EP0795083B1 - Fuel injection pump - Google Patents

Fuel injection pump Download PDF

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Publication number
EP0795083B1
EP0795083B1 EP96908019A EP96908019A EP0795083B1 EP 0795083 B1 EP0795083 B1 EP 0795083B1 EP 96908019 A EP96908019 A EP 96908019A EP 96908019 A EP96908019 A EP 96908019A EP 0795083 B1 EP0795083 B1 EP 0795083B1
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EP
European Patent Office
Prior art keywords
pump
diaphragm
drive
fuel
space
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.)
Expired - Lifetime
Application number
EP96908019A
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German (de)
French (fr)
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EP0795083A1 (en
Inventor
Wolfgang Fehlmann
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0795083A1 publication Critical patent/EP0795083A1/en
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Classifications

    • 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
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/14—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons
    • F02M41/1405—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0448—Sealing means, e.g. for shafts or housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F04B1/0456—Cylindrical

Definitions

  • the invention is based on a fuel injection pump, in particular distributor injection pump, for Internal combustion engines, which in the preamble of claim 1 defined genus.
  • Such a fuel injection pump is from the EP 0 633 398 A1 is known.
  • the suction stroke of the pump piston by simultaneous volume change in the suction and Engine room the filling process of the pump work room positively supported.
  • the fuel injection pump according to the invention with the In contrast, features of claim 1 the advantage that by the invention, from a Diaphragm limited vacuum chamber pressure fluctuations in the Engine room due to compression or expansion of the Vacuum chamber can be compensated, whereby cavitation in the Engine room avoided and its filling with lubricating liquid is improved.
  • the Vacuum chamber is integrated in the fuel injection pump and does not require additional space.
  • the membrane preferably on the movable wall is attached to what is a movable Wall made of metal by soldering.
  • This has the advantage that by soldering to connect metal membrane and movable metal wall there is a vacuum between the two interconnected parts when cooling automatically sets.
  • the membrane can harden from the Soldering process can be carried out. A constructive one
  • the structure of the fuel injection pump is not changed required, since only the movable wall must be provided with a membrane.
  • the vacuum chamber of two edges on top of each other, firmly connected shells included the together a membrane box with two effective membrane surfaces form.
  • the vacuum chamber are through the double-sided membrane surfaces the most effective Work surfaces to compensate for pressure fluctuations significantly larger.
  • Fuel injection pump in the type of Radial piston distributor injection pump for Internal combustion engines have a housing 10 therein inserted cylinder liner 11, in which a Distributor 12 rotates in through a drive shaft 13 Direction of arrow 14 is driven.
  • pump cylinders 15 are Pump piston 16 guided axially between which a pump work space 17 is included.
  • the number of Pump cylinder 15 and pump piston 16 depends on the Number of those to be supplied by the fuel injection pump Cylinder or combustion chambers of the internal combustion engine.
  • the Outlet from the distributor 12 as Distribution opening serves in the course of the rotation of the Distributor 12 in succession during the lifting movements of the Pump piston 16 with one of several injection lines 20 connectable in the housing 10 of the Fuel injection pump are provided and to the individual cylinders or combustion chambers and arranged there Lead injection points of the internal combustion engine.
  • the pump pistons 16 are driven by a cam engine 21, arranged in an engine room 22 in the housing 10 is driven to their lifting movement.
  • the engine 21 has a cam ring 23 with a radially inward directed cam track 231 on which during the Rotation of the distributor 12 rollers 24 expire their radial movement via roller tappet 25 onto the pump piston 16 transferred.
  • the cam ring 23 is essentially fixed and can be used to adjust the start of spraying via a Pin 26, which is engaged by an injection piston, in be adjusted in a known manner.
  • the axial channel 18 opens into the front of the distributor 12 a fuel chamber 27 via a channel 28 in the housing 10 with a fuel storage space formed in the housing 10 29 is connected.
  • the confluence of the Axial channel 18 in the fuel chamber 27 is through a Solenoid valve 30 controlled so that the Pump work space 17 with the solenoid valve 30 open of the suction stroke of the pump pistons 16 from the storage space 29 can be supplied with fuel.
  • the solenoid valve 30 At the beginning of Delivery stroke of the pump piston 16 becomes the solenoid valve 30 closed and thus determines the start of injection and also the duration of the pump pistons during the delivery stroke 16
  • High-pressure fuel from the pump work space 17 is conveyed into the injection line 20. Start of injection and injection quantity are thus through the solenoid valve 30 fixed.
  • the storage space 29 is from the engine room 22 through a movable wall 37 separated, the one hand close to the cylindrical inner wall 101 of the housing 10 abuts and on the other hand, tightly with the cylinder liner 11 coaxial therewith connected is. Due to the large pressure difference of the Fuel in the storage space 29 (storage pressure) and the Fuel in the engine room 22 (lubrication pressure) can be on it be dispensed with that the pump piston 16 during its Suction strokes by springs on the roller tappet 25 and Rollers 24 are pressed against the cam track 231; because during the suction stroke of the pump piston 16, the solenoid valve 30 opened and the memory pressure affects the Pump working space 17 delimiting piston area of the Pump piston 16 while in the engine room 22nd projecting end of the pump piston 16 with the same area the lubricating pressure works. Because of this pressure difference the pump pistons 16 to the roller tappets 25 pressed and follow the radially outwards during the suction stroke directed lifting movement of the rollers 24.
  • the moveable Wall 37 gives way due to that in the storage space 29 occurring pressure peaks elastic to the engine room 22 out, whereby on the one hand the rapid pressure reduction in the Pump work space 17 is facilitated and on the other hand in Memory space 29 occurring pressure vibrations damped will.
  • the movable wall 37 is only for Pressure vibrations in the storage space 29 optimally designed and generated by evading to the engine room 22 in turn, pressure fluctuations in the engine room 22.
  • a vacuum chamber 38 arranged by a membrane 39 acted upon by the lubricating pressure is shown in the Engine room 22 .
  • the rigidity of the membrane 39 is designed so that they only with a pressure load that is slightly above the stationary lubrication pressure in the engine room 22 is in Moving towards the reduction of the vacuum chamber 38 can.
  • This design of the membrane 39 is necessary so that the vacuum chamber 38 by the stationary pressure in the engine room 22 does not collapse.
  • the vacuum chamber 38 is on the one hand from the movable wall 37 and on the other hand from the Membrane 39 limited.
  • the movable ones are preferred Wall 37 and the membrane 39 made of metal, and the Membrane 39 is soldered to the movable wall 37.
  • the soldering process can adjust the rigidity of the membrane 39 become, and the vacuum in the vacuum chamber 38 arises automatically after cooling.
  • Pressure fluctuations in Fuel inside the engine room 22 will now be by more or less pressing in the membrane 39 into the vacuum chamber 38 or by bulging the membrane 39 compensated for by increasing the volume of the vacuum chamber 38. This will avoid the dreaded cavitations, and the degree of filling of the engine room 22 is improved, which gives the engine very good lubrication overall 21 is ensured.
  • Fig. 3 is the Vacuum chamber 38 enclosed by two shells 40, 41, the edge on top of each other and firmly connected are.
  • the two shells 40, 41 form a membrane box 42 with two effective membrane surfaces.
  • the membrane box 42 is attached with its edge to the movable wall 37, wherein care is taken that the movable wall 37 facing membrane surface not to the movable wall 37 triggers.
  • the membrane box 42 can also on others Components attached within the engine room 22 will. It is also possible to attach the Membrane can 42 within the engine room 22 through clamping on the edge between two components to make.
  • the invention is not based on the described Embodiment limited. So it can make sense as shown in Fig. 1, a check valve 44 in the Line 34 between the pre-feed pump 31 and the suction chamber 29 to integrate, which is expedient in the Line section after branching line 35 is arranged.
  • a check valve 44 achieved that the pressure in the storage space 29 when opening of the axial channel 18 through the solenoid valve 30 via the set delivery pressure of the feed pump 31 increase can and thus at the beginning of the subsequent Filling process of the pump work space 17 a larger one Druckunte Kunststoff is available, the filling of the Pump work room 17 improved.

