versorgten Saugraum angeschlossen sind und von Rückschlagventilen gebildet sind. Durch das zum Speicherraum öffnende, als Rückschlagventil ausgebildete Saugventil erfolgt ein neuerliches Ansaugen von Brennstoff dann, wenn der Druck im Pumpenraum unter den eingestellten Druck des Saugventils absinkt. In diesem Fall wird aus dem Niederdrucksaugram, d.h. dem unter Vorpumpendruck stehenden Raum, Brennstoff zur Füllung der Einspritzpumpe angesaugt.In a particularly simple manner, the training can be carried out in such a way that the pressure-maintaining valve opening away from the storage space and the suction valve opening toward the storage space are jointly connected on the side facing away from the storage space to the suction space supplied with fuel and are formed by check valves. The suction valve, which is designed as a non-return valve and opens to the storage chamber, causes fuel to be sucked in again when the pressure in the pump chamber drops below the set pressure of the suction valve. In this case the low pressure suction frame, i.e. the space under pre-pump pressure, fuel sucked in to fill the injection pump.

Um unerwünschte Druckspitzen bei Aufbau des Druckes im Speicherraum zu vermeiden, kann die Ausbildung mit Vorteil so getroffen sein, daß das vom Speicherraum weg öffnende Druckhalteventil über eine an sich bekannte Drosselstelle an den Speicherraum angeschlossen ist. Der im Speicherraum aufrecht zu erhaltende Druck wird hiebei vom Rückschlagventil definiert und auf einem exakt vorgegebenen Niveau gehalten, wobei derartige zusätzliche Drosselbohrungen kurzfristige Spitzendrücke abzubauen gestatten. Gegenüber der Verwendung von Drosseln ohne ein Druckhalteventil ergibt sich in jedem Fall der Vorteil, daß das Druckniveau nach Erreichen des vorgegebenen Druckniveaus konstant bleibt und daß das entsprechende Druckniveau in einfacher Weise durch die Dimensionierung bzw. Einstellung des Druckhalteventils sichergestellt werden kann.In order to avoid undesirable pressure peaks when the pressure builds up in the storage space, the design can advantageously be such that the pressure-maintaining valve opening away from the storage space is connected to the storage space via a throttle point known per se. The pressure to be maintained in the storage space is hereby defined by the check valve and kept at an exactly predetermined level, such additional throttle bores allowing short-term peak pressures to be reduced. Compared to the use of throttles without a pressure control valve, there is the advantage in any case that the pressure level remains constant after the predetermined pressure level has been reached and that the corresponding pressure level can be ensured in a simple manner by dimensioning or adjusting the pressure control valve.

Gemäß einer weiteren bevorzugten Ausbildung zur Verringerung des Verschleißes ist die Anordnung so getroffen, daß die Achsen der speicherraumseitigen Mündungen der Rückschlagventile bezüglich der Achsen der Steuerbohrungen versetzt angeordnet sind. Eine derartige versetzte Anordnung der Steuerbohrungen ermöglicht es, die besonders verschleißgefährdeten Bereiche, in welchen Kavitation auftreten könnte, durch geeignete Orientierung des eintretenden Strahles rasch zu spülen, so daß gegebenenfalls dennoch entstandene Blasen weggeschwemmt werden. Gegebenenfalls dennoch auftretende Korrosionserscheinungen können hiebei von besonders gefährdeten Stellen ferngehalten werden.According to a further preferred embodiment to reduce wear, the arrangement is such that the axes of the mouths of the check valves on the storage space side are arranged offset with respect to the axes of the control bores. Such a staggered arrangement of the control bores makes it possible to quickly find the areas at risk of wear, in which cavitation could occur, by suitable orientation of the incoming beam to rinse so that any bubbles that may have formed are washed away. If there are any signs of corrosion, they can be kept away from particularly vulnerable areas.

