EP0451227B1 - Fuel injection pump - Google Patents

Fuel injection pump Download PDF

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Publication number
EP0451227B1
EP0451227B1 EP90914055A EP90914055A EP0451227B1 EP 0451227 B1 EP0451227 B1 EP 0451227B1 EP 90914055 A EP90914055 A EP 90914055A EP 90914055 A EP90914055 A EP 90914055A EP 0451227 B1 EP0451227 B1 EP 0451227B1
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EP
European Patent Office
Prior art keywords
pump
closing
valve
fuel injection
suction conduit
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
EP90914055A
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German (de)
French (fr)
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EP0451227A1 (en
Inventor
Heinz Nothdurft
Reinhard Trunk
Kurt Sprenger
Carlos Alvarez-Avila
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0451227A1 publication Critical patent/EP0451227A1/en
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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
    • 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
    • F02M41/10—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 pump pistons acting as the distributor
    • F02M41/12—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 pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—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 pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/125—Variably-timed valves controlling fuel passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0205—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine
    • F02M63/0215—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine by draining or closing fuel conduits

Definitions

  • the invention is based on a fuel injection pump according to the preamble of claim 1.
  • a fuel injection pump known from DE-A1-31 42 750
  • the valve member is acted upon in the closing direction by a stationary supporting spring, so that when the electromagnet of the solenoid valve is fully excited, the closing part and the closing member counter to the force of the weaker closing spring of the valve member and the force of the stronger return spring of the closing part can be adjusted.
  • the weaker closing spring is designed so that it holds the valve member in its position closing the bore in the closing part when the electromagnet is not energized.
  • the valve member can now be brought into the open position against the force of the closing spring by partial excitation of the electromagnet, so that a quantity of fuel defined by the bore flows to the pump workspace of the fuel injection pump for emergency operation.
  • the closing part when it is used for the purpose of interrupting the fuel supply to the pump work space and thus stopping the internal combustion engine by its return spring when the magnet is not energized Is brought closed position, is acted upon by a pressure surge from the pump work space in the course of the remaining delivery stroke of the fuel injection pump and after opening the connection between the suction line and the pump work space.
  • This pressure surge can lead to the closing part being lifted off its seat and that a refilling process of the pump work space can now take place briefly via the suction line.
  • This quantity flowing into the pump work space can continue to be injected during the next delivery stroke of the pump piston, and the purpose of the solenoid valve serving to shut off is therefore not achieved.
  • the internal combustion engine can fail.
  • the solenoid valve according to the invention with the characterizing features of claim 1 has the advantage that an opening of the closing part and thus a correspondingly large fuel flow to the pump work space is prevented, since the pressure surge via the opening valve member, which releases only a small overflow cross section, is reduced.
  • FIG. 1 shows a partial longitudinal section through a fuel injection pump, in which the solenoid valve according to the invention is used
  • FIG. 2 shows a partial section through FIG. 1 along II-II
  • FIG. 3 shows a longitudinal section through the solenoid valve according to the invention in an enlarged view.
  • a cylinder liner 2 is inserted in a housing 1, in the cylinder bore 3 of which a pump piston 4 is set into a reciprocating movement and at the same time rotating movement by a drive and cam drive of the fuel injection pump (not shown) as shown by the arrows in the drawing.
  • the pump piston 4 includes in the cylinder bore 3 at the end a pump working chamber 6 which is supplied with fuel during the suction stroke of the pump piston via longitudinal grooves 8, which serve as filling grooves, which extend from the end face 7 of the pump piston.
  • FIG. 2 which shows a section along line II-II through FIG.
  • the filling grooves 8 are distributed around the circumferential surface of the pump piston at uniform angular intervals. Two grooves are shown in FIG. 2, corresponding to four suction strokes per pump piston revolution for supplying four injection nozzles alternately through this distributor fuel injection pump.
  • one of the filling grooves 8 is connected to a suction line 10 which opens laterally into the cylinder bore 3 and is connected to a pump suction chamber 11 which is enclosed in the housing of the fuel injection pump.
  • the pump suction chamber 11 supplied by a fuel feed pump 12 from a fuel reservoir 14 with fuel, which is preferably under speed-dependent pressure, additionally controlled by a pressure control valve 15, which is parallel to the fuel feed pump 12, which is driven in speed synchronism with the fuel injection pump.
  • the end of the pump piston opposite the pump working chamber 6 protrudes into said pump suction chamber 11 and is connected there to the drive (not shown).
  • An annular slide 17 is slidably arranged on the outer surface of the pump piston, which can be displaced in a known manner by a regulator of known design, not shown here, via a regulator lever 18 and thereby controls the outlet opening of a transverse bore 19 in the pump piston.
  • the transverse bore 19 is connected to a longitudinal channel 20 in the pump piston, which enters axially at the end face 7 of the pump piston and ends as a blind bore.
  • a radial bore 21 branches off from this longitudinal channel and leads to a distributor opening, here a distributor groove 22, on the lateral surface of the pump piston.
  • injection lines 23 branch off from the cylinder bore, each leading to an injection valve 25, for example via a pressure valve.