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

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Kraftstoffeinspritzpumpe, insbesondere Verteilereinspritzpumpe, für Brennkraftmaschinen, der im Oberbegriff des Anspruchs 1 definierten Gattung.The invention is based on a fuel injection pump, in particular distributor injection pump, for Internal combustion engines, which in the preamble of claim 1 defined genus.

Eine solche Kraftstoffeinspritzpumpe ist aus der EP 0 633 398 A1 bekannt. Die den Speicherraum von dem Triebswerksraum trennende bewegliche Wand, die als Membran oder als Verschiebekolben ausgebildet werden kann, dient dazu, die stoßartige Belastung des Speicherraums durch den zum Ende des einspritzwirksamen Förderhubs in den Speicherraum abgegebenen, zuvor auf Einspritzdruck gebrachten Kraftstoff zu verringern, indem die bewegliche Wand dem Druckstoß gegen den unter niedrigeren Druck stehenden Triebswerksraum nachgibt und die Abströmmenge auffängt. Zugleich wird beim Saughub des Pumpenkolbens durch gleichzeitige Volumenänderung im Saug- und Triebswerksraum der Füllvorgang des Pumpenarbeitsraums positiv unterstützt. Der Druckunterschied im Speicher- und Triebwerksraum, der beim Saughub des Pumpenkolbens auf diesen wirkt, treibt den Pumpenkolben in Saughubrichtung an und läßt eine gesonderte Feder zur Rückführung des Pumpenkolbens nach dem Druck- oder Füllhub aus seiner oberen Totpunktlage in seine untere Totpunktlage überflüssig werden.Such a fuel injection pump is from the EP 0 633 398 A1 is known. Which the storage space of that Moving wall separating the engine room, acting as a membrane or can be designed as a displacement piston to the sudden load on the storage space by the at the end of the injection stroke in the Storage space released, previously on injection pressure brought fuel to decrease by moving Wound the surge against the lower pressure gives way to the stationary engine room and the outflow quantity catches. At the same time during the suction stroke of the pump piston by simultaneous volume change in the suction and Engine room the filling process of the pump work room positively supported. The pressure difference in the storage and Engine room, which during the suction stroke of the pump piston this acts, drives the pump piston in the suction stroke direction and leaves a separate spring for returning the Pump piston after its pressure or filling stroke from its top dead center to its bottom dead center become superfluous.