Bei bekannten Einspritzpumpenkonstruktionen ist es bekannt, den übermäßigen Verschleiß beim Absteuervorgang dadurch zu mindern, daß in die Abströmöffnungen Prallschutzeinrichtungen eingebaut werden. Derartige Prallschutzringe sind nicht geeignet Kavitationserscheinungen zu verhindern, sondern dienen lediglich dazu, an der Stelle besonders hoher Abnutzung und besonders großen Verschleißes Materialien vorzusehen, welche besonders verschleißbeständig sind, und dazu, einen leicht austauschbaren Verschleißteil zu schaffen, welcher im Fall übermäßigen Verschleißes getauscht werden kann. Mit Prallschutzeinrichtungen üblicher Art kann aber insbesondere Kavitationserscheinungen an der Außenwand des Pumpenkolbens in keiner Weise begegnet werden. Wenn nun zusätzlich der lediglich auf große Strömungsgeschwindigkeiten, nicht aber auf Kavitation zurückzuführende Verschleiß weiter herabgemindert werden soll und an derartigen Stellen ein leicht austauschbarer Bauteil geschaffen werden soll, kann mit Vorteil die Ausbildung im Rahmen der vorliegenden Erfindung so getroffen werden, daß bei der speicherraumseitigen Mündung wenigstens eines mit einer Steuerbohrung axial ausgerichteten Rückschlagventils ein Prallschutz angeordnet ist. Mit Vorteil ist die Ausbildung hiebei so getroffen, daß als Prallschutz vor einer axialen Bohrung des Rückschlagventils eine die Bohrung verschließende Prallplatte angeordnet ist, bei deren Rückseite eine die axiale Bohrung des Rückschlagventils schneidende Querbohrung mit offenen Enden vorgesehen ist, wodurch wiederum ein Freispülen bzw. Wegspülen von gegebenenfalls entstehenden Blasen sichergestellt wird. In besonders einfacher Weise kann hiebei die Prallplatte mit dem Gehäuse des Rückschlagventils einstückig ausgebildet sein, wodurch der Einbau des Rückschlagventils wesentlich vereinfacht wird.In known injection pump designs, it is known to reduce the excessive wear during the control process by installing impact protection devices in the outflow openings. Impact protection rings of this type are not suitable for preventing cavitation phenomena, but only serve to provide materials which are particularly wear-resistant in the place of particularly high wear and tear and to create an easily replaceable wear part which can be replaced in the event of excessive wear . Impact protection devices of the usual type, in particular, can in no way counteract cavitation phenomena on the outer wall of the pump piston. If, in addition, the wear, which can only be attributed to high flow velocities, but not due to cavitation, is to be further reduced and an easily replaceable component is to be created at such locations, the design within the scope of the present invention can advantageously be made such that at the mouth on the storage space side At least one impact valve is arranged axially with a control bore check valve. Advantageously, the design is such that a baffle plate that closes the bore is arranged in front of an axial bore of the check valve, on the rear side of which a transverse bore intersecting the axial bore of the check valve is provided with open ends, which in turn rinses or flushes away of any bubbles that may arise. In a particularly simple manner, the baffle plate can be formed in one piece with the housing of the check valve, which considerably simplifies the installation of the check valve.

Eine an sich bekannte Ausbildung eines derartigen Prallschutzkörper besteht darin, daß dieser im Querschnitt kegelstumpfförmig ausgebildet ist und an der der Bohrung zugewandten Seite verrundet ist. Derartige Ausbildungen von Prallschutzkörpern zeichnen sich durch besonders hohe Verschleißbeständigkeit aus und bei einer derartigen Ausbildung ist die Anordnung des zum Speicherraum öffnenden Rückschlagventils bzw. Druckhalteventils mit Vorteil so getroffen, daß die Steuerbohrung einen zum Speicherraum kegelstumpfförmig erweiterten Abschnitt aufweist, daß das Gehäuse des zum Speicherraum öffnenden Rückschlagventils einen in den kegelstumpfförmig erweiterten Abschnitt unter Freilassung eines Zwischenraumes hineinragenden kegeligen Endteil mit abgerundeter Spitze hat und daß der Auslaßkanal des Rückschlagventils außermittig im Bereich des Kegelmantels des Endteiles mündet. Der sich auf diese Weise ergebende Strömungsweg führt wiederum zu einem Freispülen von besonders kritischen Stellen.A known design of such an impact protection body is that it is frustoconical in cross-section and is rounded on the side facing the bore. Such designs of impact protection bodies are characterized by particularly high wear resistance and with such a design, the arrangement of the check valve or pressure-maintaining valve opening to the storage space is advantageously made such that the control bore has a section that is frustoconically enlarged to the storage space such that the housing of the opening to the storage space Non-return valve has a conical end part with a rounded tip which projects into the frustoconically widened section, leaving a space free, and that the outlet channel of the non-return valve opens off-center in the region of the conical jacket of the end part. The flow path resulting in this way in turn leads to a flushing out of particularly critical points.