  • Such injection lines are distributed around the circumference of the cylinder bore 3 according to the number of injection valves to be supplied, in this case four, in that the pump piston performs four delivery strokes per revolution.
  • the latter sucks fuel from the pump suction chamber 11 via the filling groove 8, which is then covered with the suction line, so that the pump working chamber 6 is filled with fuel at the beginning of the following delivery stroke.
  • the ring slide 17 then closes the outlets of the transverse bore 19, so that during the subsequent delivery stroke of the pump piston and after the filling groove in the pump work chamber has been closed again the fuel is brought to high pressure, which is then fed via the longitudinal channel 20 and one of the injection lines 23 to the corresponding fuel injection valve and is injected.
  • the transverse bore emerges from the overlap at a stroke predetermined by the ring slide 17, so that the pump working space is now relieved via the longitudinal bore 20 and the transverse bore 19 to the pump suction space, the delivery pressure of the pump piston falls below the opening pressure of the injection valve and thus the high pressure injection is interrupted.
  • a solenoid valve 27 is also provided in the suction line 10, the closing part 28 of which cooperates with a valve seat 29 designed as a flat seat, on which the closing part 28 engages when the solenoid valve is de-energized by the force of a return spring is coming.
  • the valve seat is located at the transition from a stepped bore part 31 with a small diameter, on the pump work chamber side, to the stepped bore part 30 with a large diameter of a stepped bore, which receives the solenoid valve used from the outside. From the stepped bore part 30 with a large diameter, the suction line 10 leads further to the pump suction chamber 11.
  • the stepped bore part 31 with a small diameter opens into a recess 32 in the cylinder liner 2, from which a suction line piece 33 with a rectangular cross section opens into the cylinder bore 3.
  • the solenoid valve 27 is shown in detail in FIG. 3.
  • a solenoid 39 and a guide sleeve 40 surrounded by it, into which a magnetic core 41 is immersed, are arranged.
  • An armature 42 which is loaded by the return spring 43, is displaceable in the guide sleeve 40.
  • the valve housing 38 is on the side of the solenoid valve facing away from the armature closed by a plastic part 44 through which the power supply line 45 leads to the solenoid 39.
  • the space between the valve housing 38 and the solenoid 39 is filled with a synthetic resin in order to prevent the vibrations transmitted by the internal combustion engine from causing parts of the valve, in particular the electrical connection, to become detached.
  • the core 41 and the armature 42 are conical on the facing end faces in order to obtain a favorable magnetic force transmission for large strokes necessary for the use of the solenoid valve.
  • the armature also serves as a valve part, in which its end projecting out of the guide sleeve 40 into the stepped bore part 30 with a larger diameter is designed as a closing part 28.
  • a hat-shaped cap 47 made of elastic sealing material is vulcanized onto this end of the armature 42, which comes into abutment with its circumferential outer edge 48 on the front side on the valve seat 29 when the armature with the closing part 28 with the solenoid coil de-energized by the force of the return spring 43 in the closed position brought.
  • the armature 42 has a bore 50 which extends through the end face of the cap 47 coaxially to the stepped bore part 31 and which opens out into the receiving bore 53 with a larger diameter via a conical valve seat 52, which can also be spherical.
  • This receiving bore continues with essentially the same diameter until it emerges at the conically shaped end face of the armature opposite the core 41.
  • the return spring 43 is arranged, which is supported on the face on the correspondingly conical core, there on a shoulder, and on the other hand on a sleeve pressed into the receiving bore 53.
  • This sleeve which can also be fixed in the receiving bore in another way, is to be referred to as an intermediate spring plate 55, since a closing spring 57 is supported on the latter on the other side, which, designed as a compression spring, supports it the other end comes to rest on a spring plate 58 which is displaceable within the receiving bore 53.
  • the spring plate has a recess 60 on its end face facing the bore 50, in which a ball 61, which serves as a valve member, is centered. The ball 61, on the other hand, comes to rest in the closed position on the conical valve seat 52 between the receiving bore 53 and the bore 50.
  • the spring plate 58 is advantageously made of plastic and has on the side of the closing spring 57 a pin 63 which projects through a central opening 64 in the intermediate spring plate 55 and is guided there.
  • the intermediate spring plate 55 On its circumference, the intermediate spring plate 55 has recesses 67, so that when the intermediate spring plate or the armature is adjusted, fuel is throttled and the movement cannot flow past the intermediate spring plate.
  • Cross openings 66 branch off from the receiving bore 53, via which the parts of the suction line 10 upstream and downstream of the valve seat 29 are connected when the valve member 61 is lifted off, even when the closing part 28 is in the closed position and via the armature 42 when the closing part 28 is opened the fuel that it displaces can flow off.
  • the small mass of ball 61 and spring plate 58 with a correspondingly dimensioned closing spring allows a very brief low-hysteresis opening and reclosing of the bore 50 or the connection between the suction line parts. This prevents large amounts of fuel from overflowing from the pump work chamber to equalize the pressure, even if the valve member had been brought into the open position due to momentary pressure surges. In any case, it is prevented that the closing part 28 controlling the substantially larger diameter of the stepped bore part 31 is lifted off its seat. This reduces the risk of the internal combustion engine going through. The danger of the internal combustion engine running through exists in particular when the ring slide 17 is displaced in a very high position towards the pump work space and, for. B.
  • the fuel can be injected again during the subsequent pressure stroke, in particular if the pump work space cannot be relieved via the ring slide.
  • the pressure surge can in turn cause the closing portion 28 to open, followed by pressure equalization and a reflow of fuel to the pump work space as previously described.