Aufgrund der großen Druckdifferenz zwischen dem Druck im Speicherraum (Speicherdruck) und dem Druck im Triebwerksraum (Schmierdruck) ist die bewegliche Wand nur für Druckschwankungen im Speicherraum optimal ausgelegt, kann aber Druckschwankungen im Triebwerksraum nicht kompensieren, sondern trägt vielmehr zur Ausbildung von Druckschwingungen im Triebwerksraum bei. Die Folge sind Kavitationen in der schmierfähigen Flüssigkeit, die zu unvollständiger Schmierung des Triebwerks führt.Due to the large pressure difference between the pressure in the Storage space (storage pressure) and the pressure in the Engine room (lubrication pressure) is the movable wall only optimally designed for pressure fluctuations in the storage space, can not but pressure fluctuations in the engine room compensate, but rather contributes to the training of Pressure fluctuations in the engine room. The result is Cavitation in the lubricating fluid leading to incomplete lubrication of the engine.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzpumpe mit den Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, daß durch die erfindungsgemäße, von einer Membran begrenzte Vakuumkammer Druckschwingungen im Triebwerksraum infolge Kompression oder Ausdehnung der Vakuumkammer ausgeglichen werden, wodurch Kavitation im Triebwerksraum vermieden und dessen Füllung mit schmierfähiger Flüssigkeit verbessert wird. Die Vakuumkammer ist in der Kraftstoffeinspritzpumpe integriert und erfordert keinen zusätzlichen Bauraum.The fuel injection pump according to the invention with the In contrast, features of claim 1 the advantage that by the invention, from a Diaphragm limited vacuum chamber pressure fluctuations in the Engine room due to compression or expansion of the Vacuum chamber can be compensated, whereby cavitation in the Engine room avoided and its filling with lubricating liquid is improved. The Vacuum chamber is integrated in the fuel injection pump and does not require additional space.

Durch die in den weiteren Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Anspruch 1 angegebenen Kraftstoffeinspritzpumpe möglich. By the measures listed in the other claims are advantageous developments and improvements in Claim 1 specified fuel injection pump possible.

Gemäß einer bevorzugten Ausführungsform der Erfindung schließt die Membran zusammen mit der beweglichen Wand die Vakuumkammer ein, wobei die Membran bevorzugt an der beweglichen Wand befestig wird, was bei einer beweglichen Wand aus Metall durch Löten erfolgt. Dies hat den Vorteil, daß durch den Lötvorgang zum Verbinden von Metallmembran und beweglicher Metallwand sich ein Vakuum zwischen den beiden miteinander verbundenen Teilen beim Abkühlen automatisch einstellt. Das Härten der Membran kann aus dem Lötvorgang heraus durchgeführt werden. Eine konstruktive Änderung des Aufbaus der Kraftstoffeinspritzpumpe ist nicht erforderlich, da gegenüber den Serienpumpen lediglich die bewegliche Wand mit einer Membran versehen werden muß.According to a preferred embodiment of the invention closes the membrane together with the movable wall Vacuum chamber, the membrane preferably on the movable wall is attached to what is a movable Wall made of metal by soldering. This has the advantage that by soldering to connect metal membrane and movable metal wall there is a vacuum between the two interconnected parts when cooling automatically sets. The membrane can harden from the Soldering process can be carried out. A constructive one The structure of the fuel injection pump is not changed required, since only the movable wall must be provided with a membrane.

Gemäß einer vorteilhaften Ausführungsform der Erfindung ist die Vakuumkammer von zwei randseitig aufeinanderliegenden, fest miteinander verbundenen Schalen eingeschlossen, die zusammen eine Membrandose mit zwei wirksamen Membranflächen bilden. Bei dieser Ausführung der Vakuumkammer sind durch die doppelseitigen Membranflächen die wirksamen Arbeitsflächen zum Ausgleich der Druckschwingungen bedeutend größer.According to an advantageous embodiment of the invention the vacuum chamber of two edges on top of each other, firmly connected shells included the together a membrane box with two effective membrane surfaces form. In this version the vacuum chamber are through the double-sided membrane surfaces the most effective Work surfaces to compensate for pressure fluctuations significantly larger.