Die Erfindung wird nachfolgend an Hand von in der Zeichnung dargestellten Ausführungsbeispielen näher erläutert. In dieser zeigt: Fig.1 einen Teilschnitt durch den Oberteil einer Einspritzpumpe für große Dieselmotoren; Fig.2 eine Weiterbildung einer Einzelheit der Einspritzpumpe nach Fig.1; Fig.3 in einem Diagramm den Verlauf von Pumpenraumdruck und Speicherraumdruck über dem Nockenwinkel und die Fig.4, 5 und 6 in ähnlicher Darstellung wie Fig.1 Varianten der Konstruktion einer Einspritzpumpe mit unmittelbarer Zu-und Ableitung von Brennstoff in den bzw. aus dem Speicherraum sowie Ausbildung eines Prallschutzes.The invention is explained in more detail below with reference to exemplary embodiments shown in the drawing. 1 shows a partial section through the upper part of an injection pump for large diesel engines; 2 shows a development of a detail of the injection pump according to FIG. 1; 3 shows a diagram of the course of pump chamber pressure and storage chamber pressure over the cam angle and FIGS. 4, 5 and 6 in a representation similar to that of FIG. 1, variants of the construction of an injection pump with direct supply and discharge of fuel into and from the Storage space and training of an impact protection.

Bei der in Fig.1 dargestellten Einspritzpumpe wird in einer Pumpenkolbenbüchse 1 ein Pumpenkolben 2 durch einen nicht dargestellten Nockenantrieb auf und ab bewegt. Die Pumpenkolbenbüchse 1 ist in einem Gehäuse 3 abgestützt, das einen Saugraum 4 aufweist, in welchen über eine Rohrverschraubung 5 Brennstoff zugeführt wird bzw. aus welchem überschüssiger Brennstoff abgeleitet wird. Beim Aufwärtsgang des Pumpenkolbens 2 verschließt dieser mit seiner Oberkante 6 Steuerbohrungen 7. Bereits kurz vorher baut sich wegen der Drosselung des aus dem Pumpenraum 8 durch den aufwärtsgehenden Kolben 2 verdrängten Brennstoffes im Speicherraum 9 ein Brennstoffdruck auf, weil ein Saugventil 10 mit seinem Öffnungsdruck von einigen Zehntel bar in Richtung zum Saugraum 4 geschlossen hat und ein Druckhalteventil 11 einen Druck von etwa 20 bis 50 bar im Speicherraum aufrecht hält. Durch den im Speicherraum 9 aufgebauten Druck kommen Hohlräume bzw. Dampfblasen im Brennstoff, die beim Zusteuervorgang dort und in den Steuerbohrungen 7 entstehen können, zu einem verhältnismäßig weichen und damit unschädlichen Zusammenbrechen. Wenn der Pumpenkolben 2 bei seinem Aufwärtsgang mit seinen unteren Steuerkanten 12 die Verbindung zwischen Pumpenraum 8 und Steuerbohrungen 7 wieder öffnet, dann entspannt sich der Brennstoff von einem hohen Druck von etwa 1500 bar auf den vom Druckhalteventil 11 im Speicherraum 9 gehaltenen Druck von etwa 20 bis 50 bar. Wegen des großen Sicherheitsabstandes zum Dampfdruck des Brennstoffes kommt es im Bereich der Absteuerstrahlen nicht zu Hohlraumbildungen im Brennstoff und es wird daher auch die sogenannte Strahlkavitation im Auftreffbereich des Absteuerstrahls auf die Wand der Steuerbohrungen und des Speicherraumes vermieden. Sobald der Druck im Speicherraum 9 den Einstellwert des Druckhalteventils 11 überschreitet, öffnet dieses und läßt den überschüssigen Brennstoff aus dem Speicherraum 9 in den Saugraum 4 abströmen. Beide Ventile 10,11 sind als Rückschlagventile ausgebildet.In the injection pump shown in FIG. 1, a pump piston 2 is moved up and down in a pump piston liner 1 by a cam drive, not shown. The pump piston liner 1 is supported in a housing 3 which has a suction space 4, into which fuel is supplied via a pipe screw connection 5 or from which excess fuel is derived. When going up the pump piston 2 closes with its upper edge 6 control bores 7. Already shortly before, because of the throttling of the fuel displaced from the pump chamber 8 by the piston 2 rising upwards, a fuel pressure builds up in the storage chamber 9 because a suction valve 10 with its opening pressure of a few tenths of a bar has closed in the direction of the suction chamber 4 and a pressure maintaining valve 11 maintains a pressure of approximately 20 to 50 bar in the storage chamber. Due to the pressure built up in the storage space 9, cavities or vapor bubbles in the fuel, which can arise there during the actuation process and in the control bores 7, come to a relatively soft and thus harmless breakdown. When the pump piston 2 opens the connection between the pump chamber 8 and the control bores 7 again in its upward gear with its lower control edges 12, the fuel expands from a high pressure of approximately 1500 bar to the pressure of approximately 20 to held in the accumulator chamber 9 by the pressure control valve 11 50 bar. Because of the large safety distance to the vapor pressure of the fuel, there are no cavities in the area of the control jets and therefore the so-called jet cavitation in the area where the control jet strikes the wall of the control bores and the storage space is avoided. As soon as the pressure in the storage space 9 exceeds the set value of the pressure-maintaining valve 11, the latter opens and allows the excess fuel to flow out of the storage space 9 into the suction space 4. Both valves 10, 11 are designed as check valves.