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

Abstract

In a magnetic valve serving to block a fuel inlet line (10) to supply a pump working chamber of a fuel injection pump with fuel, the closing component (28) has a drilling (50) penetrating from the front which can be closed off by a valve member (61) under the action of a closing spring (57). On the occurrence of pressure surges in the intake line section (31) closed off by the closing member (28) and leading to the pump working chamber, the closing member (28) and the entire cross-section of the intake line section (31) is not opened but only the cross-section of the drilling (50). This drilling is quickly closed again by the low-mass valve member (61) after the surge has passed so that only small quantities of fuel can flow via the drilling (50) to equalise the pressure.

Description

Stand der TechnikState of the art

Die Erfindung geht von einer Kraftstoffeinspritzpumpe nach der Gattung des Patentanspruchs 1 aus. Bei einer solchen, durch die DE-A1-31 42 750 bekannten Kraftstoffeinspritzpumpe ist das Ventilglied, durch eine sich ortsfest abstützende Schließfeder in Schließrichtung beaufschlagt, so daß bei voller Erregung des Elektromagneten des Magnetventils Schließteil und Schließglied entgegen der Kraft der schwächer ausgelegten Schließfeder des Ventilglieds und der Kraft der stärker ausgelegten Rückstellfeder des Schließteils verstellt werden. Die schwächere Schließfeder ist dabei so ausgelegt, daß sie das Ventilglied in seiner die Bohrung im Schließteil verschließenden Stellung bei nicht erregtem Elektromagneten hält. Für einen Notbetrieb kann nun aber durch eine Teilweiseerregung des Elektromagneten das Ventilglied gegen die Kraft der Schließfeder in Offenstellung gebracht werden, so daß dem Pumpenarbeitsraum der Kraftstoffeinspritzpumpe eine durch die Bohrung definierte Kraftstoffmenge für den Notbetrieb zufließt.The invention is based on a fuel injection pump according to the preamble of claim 1. In such a fuel injection pump, known from DE-A1-31 42 750, the valve member is acted upon in the closing direction by a stationary supporting spring, so that when the electromagnet of the solenoid valve is fully excited, the closing part and the closing member counter to the force of the weaker closing spring of the valve member and the force of the stronger return spring of the closing part can be adjusted. The weaker closing spring is designed so that it holds the valve member in its position closing the bore in the closing part when the electromagnet is not energized. For emergency operation, however, the valve member can now be brought into the open position against the force of the closing spring by partial excitation of the electromagnet, so that a quantity of fuel defined by the bore flows to the pump workspace of the fuel injection pump for emergency operation.