Zeichnungdrawing

Die Erfindung ist anhand von in der Zeichnung dargestellten Ausführungsbeispielen in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Fig. 1
einen Längsschnitt einer Kraftstoffeinspritzpumpe, schematisch dargestellt,
Fig. 2 und 3
jeweils eine vergrößerte Darstellung eines Ausschnitts der Kraftstoffeinspritzpumpe in Fig. 1 im Bereich von Saug- und Triebwerksraum.
The invention is explained in more detail in the following description with reference to exemplary embodiments shown in the drawing. Show it:
Fig. 1
2 shows a longitudinal section of a fuel injection pump, shown schematically,
2 and 3
each an enlarged view of a section of the fuel injection pump in Fig. 1 in the area of the suction and engine room.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Die in Fig. 1 im Längsschnitt schematisch dargestellte Kraftstoffeinspritzpumpe in der Bauart einer Radialkolbenverteiler-Einspritzpumpe für Brennkraftmaschinen weist ein Gehäuse 10 mit darin eingesetzter Zylinderbüchse 11 auf, in welcher ein Verteiler 12 rotiert, der durch eine Antriebswelle 13 in Pfeilrichtung 14 angetrieben ist. In radial in den Verteiler 12 eingebrachten Pumpenzylindern 15 sind Pumpenkolben 16 axial verschieblich geführt, zwischen denen ein Pumpenarbeitsraum 17 eingeschlossen ist. Die Anzahl der Pumpenzylinder 15 und Pumpenkolben 16 richtet sich nach der Zahl der von der Kraftstoffeinspritzpumpe zu versorgenden Zylinder oder Brennräume der Brennkraftmaschine. Der Pumpenarbeitsraum 17 ist über einen Axialkanal 18 im Verteiler 12 und über eine von diesem abzweigende Radialbohrung 19, deren Austritt aus dem Verteiler 12 als Verteileröffnung dient, im Laufe der Rotation des Verteilers 12 nacheinander während der Hubbewegungen der Pumpenkolben 16 mit einer von mehreren Einspritzleitungen 20 verbindbar, die im Gehäuse 10 der Kraftstoffeinspritzpumpe vorgesehen sind und zu den einzelnen Zylindern bzw. Brennräumen und dort angeordneten Einspritzstellen der Brennkraftmaschine führen.The schematically shown in Fig. 1 in longitudinal section Fuel injection pump in the type of Radial piston distributor injection pump for Internal combustion engines have a housing 10 therein inserted cylinder liner 11, in which a Distributor 12 rotates in through a drive shaft 13 Direction of arrow 14 is driven. In radial in the Distributor 12 introduced pump cylinders 15 are Pump piston 16 guided axially between which a pump work space 17 is included. The number of Pump cylinder 15 and pump piston 16 depends on the Number of those to be supplied by the fuel injection pump Cylinder or combustion chambers of the internal combustion engine. Of the Pump work space 17 is in the axial channel 18 Distributor 12 and one branching from this Radial bore 19, the outlet from the distributor 12 as Distribution opening serves in the course of the rotation of the Distributor 12 in succession during the lifting movements of the Pump piston 16 with one of several injection lines 20 connectable in the housing 10 of the Fuel injection pump are provided and to the individual cylinders or combustion chambers and arranged there Lead injection points of the internal combustion engine.

Die Pumpenkolben 16 werden von einem Nockentriebwerk 21, das in einem Triebwerksraum 22 im Gehäuse 10 angeordnet ist, zu ihrer Hubbewegung angetrieben. Das Triebwerk 21 weist einen Nockenring 23 mit einer radial einwärts gerichteten Nockenbahn 231 auf, auf welcher während der Drehung des Verteilers 12 Rollen 24 ablaufen, die ihre radiale Bewegung über Rollenstößel 25 auf die Pumpenkolben 16 übertragen. Der Nockenring 23 ist im wesentlichen feststehend und kann zur Spritzbeginnverstellung über einen Zapfen 26, an dem ein Spritzverstellkolben angreift, in bekannter Weise verstellt werden.The pump pistons 16 are driven by a cam engine 21, arranged in an engine room 22 in the housing 10 is driven to their lifting movement. The engine 21 has a cam ring 23 with a radially inward directed cam track 231 on which during the Rotation of the distributor 12 rollers 24 expire their radial movement via roller tappet 25 onto the pump piston 16 transferred. The cam ring 23 is essentially fixed and can be used to adjust the start of spraying via a Pin 26, which is engaged by an injection piston, in be adjusted in a known manner.