In den Einlaß des Druckhalteventils 11 kann gemäß Fig.2 eine Drossel 13 eingebaut sein, die eine mengenabhängige Erhöhung des Speicherraumdruckes bewirkt, so daß bei größeren Fördermengen und/oder höheren Drehzahlen bzw. Kolbengeschwindigkeiten eine weitere Verringerung der Gefahr der Hohlraumbildung im Brennstoff erreicht wird. Das Saugventil 10 und das Druckhalteventil 11 sind in einer Hülse 14 untergebracht, die auch den Speicherraum 9 enthält. Durch Dichtungsringe 15, 16 und 17 erfolgt eine Druckabdichtung von Speicherraum 9 und Saugraum 4. Über eine Leckölbohrung 18 wird Brennstoff, der nach unten zwischen Pumpenkolben 2 und Pumpenkolbenbüchse 1 hindurchgelangt, in den Speicherraum 9 zurückgeführt.According to FIG. 2, a throttle 13 can be installed in the inlet of the pressure-maintaining valve 11, which causes a quantity-dependent increase in the storage space pressure, so that a further reduction in the risk of cavity formation in the fuel is achieved with larger delivery quantities and / or higher speeds or piston speeds. The suction valve 10 and the pressure holding valve 11 are accommodated in a sleeve 14 which also contains the storage space 9. A pressure seal of the storage space 9 and the suction space 4 is carried out by means of sealing rings 15, 16 and 17 down between pump piston 2 and pump piston liner 1, returned to the storage space 9.

Es ist zweckmäßig, die beiden Ventile 10, 11 bzw. deren Durchflußöffnungen nicht in einer Schnittebene mit den Steuerbohrungen 7 im Pumpenzylinder anzuordnen, sondern sie beispielsweise um 90° verdreht anzuordnen. Weiters können bei Bedarf auch zwei oder mehr Druckhalte- bzw. Saugventile in der Hülse 14 angeordnet werden.It is expedient not to arrange the two valves 10, 11 or their flow openings in a sectional plane with the control bores 7 in the pump cylinder, but rather to arrange them rotated by 90 °, for example. Furthermore, two or more pressure-maintaining or suction valves can also be arranged in the sleeve 14 if required.