Unter bestimmten Voraussetzungen kann es aber bei einem Magnetventil der gattungsgemäßen Art vorkommen, daß das Schließteil, wenn es zum Zwecke der Unterbrechung der Kraftstoffzufuhr zum Pumpenarbeitsraum und damit Stillsetzen der Brennkraftmaschine durch seine Rückstellfeder bei nicht erregtem Magneten in Schließstellung gebracht ist, durch einen Druckstoß aus dem Pumpenarbeitsraum im Laufe des restlichen Förderhubs der Kraftstoffeinspritzpumpe und nach Öffnen der Verbindung zwischen Saugleitung und Pumpenarbeitsraum beaufschlagt wird. Dieser Druckstoß kann dazu führen, daß das Schließteil von seinem Sitz abgehoben wird und daß nun über die Saugleitung kurzzeitig ein Wiederfüllvorgang des Pumpenarbeitsraumes erfolgen kann. Diese dem Pumpenarbeitsraum zufließende Menge kann weiterhin beim nächsten Förderhub des Pumpenkolbens zur Einspritzung gebracht werden, und es ist somit der Zweck des der Abstellung dienenden Magnetventils nicht erreicht. Insbesondere kann bei einem sonstigen Fehler in der Steuerung der Kraftstoffeinspritzpumpe die Brennkraftmaschine durchgehen.Under certain conditions, however, it can happen with a solenoid valve of the generic type that the closing part, when it is used for the purpose of interrupting the fuel supply to the pump work space and thus stopping the internal combustion engine by its return spring when the magnet is not energized Is brought closed position, is acted upon by a pressure surge from the pump work space in the course of the remaining delivery stroke of the fuel injection pump and after opening the connection between the suction line and the pump work space. This pressure surge can lead to the closing part being lifted off its seat and that a refilling process of the pump work space can now take place briefly via the suction line. This quantity flowing into the pump work space can continue to be injected during the next delivery stroke of the pump piston, and the purpose of the solenoid valve serving to shut off is therefore not achieved. In particular, if there is another fault in the control of the fuel injection pump, the internal combustion engine can fail.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Magnetventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß ein Aufstoßen des Schließteils und damit ein entsprechend großer Kraftstofffluß zum Pumpenarbeitsraum hin verhindert wird, da der Druckstoß über das öffnende Ventilglied, das nur einen kleinen Überströmquerschnitt freigibt, abgebaut wird.The solenoid valve according to the invention with the characterizing features of claim 1 has the advantage that an opening of the closing part and thus a correspondingly large fuel flow to the pump work space is prevented, since the pressure surge via the opening valve member, which releases only a small overflow cross section, is reduced.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Hauptanspruch angegebenen Lösung möglich. Insbesondere nach den Augestaltungen nach Anspruch 3 und 4 ergibt sich ein kleines, massearmes Ventilglied, das trägheitsarm wieder in Schließstellung gelangen kann, so daß nur ein minimaler Rückströmeffekt nach dem Aufstoßen des Ventilglieds stattfindet. Damit werden die eingangs genannten Nachteile weitgehendst vermieden.Advantageous further developments and improvements of the solution specified in the main claim are possible through the measures listed in the subclaims. In particular, according to the eye designs according to claims 3 and 4, there is a small, low-mass valve member, which can return to the closed position with low inertia, so that only a minimal backflow effect takes place after the valve member is pushed open. This largely avoids the disadvantages mentioned at the outset.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und wird in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 einen Teillängsschnitt durch eine Kraftstoffeinspritzpumpe, in der das erfindungsgemäße Magnetventil eingesetzt ist, Figur 2 einen Teilschnitt durch Figur 1 entlang II-II und Figur 3 einen Längsschnitt durch das erfindungsgemäße Magnetventil in vergrößerter Darstellung.An embodiment of the invention is shown in the drawing and is explained in more detail in the following description. 1 shows a partial longitudinal section through a fuel injection pump, in which the solenoid valve according to the invention is used, FIG. 2 shows a partial section through FIG. 1 along II-II and FIG. 3 shows a longitudinal section through the solenoid valve according to the invention in an enlarged view.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Bei der in Figur 1 dargestellten Kraftstoffeinspritzpumpe für mehrzylindrige Brennkraftmaschinen ist in einem Gehäuse 1 eine Zylinderbüchse 2 eingesetzt, in deren Zylinderbohrung 3 ein Pumpenkolben 4 durch einen nicht weiter gezeigten Antrieb und Nockenantrieb der Kraftstoffeinspritzpumpe in eine hin- und hergehende Bewegung und zugleich rotierende Bewegung versetzt wird, wie das die Pfeile in der Zeichnung anzeigen. Der Pumpenkolben 4 schließt in der Zylinderbohrung 3 stirnseitig einen Pumpenarbeitsraum 6 ein, der über von der Stirnseite 7 des Pumpenkolbens ausgehende Längsnuten 8, die als Füllnuten dienen, mit Kraftstoff beim Saughub des Pumpenkolbens versorgt wird. Wie der Figur 2 entnehmbar ist, die einen Schnitt gemäß Linie II-II durch die Figur 1 darstellt, sind die Füllnuten 8 in gleichmäßigen Winkelabständen an der Mantelfläche des Pumpenkolbens herum verteilt angeordnet. In Figur 2 sind davon vier Nuten gezeigt entsprechend vier pro Pumpenkolbenumdrehung erfolgenden Saughüben zur Versorgung von hier vier Einspritzdüsen im Wechsel durch diese Verteilerkraftstoffeinspritzpumpe. Während des Saughubs wird jeweils eine der Füllnuten 8 mit einer seitlich in die Zylinderbohrung 3 mündende Saugleitung 10 in Verbindung gebracht, die mit einem Pumpensaugraum 11, der im Gehäuse der Kraftstoffeinspritzpumpe eingeschlossen ist, in Verbindung steht. Der Pumpensaugraum 11 wird durch eine Kraftstofförderpumpe 12 aus einem Kraftstoffvorratsbehälter 14 mit Kraftstoff versorgt, der vorzugsweise unter drehzahlabhängigem Druck steht, zusätzlich gesteuert durch ein Drucksteuerventil 15, das parallel zur Kraftstofförderpumpe 12 liegt, die drehzahlsynchron mit der Kraftstoffeinspritzpumpe angetrieben wird.In the fuel injection pump for multi-cylinder internal combustion engines shown in FIG. 1, a cylinder liner 2 is inserted in a housing 1, in the cylinder bore 3 of which a pump piston 4 is set into a reciprocating movement and at the same time rotating movement by a drive and cam drive of the fuel injection pump (not shown) as shown by the arrows in the drawing. The pump piston 4 includes in the cylinder bore 3 at the end a pump working chamber 6 which is supplied with fuel during the suction stroke of the pump piston via longitudinal grooves 8, which serve as filling grooves, which extend from the end face 7 of the pump piston. As can be seen in FIG. 2, which shows a section along line II-II through FIG. 1, the filling grooves 8 are distributed around the circumferential surface of the pump piston at uniform angular intervals. Two grooves are shown in FIG. 2, corresponding to four suction strokes per pump piston revolution for supplying four injection nozzles alternately through this distributor fuel injection pump. During the suction stroke, one of the filling grooves 8 is connected to a suction line 10 which opens laterally into the cylinder bore 3 and is connected to a pump suction chamber 11 which is enclosed in the housing of the fuel injection pump. The pump suction chamber 11 supplied by a fuel feed pump 12 from a fuel reservoir 14 with fuel, which is preferably under speed-dependent pressure, additionally controlled by a pressure control valve 15, which is parallel to the fuel feed pump 12, which is driven in speed synchronism with the fuel injection pump.