Der Axialkanal 18 mündet stirnseitig des Verteilers 12 in einem Kraftstoffraum 27, der über einen Kanal 28 im Gehäuse 10 mit einem im Gehäuse 10 ausgebildeten Kraftstoff-Speicherraum 29 verbunden ist. Die Einmündung des Axialkanals 18 in den Kraftstoffraum 27 wird durch ein Magnetventil 30 gesteuert, derart, daß der Pumpenarbeitsraum 17 bei geöffnetem Magnetventil 30 während des Saughubs der Pumpenkolben 16 aus dem Speicherraum 29 mit Kraftstoff versorgt werden kann. Zu Beginn des Förderhubs der Pumpenkolben 16 wird das Magnetventil 30 geschlossen und bestimmt somit den Einspritzbeginn und auch die Dauer, über die während des Förderhubs der Pumpenkolben 16 Kraftstoff unter Hochdruck aus dem Pumpenarbeitsraum 17 in die Einspritzleitung 20 gefördert wird. Einspritzbeginn und Einspritzmenge werden damit durch das Magnetventil 30 festgelegt.The axial channel 18 opens into the front of the distributor 12 a fuel chamber 27 via a channel 28 in the housing 10 with a fuel storage space formed in the housing 10 29 is connected. The confluence of the Axial channel 18 in the fuel chamber 27 is through a Solenoid valve 30 controlled so that the Pump work space 17 with the solenoid valve 30 open of the suction stroke of the pump pistons 16 from the storage space 29 can be supplied with fuel. At the beginning of Delivery stroke of the pump piston 16 becomes the solenoid valve 30 closed and thus determines the start of injection and also the duration of the pump pistons during the delivery stroke 16 High-pressure fuel from the pump work space 17 is conveyed into the injection line 20. Start of injection and injection quantity are thus through the solenoid valve 30 fixed.

Zur Versorgung des Speicherraums 29 mit Kraftstoff saugt eine Vorförderpumpe 31 über eine Leitung 32 Kraftstoff aus einem Kraftstoffvorratsbehälter 33 an und fördert diesen über eine Leitung 34 in den Speicherraum 29. Von der Leitung 34 zweigt eine Leitung 35 ab, über die Kraftstoff in den Triebwerksraum 22 gelangt. Der Triebwerksraum 22 wird über ein Druckhalteventil 36, das den Druck im Triebwerksraum 22 bestimmt, zum Kraftstoffvorratsbehälter 33 hin entlastet. In der Leitung 35 ist eine Abkoppeldrossel 43 eingesetzt, um zu gewährleisten, daß im Triebwerksraum 22 ein Druck eingestellt werden kann, der wesentlich kleiner ist als der Kraftstoffdruck im Speicherraum 29. Der Kraftstoff im Triebwerksraum 22 wird als Schmierflüssigkeit für das Nockentriebwerk 21 verwendet. Anstelle von Kraftstoff kann auch eine andere schmierfähige Flüssigkeit entlastet werden. Sucks fuel to supply the storage space 29 a feed pump 31 via a line 32 fuel a fuel tank 33 and promotes this via a line 34 into the storage space 29. From the Line 34 branches off a line 35 through which fuel enters the engine room 22. The engine room 22 is a pressure maintaining valve 36, which the pressure in Engine room 22 determined to the fuel tank 33 relieved. In line 35 is one Decoupling throttle 43 used to ensure that in the Engine room 22 a pressure can be set that is significantly lower than the fuel pressure in the Storage space 29. The fuel in the engine room 22 is as a lubricating fluid for the cam engine 21 used. Instead of fuel, another can relieve lubricant liquid.