Es ist schließlich möglich, die Auftreffbereiche der Absteuerstrahlen im Speicherraum 9 zu härten oder mit besonders harten Metallen zu panzern, um eine besonders hohe Standfestigkeit dieser Bereiche zu erzielen.Finally, it is possible to harden the impact areas of the diverter jets in the storage space 9 or to armor them with particularly hard metals in order to achieve a particularly high stability of these areas.

Fig.3 zeigt die Verläufe von Pumpenraumdruck pP und Speicherraumdruck pS über dem Nockenwinkel, wobei der Förderbeginn der Einspritzpumpe mit FB und das Förderende mit FE bezeichnet sind. Aus dem Diagramm ist ersichtlich, daß bereits bei Förderbeginn der Druck pS im Speicherraum 9 den Haltewert des Ventils 11 erreicht und daß unmittelbar nach dem Förderende durch den aus den Steuerbohrungen 7 herausschießenden abgesteuerten Brennstoff eine kurzzeitige dynamische Drucküberhöhung im Speicherraum 9 auftritt, wonach bei der Füllung des Pumpenraumes 8 der Druck zunächst bis auf den Förderdruck der Vorpumpe absinkt, um dann nach Beginn des Aufwärtsganges des Pumpenkolbens 2 neuerlich anzusteigen. Durch eine Drosselbohrung vor dem Druckhalteventil kann auch noch eine Abhängigkeit des Speicherraumdruckes von der Fördermenge und der Drehzahl der Pumpe erzielt werden, wobei verschiedene Durchmesser der Drossel 13 unterschiedliche Druckverläufe im Bereich der Drucküberhöhung ergeben, wie dies in Fig.3 angedeutet ist.3 shows the curves of pump chamber pressure p P and storage chamber pressure p S over the cam angle, the start of delivery of the injection pump being designated FB and the end of delivery being FE. From the diagram it can be seen that the pressure p S in the storage space 9 already reaches the holding value of the valve 11 at the start of delivery and that a short-term dynamic pressure increase occurs in the storage space 9 immediately after the end of the delivery due to the deactivated fuel which shoots out of the control bores 7, after which Filling the pump chamber 8, the pressure initially drops to the delivery pressure of the backing pump, and then increases again after the upward gear of the pump piston 2 begins. A throttle bore in front of the pressure-maintaining valve can also achieve a dependency of the storage space pressure on the delivery volume and the speed of the pump, different diameters of the throttle 13 resulting in different pressure profiles in the region of the pressure increase, as indicated in FIG. 3.

Bei den in den Fig.4 und 5 dargestellten Varianten ist kein eigener Saugraum vorgesehen, sondern Zuführung 19 und Ableitung 20 des Brennstoffes erfolgen unmittelbar in den bzw. aus dem Speicherraum 9, u.zw. über das Saugventil 10 bzw. das Druckhalteventil 11, so daß sich im Speicherraum 9 während des Zusteuervorganges unmittelbar vor dem geometrischen Förderbeginn ein höheres Druckniveau - bestimmt durch den eingestellten Druck des Druckhalteventils 11 - aufbauen kann. Beim Absteuern der Steuerbohrungen 7 stößt der Hochdruckstrahl in ein Brennstoffvolumen ohne Resthohlräume vom vorhergehenden Zusteuern. Auch die Strahlkavitation wird auf Grund des hohen Druckniveaus vermieden.In the variants shown in FIGS. 4 and 5, no separate suction space is provided, but fuel supply and discharge 20 take place directly into or out of the storage space 9, etc. via the suction valve 10 or the pressure-maintaining valve 11, so that a higher pressure level — determined by the set pressure of the pressure-maintaining valve 11 — builds up in the storage space 9 during the control process immediately before the geometric start of delivery can. When the control bores 7 are shut off, the high-pressure jet strikes a fuel volume without residual cavities from the previous control. Jet cavitation is also avoided due to the high pressure level.