Das dem Pumpenarbeitsraum 6 gegenüberliegende Ende des Pumpenkolbens ragt in den genannten Pumpensaugraum 11 und hat dort Verbindung mit dem nicht gezeigten Antrieb. Innerhalb des Saugraums ist auf der Mantelfläche des Pumpenkolbens ein Ringschieber 17 verschiebbar angeordnet, der durch einen hier nicht gezeigten Regler bekannter Bauart über einen Reglerhebel 18 in bekannter Weise verschiebbar ist und dabei die Austrittsöffnung einer Querbohrung 19 im Pumpenkolben steuert. Die Querbohrung 19 steht mit einem Längskanal 20 im Pumpenkolben in Verbindung, der axial an der Stirnseite 7 des Pumpenkolbens eintritt und als Sackbohrung endet. Von diesem Längskanal zweigt ferner eine Radialbohrung 21 ab, die zu einer Verteileröffnung, hier eine Verteilernut 22, an der Mantelfläche des Pumpenkolbens führt. In Höhe dieser Verteilernut zweigen von der Zylinderbohrung 3 Einspritzleitungen 23 ab, die zum Beispiel über ein Druckventil jeweils zu einem Einspritzventil 25 führen. Solche Einspritzleitungen sind entsprechend der Zahl der zu versorgenden Einspritzventile am Umfang der Zylinderbohrung 3 herum verteilt angeordnet, in diesem Falle vier, indem der Pumpenkolben pro Umdrehung vier Förderhübe durchführt.The end of the pump piston opposite the pump working chamber 6 protrudes into said pump suction chamber 11 and is connected there to the drive (not shown). An annular slide 17 is slidably arranged on the outer surface of the pump piston, which can be displaced in a known manner by a regulator of known design, not shown here, via a regulator lever 18 and thereby controls the outlet opening of a transverse bore 19 in the pump piston. The transverse bore 19 is connected to a longitudinal channel 20 in the pump piston, which enters axially at the end face 7 of the pump piston and ends as a blind bore. A radial bore 21 branches off from this longitudinal channel and leads to a distributor opening, here a distributor groove 22, on the lateral surface of the pump piston. At the level of this distributor groove, 3 injection lines 23 branch off from the cylinder bore, each leading to an injection valve 25, for example via a pressure valve. Such injection lines are distributed around the circumference of the cylinder bore 3 according to the number of injection valves to be supplied, in this case four, in that the pump piston performs four delivery strokes per revolution.

Während der jeweiligen Saughübe des Pumpenkolbens saugt dieser über die dann in Überdeckung mit der Saugleitung gebrachte Füllnut 8 Kraftstoff aus dem Pumpensaugraum 11 an, so daß der Pumpenarbeitsraum 6 beim Beginn des folgenden Förderhubs kraftstoffgefüllt ist. In Laststellung hat dann der Ringschieber 17 die Austritte der Querbohrung 19 verschlossen, so daß beim folgenden Förderhub des Pumpenkolbens und nach Wiederschließen der Füllnut im Pumpenarbeitsraum der Kraftstoff auf Hochdruck gebracht wird, der dann über den Längskanal 20 und eine der Einspritzleitungen 23 dem entsprechenden Kraftstoffeinspritzventil zugeführt wird und zur Einspritzung kommt. Zur Beendigung der Hochdruckeinspritzung taucht zu einem durch den Ringschieber 17 vorgegebenen Hub die Querbohrung aus der Überdeckung aus, so daß der Pumpenarbeitsraum nun über die Längsbohrung 20 und die Querbohrung 19 zum Pumpensaugraum hin entlastet wird, der Förderdruck des Pumpenkolbens den Öffnungsdruck des Einspritzventils unterschreitet und somit die Hochdruckeinspritzung unterbrochen wird.During the respective suction strokes of the pump piston, the latter sucks fuel from the pump suction chamber 11 via the filling groove 8, which is then covered with the suction line, so that the pump working chamber 6 is filled with fuel at the beginning of the following delivery stroke. In the load position, the ring slide 17 then closes the outlets of the transverse bore 19, so that during the subsequent delivery stroke of the pump piston and after the filling groove in the pump work chamber has been closed again the fuel is brought to high pressure, which is then fed via the longitudinal channel 20 and one of the injection lines 23 to the corresponding fuel injection valve and is injected. To end the high-pressure injection, the transverse bore emerges from the overlap at a stroke predetermined by the ring slide 17, so that the pump working space is now relieved via the longitudinal bore 20 and the transverse bore 19 to the pump suction space, the delivery pressure of the pump piston falls below the opening pressure of the injection valve and thus the high pressure injection is interrupted.