Der Speicherraum 29 ist vom Triebwerksraum 22 durch eine bewegliche Wand 37 getrennt, die einerseits dicht an der zylindrischen Innenwand 101 des Gehäuses 10 anliegt und andererseits dicht mit der dazu koaxialen Zylinderbüchse 11 verbunden ist. Durch den großen Druckunterschied des Kraftstoffs im Speicherraum 29 (Speicherdruck) und des Kraftstoffs im Triebwerksraum 22 (Schmierdruck) kann darauf verzichtet werden, daß die Pumpenkolben 16 während ihres Saughubs durch Federn über die Rollenstößel 25 und die Rollen 24 an die Nockenbahn 231 angedrückt werden; denn beim Saughub der Pumpenkolben 16 ist das Magnetventil 30 geöffnet und der Speicherdruck wirkt auf die den Pumpenarbeitsraum 17 begrenzende Kolbenfläche der Pumpenkolben 16, während auf die in den Triebwerksraum 22 ragende Stirnseite der Pumpenkolben 16 mit gleicher Fläche der Schmierdruck wirkt. Durch diesen Druckunterschied werden die Pumpenkolben 16 an die Rollenstößel 25 angedrückt und folgen beim Saughub der radial nach außen gerichteten Hubbewegung der Rollen 24.The storage space 29 is from the engine room 22 through a movable wall 37 separated, the one hand close to the cylindrical inner wall 101 of the housing 10 abuts and on the other hand, tightly with the cylinder liner 11 coaxial therewith connected is. Due to the large pressure difference of the Fuel in the storage space 29 (storage pressure) and the Fuel in the engine room 22 (lubrication pressure) can be on it be dispensed with that the pump piston 16 during its Suction strokes by springs on the roller tappet 25 and Rollers 24 are pressed against the cam track 231; because during the suction stroke of the pump piston 16, the solenoid valve 30 opened and the memory pressure affects the Pump working space 17 delimiting piston area of the Pump piston 16 while in the engine room 22nd projecting end of the pump piston 16 with the same area the lubricating pressure works. Because of this pressure difference the pump pistons 16 to the roller tappets 25 pressed and follow the radially outwards during the suction stroke directed lifting movement of the rollers 24.

Beim anschließenden Förderhub der Pumpenkolben 16, bei welchem diese jeweils über die Rollen 24 und die Rollenstößel 25 radial nach innen verschoben werden, wird durch Öffnen des Magnetventils 30 bei Förderende ein Teil des von dem Pumpenkolben 16 geförderten Kraftstoffs statt unter Hochdruck in die Einspritzleitungen 20 über den Kanal 28 in den Speicherraum 29 zurückgefördert. Die bewegliche Wand 37 weicht aufgrund der im Speicherraum 29 dadurch auftretenden Druckspitzen elastisch zum Triebwerksraum 22 hin aus, wodurch einerseits der schnelle Druckabbau im Pumpenarbeitsraum 17 erleichtert wird und andererseits im Speicherraum 29 auftretende Druckschwingungen gedämpft werden. Allerdings ist die bewegliche Wand 37 nur für Druckschwingungen im Speicherraum 29 optimal ausgelegt und erzeugt durch ihr Ausweichen hin zum Triebwerksraum 22 ihrerseits wiederum Druckschwingungen im Triebwerksraum 22. During the subsequent delivery stroke of the pump piston 16, at which these each via the rollers 24 and the Roller tappet 25 are moved radially inwards by opening the solenoid valve 30 at the end of delivery of the fuel delivered by the pump piston 16 instead under high pressure in the injection lines 20 via the channel 28 conveyed back into the storage space 29. The moveable Wall 37 gives way due to that in the storage space 29 occurring pressure peaks elastic to the engine room 22 out, whereby on the one hand the rapid pressure reduction in the Pump work space 17 is facilitated and on the other hand in Memory space 29 occurring pressure vibrations damped will. However, the movable wall 37 is only for Pressure vibrations in the storage space 29 optimally designed and generated by evading to the engine room 22 in turn, pressure fluctuations in the engine room 22.

Die Folge sind Kavitationen im Kraftstoff innerhalb des Triebwerksraums 22 und eine schlechte Füllung des Triebwerksraums 22 durch Kraftstoff, was in extremen Fällen zu einer nicht ausreichenden Schmierung des Triebwerks 21 führt. Im dies zu vermeiden, ist, wie in der vergrößerten Ausschnittdarstellung der Fig. 2 dargestellt ist, in dem Triebwerksraum 22 eine Vakuumkammer 38 angeordnet, die von einer vom Schmierdruck beaufschlagten Membran 39 begrenzt ist. Die Steifigkeit der Membran 39 ist so ausgelegt, daß sie erst bei einer Druckbelastung, die wenig oberhalb des stationären Schmierdrucks im Triebwerksraum 22 liegt, in Richtung Verkleinerung der Vakuumkammer 38 bewegt werden kann. Diese Auslegung der Membran 39 ist erforderlich, damit die Vakuumkammer 38 durch den stationären Druck in der Triebwerksraum 22 nicht zusammenbricht.The result is cavitation in the fuel within the Engine room 22 and poor filling of the Engine room 22 by fuel, which in extreme cases insufficient lubrication of the engine 21 leads. Avoiding this is like in the enlarged 2 is shown in the Engine room 22 a vacuum chamber 38 arranged by a membrane 39 acted upon by the lubricating pressure is. The rigidity of the membrane 39 is designed so that they only with a pressure load that is slightly above the stationary lubrication pressure in the engine room 22 is in Moving towards the reduction of the vacuum chamber 38 can. This design of the membrane 39 is necessary so that the vacuum chamber 38 by the stationary pressure in the engine room 22 does not collapse.