Zweckmäßig erscheint es, in die Brennstoffleitung von der Förderpumpe einen Druckspeicher (Windkessel) einzubauen, dessen Volumen etwa das 5 bis 20-fache des Speicherraumvolumens betragen sollte. Dadurch wird eine zuverlässige Füllung des Speicherraumes und des Pumpenraumes erreicht.It seems advisable to install a pressure accumulator (wind boiler) in the fuel line from the feed pump, the volume of which should be about 5 to 20 times the volume of the storage space. As a result, a reliable filling of the storage space and the pump space is achieved.

Die Achsen der speicherraumseitigen Bohrungen zu den Ventilen 10 und 11 sind gegenüber den Steuerbohrungen 7 versetzt, so daß im Brennstoff gegebenenfalls gebildete Hohlräume von dem aus der Steuerbohrung 7 austretenden Strahl rasch weggespült werden können und eine allenfalls auftretende Korrosion von gefährdeten Bereichen ferngehalten wird.The axes of the bores towards the valves 10 and 11 are offset relative to the control bores 7, so that any cavities formed in the fuel can be quickly washed away by the jet emerging from the control bore 7 and any corrosion that may occur is kept away from hazardous areas.

Bei der Ausführung nach Fig.5 liegen Zuführung 19 und Ableitung 20 des Brennstoffes gleichachsig mit den Steuerbohrungen 7, jedoch ist der der Steuerbohrung 7 zugewendeten Bohrung eines jeden der Ventile 10, 11 als Prallschutz eine Prallplatte 21 bzw. 22 vorgeschaltet, deren jede mit der Armatur des zugeordneten Ventils einstückig ausgebildet ist.In the embodiment according to FIG. 5, feed 19 and discharge line 20 of the fuel lie coaxially with the control bores 7, but the bore of each of the valves 10, 11 facing the control bore 7 is connected upstream of a baffle plate 21 or 22, each of which with the Armature of the associated valve is integrally formed.

In einer weiteren Variante nach Fig.6 ist das Saugventil 10 auf beiden Seiten in einen Prallschutz eingebaut, der eine kegelige Form aufweist und weit in die Steuerbohrung 7 hineinragt. Der Brennstoff wird durch eine Bohrung 23 vom Saugventil 10 kommend in den Spalt zwischen dem Kegel 24 des Prallschutzes und der konischen Erweiterung 25 der Steuerbohrung gefördert. Die Bohrung 23 ist dabei derart positioniert, daß sie den Brennstoff am höchstgelegenen Teil des Spaltes austreten läßt, so daß die dort befindlichen Hohlräume im Brennstoff direkt vom Spülstrom getroffen und in den Speicherraum 9 befördert werden. Ein nicht dargestelltes Druckhalteventil sorgt für die Aufrechterhaltung eines erhöhten Standdruckes im Speicherraum 9 nach dem Ende des Zusteuervorganges bis zum Wiederansaugen. Die Brennstoffzuführung erfolgt zweckmäßig mit einem Druck von 5 bis 20 bar, um eine ausreichende Spülwirkung in den Steuerbohrungen 7 zu erzielen. Auch hier erscheint zur Vergleichmäßigung des Zulaufdruckes ein Druckspeicher in der Brennstoffleitung zwischen Förderpumpe und Saugventil 10 zweckmäßig.

Figure imgb0001
In a further variant according to FIG. 6, the suction valve 10 is installed on both sides in an impact protection which has a conical shape and projects far into the control bore 7. The fuel is conveyed through a bore 23 coming from the suction valve 10 into the gap between the cone 24 of the impact protection and the conical extension 25 of the control bore. The bore 23 is positioned in such a way that it allows the fuel to exit at the highest part of the gap, so that the cavities in the fuel are hit directly by the flushing stream and conveyed into the storage space 9. A pressure control valve, not shown, ensures the maintenance of an increased standing pressure in the storage space 9 after the end of the control process until it is sucked in again. The fuel is advantageously supplied at a pressure of 5 to 20 bar, in order to achieve a sufficient flushing effect in the control bores 7. Here, too, a pressure accumulator in the fuel line between the feed pump and suction valve 10 appears to be useful for making the inlet pressure more uniform.
Figure imgb0001

Claims (9)