Zur Stillsetzung der Brennkraftmaschine bzw. zur Beendigung der Hochdruckeinspritzung ist weiterhin in der Saugleitung 10 ein Magnetventil 27 vorgesehen, dessen Schließteil 28 mit einem als Flachsitz ausgebildeten Ventilsitz 29 zusammenwirkt, auf den das Schließteil 28 beim stromlosen Magneten des Magnetventils durch die Kraft einer Rückstellfeder zur Anlage kommt. Der Ventilsitz befindet sich am Übergang eines Stufenbohrungsteils 31 mit kleinem Durchmesser, pumpenarbeitsraumseitig, zum Stufenbohrungsteil 30 mit großem Durchmesser einer Stufenbohrung, das das von außen eingesetzte Magnetventil aufnimmt. Von dem Stufenbohrungsteil 30 mit großem Durchmesser führt die Saugleitung 10 weiter zum Pumpensaugraum 11. Der Stufenbohrungsteil 31 mit kleinem Durchmesser mündet in eine Ausnehmung 32 in der Zylinderbüchse 2, von der aus ein Saugleitungsstück 33 mit Rechteckquerschnitt in die Zylinderbohrung 3 mündet.To shut down the internal combustion engine or to end the high-pressure injection, a solenoid valve 27 is also provided in the suction line 10, the closing part 28 of which cooperates with a valve seat 29 designed as a flat seat, on which the closing part 28 engages when the solenoid valve is de-energized by the force of a return spring is coming. The valve seat is located at the transition from a stepped bore part 31 with a small diameter, on the pump work chamber side, to the stepped bore part 30 with a large diameter of a stepped bore, which receives the solenoid valve used from the outside. From the stepped bore part 30 with a large diameter, the suction line 10 leads further to the pump suction chamber 11. The stepped bore part 31 with a small diameter opens into a recess 32 in the cylinder liner 2, from which a suction line piece 33 with a rectangular cross section opens into the cylinder bore 3.

Das Magnetventil 27 ist in Figur 3 detailliert dargestellt. Im Gehäuse 38 des Magnetventils sind eine Magnetspule 39 und eine von dieser umgebene Führungshülse 40, in die ein Magnetkern 41 eintaucht, angeordnet. In der Führungshülse 40 ist ein Anker 42 verschiebbar, der durch die Rückstellfeder 43 belastet ist. Auf der dem Anker abgewandten Seite des Magnetventils ist das Ventilgehäuse 38 durch ein Kunststoffteil 44 verschlossen, durch welches die Stromzuleitung 45 zur Magnetspule 39 führt. Der zwischen Ventilgehäuse 38 und Magnetspule 39 bestehende Raum ist mit einem Kunstharz ausgefüllt, um zu verhindern, daß die von der Brennkraftmaschine her übertragenen Erschütterungen ein Loslösen von Teilen des Ventils insbesondere des elektrischen Anschlusses bewirken. Der Kern 41 und der Anker 42 sind auf den sich zugewandten Stirnseiten konisch ausgebildet, um bei großen für den Einsatz des Magnetventils notwendigen Hüben eine günstige Magnetkraftübertragung zu erhalten. Der Anker dient gleichzeitig als Ventilteil, in dem sein aus der Führungshüle 40 heraus in den Stufenbohrungsteil 30 mit größerem Durchmesser ragendes Endes als Schließteil 28 ausgebildet ist. Dazu ist auf diesem Ende des Ankers 42 eine hutförmige Kappe 47 aus elastischem Dichtungsmaterial aufvulkanisiert, die mit ihrer umlaufenden Außenkante 48 an der Stirnseite am Ventilsitz 29 zur Anlage kommt, wenn der Anker mit Schließteil 28 bei stromloser Magnetspule durch die Kraft der Rückstellfeder 43 in Schließstellung gebracht wird.The solenoid valve 27 is shown in detail in FIG. 3. In the housing 38 of the solenoid valve, a solenoid 39 and a guide sleeve 40 surrounded by it, into which a magnetic core 41 is immersed, are arranged. An armature 42, which is loaded by the return spring 43, is displaceable in the guide sleeve 40. The valve housing 38 is on the side of the solenoid valve facing away from the armature closed by a plastic part 44 through which the power supply line 45 leads to the solenoid 39. The space between the valve housing 38 and the solenoid 39 is filled with a synthetic resin in order to prevent the vibrations transmitted by the internal combustion engine from causing parts of the valve, in particular the electrical connection, to become detached. The core 41 and the armature 42 are conical on the facing end faces in order to obtain a favorable magnetic force transmission for large strokes necessary for the use of the solenoid valve. The armature also serves as a valve part, in which its end projecting out of the guide sleeve 40 into the stepped bore part 30 with a larger diameter is designed as a closing part 28. For this purpose, a hat-shaped cap 47 made of elastic sealing material is vulcanized onto this end of the armature 42, which comes into abutment with its circumferential outer edge 48 on the front side on the valve seat 29 when the armature with the closing part 28 with the solenoid coil de-energized by the force of the return spring 43 in the closed position brought.