Im Beispiel der Fig. 2 wird die Vakuumkammer 38 einerseits von der beweglichen Wand 37 und andererseits von der Membran 39 begrenzt. Bevorzugt werden dabei die bewegliche Wand 37 und die Membran 39 aus Metall hergestellt, und die Membran 39 wird an der beweglichen Wand 37 angelötet. Beim Lötvorgang kann die Steifigkeit der Membran 39 eingestellt werden, und das Vakuum in der Vakuumkammer 38 stellt sich nach Abkühlen automatisch ein. Druckschwingungen im Kraftstoff innerhalb des Triebwerksraums 22 werden nun durch mehr oder weniger starkes Eindrücken der Membran 39 in die Vakuumkammer 38 oder durch Ausbeulen der Membran 39 unter Volumenvergrößerung der Vakuumkammer 38 kompensiert. Damit werden die gefürchteten Kavitationen vermieden, und der Füllgrad des Triebwerksraums 22 wird verbessert, wodurch insgesamt eine sehr gute Schmierung des Triebwerks 21 sichergestellt wird.In the example in FIG. 2, the vacuum chamber 38 is on the one hand from the movable wall 37 and on the other hand from the Membrane 39 limited. The movable ones are preferred Wall 37 and the membrane 39 made of metal, and the Membrane 39 is soldered to the movable wall 37. At the The soldering process can adjust the rigidity of the membrane 39 become, and the vacuum in the vacuum chamber 38 arises automatically after cooling. Pressure fluctuations in Fuel inside the engine room 22 will now be by more or less pressing in the membrane 39 into the vacuum chamber 38 or by bulging the membrane 39 compensated for by increasing the volume of the vacuum chamber 38. This will avoid the dreaded cavitations, and the degree of filling of the engine room 22 is improved, which gives the engine very good lubrication overall 21 is ensured.

In dem in Fig. 3 dargestellten Ausführungsbeispiel ist die Vakuumkammer 38 von zwei Schalen 40,41 eingeschlossen, die randseitig aufeinanderliegen und fest miteinander verbunden sind. Die beiden Schalen 40,41 bilden eine Membrandose 42 mit zwei wirksamen Membranflächen. Die Membrandose 42 ist mit ihrem Rand an der beweglichen Wand 37 befestigt, wobei darauf geachtet ist, daß die zur beweglichen Wand 37 weisende Membranfläche nicht an die bewegliche Wand 37 anstößt. Die Membrandose 42 kann aber auch an anderen Bauteilen innerhalb des Triebwerksraums 22 befestigt werden. Auch ist es möglich, die Befestigung der Membrandose 42 innerhalb des Triebwerksraums 22 durch randseitiges Einspannen zwischen zwei Bauteilen vorzunehmen.In the embodiment shown in Fig. 3 is the Vacuum chamber 38 enclosed by two shells 40, 41, the edge on top of each other and firmly connected are. The two shells 40, 41 form a membrane box 42 with two effective membrane surfaces. The membrane box 42 is attached with its edge to the movable wall 37, wherein care is taken that the movable wall 37 facing membrane surface not to the movable wall 37 triggers. The membrane box 42 can also on others Components attached within the engine room 22 will. It is also possible to attach the Membrane can 42 within the engine room 22 through clamping on the edge between two components to make.

Die Erfindung ist nicht auf das beschriebene Ausführungsbeispiel beschränkt. So kann es sinnvoll sein, wie in Fig. 1 dargestellt, ein Rückschlagventil 44 in die Leitung 34 zwischen der Vorförderpumpe 31 und dem Saugraum 29 zu integrieren, das zweckmäßigerweise in dem Leitungsabschnitt nach dem Abzweig der Leitung 35 angeordnet ist. Durch dieses Rückschlagventil 44 wird erreicht, daß der Druck im Speicherraum 29 bei Aufsteuern des Axialkanals 18 durch das Magnetventil 30 über den eingestellten Förderdruck der Vorförderpumpe 31 ansteigen kann und dadurch zu Beginn des sich daran anschließenden Füllvorgangs des Pumpenarbeitsraums 17 ein größerer Druckunteschied zur Verfügung steht, der die Füllung des Pumpenarbeitsraums 17 verbessert.The invention is not based on the described Embodiment limited. So it can make sense as shown in Fig. 1, a check valve 44 in the Line 34 between the pre-feed pump 31 and the suction chamber 29 to integrate, which is expedient in the Line section after branching line 35 is arranged. Through this check valve 44 achieved that the pressure in the storage space 29 when opening of the axial channel 18 through the solenoid valve 30 via the set delivery pressure of the feed pump 31 increase can and thus at the beginning of the subsequent Filling process of the pump work space 17 a larger one Druckunteschied is available, the filling of the Pump work room 17 improved.