  1. Injection pump for internal-combustion engines, having a pump piston bush (1) and a pump piston (2) which is guided in the latter and has control edges (6, 12) for controlling the beginning and end of an injection operation, which control edges interact with control bores (7) provided in the wall of the pump piston bush, which control bores open out into an accumulator chamber (9) which surrounds the pump piston bush and into which fuel can be fed under pressure and from which excess fuel, or when ending an injection operation overflowing fuel, can be drained off, a suction valve (10) which opens towards the accumulator chamber (9) being connected to the accumulator chamber (9) for the fuel feeding and a valve (11) which opens away from the accumulator chamber (9) being connected to the accumulator chamber for the fuel draining, characterised in that the valve opening away from the accumulator chamber is designed in such a way that it maintains a pressure of at least 20 bar in the accumulator chamber (9).
  2. Injection pump according to Claim 1, characterised in that the accumulator chamber (9) is connected to the control bores (7) of the pump piston bush (1) concentrically with respect to a suction chamber ( 4 ).
  3. Injection pump according to Claim 2, characterised in that the pressure-maintaining valve (11) opening away from the accumulator chamber (9) and the suction valve (10) opening towards the accumulator chamber (9) are connected on the side remote from the accumulator chamber (9) jointly to the suction chamber (4) supplied with fuel and are formed by non-return valves.
  4. Injection pump according to Claim 1, 2 or 3, characterised in that the pressure-maintaining valve (11) opening away from the accumulator chamber (9) is connected to the accumulator chamber (9) via a throttling point (13), known per se.
  5. Injection pump according to one of Claims 1 to 4, characterised in that the axes of the mouths of the non-return valves (10, 11) on the accumulator chamber side are arranged offset with respect to the axes of the control bores (7).
  6. Injection pump according to one of Claims 1 to 4, characterised in that a baffle guard is arranged at the mouth on the accumulator chamber side of at least one of the non-return valves (10, 11) axially aligned with a control bore (7).
  7. Injection pump according to Claim 6, characterised in that a baffle plate (21, 22), closing the bore, is arranged as baffle guard in front of an axial bore of the non-return valve (10, 11), on the rear side of which baffle plate there is provided a transverse bore which has open ends and intersects the axial bore of the non-return valve.
  8. Injection pump according to Claim 7, characterised in that the baffle plate (21, 22) is designed in one piece with the housing of the non-return valve (10, 11).
  9. Injection pump according to Claim 6, characterised in that the control bore (7) has a section (25) widened frustoconically towards the accumulator chamber (9), in that the housing of the non-return valve (10, 11) opening towards the accumulator chamber (9) has a conical end part (24) which has a rounded-off tip and protrudes into the frustoconically widened section (25), leaving an intermediate space clear, and in that the outlet channel (23) of the non-return valve (10, 11) opens out off-centre in the region of the cone shell of the end part (24).
EP89108890A 1988-06-18 1989-05-18 Injection pump for internal-combustion engines Expired - Lifetime EP0347581B1 (en)

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DE3820707A DE3820707A1 (en) 1988-06-18 1988-06-18 INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE3820707 1988-06-18

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EP0347581B1 true EP0347581B1 (en) 1993-02-03

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US4118156A (en) * 1976-12-01 1978-10-03 Sulzer Brothers Limited Fuel injection pump having choke means in overflow line
US4355961A (en) * 1978-04-03 1982-10-26 Ingersoll-Rand Company Controlling means for a fuel valve
JPS5947359U (en) * 1982-09-22 1984-03-29 株式会社小松製作所 engine fuel injector
DE3245142A1 (en) * 1982-12-07 1984-06-07 Robert Bosch Gmbh, 7000 Stuttgart METHOD AND DEVICE FOR INJECTING FUEL
DE3535808A1 (en) * 1985-10-08 1987-04-09 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101178681B1 (en) 2006-11-06 2012-08-30 미츠비시 쥬고교 가부시키가이샤 Fuel injection pump equipped with rotary deflector

Also Published As

Publication number Publication date
JP2721243B2 (en) 1998-03-04
DE58903432D1 (en) 1993-03-18
EP0347581A1 (en) 1989-12-27
JPH0237166A (en) 1990-02-07
US5015160A (en) 1991-05-14
DE3820707A1 (en) 1989-12-21

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