Der Anker 42 weist eine durch die Stirnseite der Kappe 47 koaxial zum Stufenbohrungsteil 31 hindurchgehende Bohrung 50 auf, die über einen konischen Ventilsitz 52, der auch sphärisch ausgebildet sein kann, in die Aufnahmebohrung 53 mit größerem Durchmesser mündet. Diese Aufnahmebohrung setzt sich mit im wesentlichen gleichen Durchmesser fort bis zum Austritt an der konisch geformten, dem Kern 41 gegenüberliegenden Stirnseite des Ankers. In dieser Aufnahmebohrung ist die Rückstellfeder 43 angeordnet, die sich stirnseitig an dem entsprechend konisch ausgebildeten Kern, dort an einem Absatz abstützt, und andererseits an einer in die Aufnahmebohrung 53 eingepreßte Hülse stützt. Diese Hülse, die auch auf andere Art in der Aufnahmebohrung fixiert werden kann, ist als Zwischenfederteller 55 zu bezeichnen, da sich auf dieser auf der anderen Seite eine Schließfeder 57 abstützt, die, als Druckfeder ausgebildet, an ihrem anderen Ende zur Anlage an einem Federteller 58 kommt, der innerhalb der Aufnahmebohrung 53 verschiebbar ist. Der Federteller weist auf seiner der Bohrung 50 zugewandten Stirnseite eine Ausnehmung 60 auf, in der eine Kugel 61, die als Ventilglied dient, zentriert wird. Die Kugel 61 kommt andererseits in Schließstellung am konischen Ventilsitz 52 zwischen Aufnahmebohrung 53 und Bohrung 50 zur Anlage. Vorteilhaft besteht der Federteller 58 aus Kunststoff und weist auf der Seite der Schließfeder 57 einen Zapfen 63 auf, der durch eine Mittelöffnung 64 im Zwischenfederteller 55 ragt und dort geführt wird. An seinem Umfang weist der Zwischenfederteller 55 Ausnehmungen 67 auf, so daß bei einer Verstellung des Zwischenfedertellers oder des Ankers Kraftstoff ungedrosselt und die Bewegung nicht behindert am Zwischenfederteller vorbeiströmen kann. Von der Aufnahmebohrung 53 zweigen Queröffnungen 66 ab, über die bei abgehobenem Ventilglied 61 die Teile der Saugleitung 10 stromaufwärts und stromabwärts des Ventilsitzes 29 in Verbindung sind, auch wenn das Schließteil 28 in Schließstellung ist und über die beim Öffnen des Schließteils 28 durch den Anker 42 der von diesem verdrängte Kraftstoff abfließen kann.The armature 42 has a bore 50 which extends through the end face of the cap 47 coaxially to the stepped bore part 31 and which opens out into the receiving bore 53 with a larger diameter via a conical valve seat 52, which can also be spherical. This receiving bore continues with essentially the same diameter until it emerges at the conically shaped end face of the armature opposite the core 41. In this receiving bore, the return spring 43 is arranged, which is supported on the face on the correspondingly conical core, there on a shoulder, and on the other hand on a sleeve pressed into the receiving bore 53. This sleeve, which can also be fixed in the receiving bore in another way, is to be referred to as an intermediate spring plate 55, since a closing spring 57 is supported on the latter on the other side, which, designed as a compression spring, supports it the other end comes to rest on a spring plate 58 which is displaceable within the receiving bore 53. The spring plate has a recess 60 on its end face facing the bore 50, in which a ball 61, which serves as a valve member, is centered. The ball 61, on the other hand, comes to rest in the closed position on the conical valve seat 52 between the receiving bore 53 and the bore 50. The spring plate 58 is advantageously made of plastic and has on the side of the closing spring 57 a pin 63 which projects through a central opening 64 in the intermediate spring plate 55 and is guided there. On its circumference, the intermediate spring plate 55 has recesses 67, so that when the intermediate spring plate or the armature is adjusted, fuel is throttled and the movement cannot flow past the intermediate spring plate. Cross openings 66 branch off from the receiving bore 53, via which the parts of the suction line 10 upstream and downstream of the valve seat 29 are connected when the valve member 61 is lifted off, even when the closing part 28 is in the closed position and via the armature 42 when the closing part 28 is opened the fuel that it displaces can flow off.