Claims (7)

  1. Fuel injection pump, especially distributor injection pump, for internal combustion engines, with at least one pump piston (16) guided axially displaceably in a pump cylinder (15) and delimiting a pump working space (17) on the end face, with a drive unit (21) which engages on that end face of the pump piston (16) facing away from the pump working space (17) and which drives the pump piston (16) in the axial direction of the latter for the execution of delivery or feed strokes, with a drive-unit space (22) receiving the drive unit (21) and filled with lubricating fluid, and with a fuel-filled storage space (29) which is separated from the drive-unit space (22) by a movable wall (37) and out of which the pump working space (17) is filled with fuel during the execution of suction strokes of the pump piston (16) and into which a part quantity of the fuel under injection pressure, fed during the feed stroke of the pump piston (16), is discharged at the end of the feed stroke, the fuel pressure in the storage space (29) being substantially higher than the fluid pressure in the drive-unit space (22), characterized in that the drive-unit space (22) has arranged in it a vacuum chamber (38) which is delimited at least partially by a diaphragm (39; 40, 41), on which the fluid pressure in the drive-unit space (22) acts, and in that the rigidity of the diaphragm (39; 40, 41) is designed in such a way that it shifts in relation to the vacuum chamber (38) only under a pressure load which is a little above the stationary fluid pressure in the drive-unit space (22).
  2. Pump according to Claim 1, characterized in that the diaphragm (39), together with the movable wall (37), encloses the vacuum chamber (38), and in that the diaphragm (39) is fastened to the movable wall (37).
  3. Pump according to Claim 2, characterized in that the movable wall (37) and the diaphragm (39) consist of metal, and in that the diaphragm (39) is soldered to the movable wall (37).
  4. Pump according to Claim 1, characterized in that the vacuum chamber (38) is enclosed by two shells (40, 41) which rest one on the other at the edge and are fixedly connected to one another and which together form a diaphragm cell (42) having two effective diaphragm surfaces.
  5. Pump according to Claim 4, characterized in that the diaphragm cell (42) is fastened at the edge to a component of the fuel injection pump.
  6. Pump according to Claim 5, characterized in that the component is the movable wall (37) between the storage space (29) and drive-unit space (22).
  7. Pump according to Claim 4, characterized in that the diaphragm cell (42) is clamped at the edge between two components of the fuel injection pump.
EP96908019A 1995-08-30 1996-03-29 Fuel injection pump Expired - Lifetime EP0795083B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19531811 1995-08-30
DE19531811A DE19531811A1 (en) 1995-08-30 1995-08-30 Fuel injection pump
PCT/DE1996/000612 WO1997008454A1 (en) 1995-08-30 1996-03-29 Fuel injection pump

Publications (2)

Publication Number Publication Date
EP0795083A1 EP0795083A1 (en) 1997-09-17
EP0795083B1 true EP0795083B1 (en) 1998-09-16

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EP96908019A Expired - Lifetime EP0795083B1 (en) 1995-08-30 1996-03-29 Fuel injection pump

Country Status (6)

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US (1) US5794594A (en)
EP (1) EP0795083B1 (en)
JP (1) JPH10508358A (en)
DE (2) DE19531811A1 (en)
RU (1) RU2156881C2 (en)
WO (1) WO1997008454A1 (en)

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JP3471587B2 (en) * 1997-10-27 2003-12-02 三菱電機株式会社 High pressure fuel pump for in-cylinder injection
JPH11132130A (en) * 1997-10-27 1999-05-18 Mitsubishi Electric Corp Cylinder injection type high pressure fuel pump
DE10362411B3 (en) * 2002-10-19 2017-09-07 Robert Bosch Gmbh Device for damping pressure pulsations in a fluid system, in particular in a fuel system of an internal combustion engine
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JP4036153B2 (en) * 2003-07-22 2008-01-23 株式会社日立製作所 Damper mechanism and high-pressure fuel supply pump
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JP4686501B2 (en) * 2007-05-21 2011-05-25 日立オートモティブシステムズ株式会社 Liquid pulsation damper mechanism and high-pressure fuel supply pump having liquid pulsation damper mechanism
DE102008043643A1 (en) * 2007-11-29 2009-06-04 Robert Bosch Gmbh Fuel injection system for an internal combustion engine with HC injector
JP5002523B2 (en) 2008-04-25 2012-08-15 日立オートモティブシステムズ株式会社 Fuel pressure pulsation reduction mechanism and high-pressure fuel supply pump for internal combustion engine equipped with the same
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Also Published As

Publication number Publication date
DE59600567D1 (en) 1998-10-22
WO1997008454A1 (en) 1997-03-06
JPH10508358A (en) 1998-08-18
US5794594A (en) 1998-08-18
RU2156881C2 (en) 2000-09-27
EP0795083A1 (en) 1997-09-17
DE19531811A1 (en) 1997-03-06

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