Die geringe Masse von Kugel 61 und Federteller 58 bei entsprechend dimensionierter Schließfeder erlaubt ein sehr kurzzeitiges hysteresearmes Öffnen und Wiederschließen der Bohrung 50 bzw. der Verbindung zwischen den Saugleitungsteilen. Dadurch wird vermieden, daß größere Mengen Kraftstoff vom Pumpenarbeitsraum zum Druckausgleich überfließen können, selbst wenn aufgrund momentaner Druckstöße das Ventilglied in Öffnungsstellung gebracht worden war. Es wird in jedem Fall verhindert, daß das den wesentlichen größeren Durchmesser des Stufenbohrungsteil 31 steuernde Schließteil 28 von seinem Sitz abgehoben wird. Damit wird die Gefahr des Durchgehens der Brennkraftmaschine vermindert. Die Gefahr des Durchgehens der Brennkraftmaschine besteht insbesondere dann, wenn der Ringschieber 17 in sehr hoher Stellung zum Pumpenarbeitsraum hin verschoben ist und z. B. dort verklemmt ist, so daß die ganze oder die nahezu ganze vom Pumpenkolben förderbare Kraftstoffmenge aus dem Arbeitsraum zur Einspritzung gelangt, weil nur ein sehr kleiner oder kein Resthub mit Entspannung zum Pumpensaugraum hin mehr erfolgt. Weiterhin besteht die Gefahr dann, wenn aufgrund der Spritzverstellung der Förderhub des Pumpenkolbens bezogen auf seine Drehlage spät erfolgt, so daß die Füllnuten 8 bereits im oberen Totpunkt des Pumpenkolbens oder früher die Verbindung zwischen Pumpenarbeitsraum und Saugleitung 10 bzw. 31, 32, 33 herstellen. Dadurch tritt schlagartig in die Ausnehmung 32 und den anschließenden Stufenbohrungsteil mit kleinerem Durchmesser 31 Kraftstoff unter Hochdruck ein, der stoßartig auf das Schließteil 28 wirkt und diesen abzuheben versucht. Aufgrund des Speichervermögens des elastischen Kraftstoffmediums kann deshalb eine relativ hohe Kraftstoffmenge in dem Raum zwischen Zylinderbohrung 3 und Ventilsitz 29 gespeichert werden, insbesondere dann, wenn Unterdrücke wiederum über die Saugleitung 10 bei geöffnetem Schließteil 28 ausgeglichen werden. Diese gespeicherte Menge fließt dem Pumpenarbeitsraum beim folgenden Saughub zu, wobei der Druck des Kraftstoffs in der Ausnehmung 32 und angrenzenden Bereichen 31, 33 sowie im Pumpenarbeitsraum entsprechend abgesenkt wird. Nach Verschließen des Saugleitungsteilstücks 33 durch die Füllnut bleibt im Bereich bis zum Ventilsitz ein Volumen mit relativ niedrigem Druck übrig und ein Großteil des zuvor darin unter Hochdruck gespeicherten Kraftstoffs ist in den Pumpenarbeitsraum gelangt. Aus diesem kann beim nachfolgenden Druckhub der Kraftstoff wieder zur Einspritzung gelangen, insbesondere, wenn der Pumpenarbeitsraum nicht über den Ringschieber entlastbar wird. Am Ende des Förderhubs beim Wiederaufsteuern des Saugleitungsteilstückes 33 bzw. der nachfolgenden Räume kann der Druckstoß wiederum ein Aufstoßen des Schließteils 28 bewirken, gefolgt von einem Druckausgleich und einem Wiederzufließen von Kraftstoff zum Pumpenarbeitsraum wie zuvor beschrieben. Diese Vorgänge werden nun durch die erfindungsgemäße Lösung weitgehenst vermieden. Damit wird ein sicheres Abschalten der Kraftstoffeinspritzung erzielt.The small mass of ball 61 and spring plate 58 with a correspondingly dimensioned closing spring allows a very brief low-hysteresis opening and reclosing of the bore 50 or the connection between the suction line parts. This prevents large amounts of fuel from overflowing from the pump work chamber to equalize the pressure, even if the valve member had been brought into the open position due to momentary pressure surges. In any case, it is prevented that the closing part 28 controlling the substantially larger diameter of the stepped bore part 31 is lifted off its seat. This reduces the risk of the internal combustion engine going through. The danger of the internal combustion engine running through exists in particular when the ring slide 17 is displaced in a very high position towards the pump work space and, for. B. is jammed there, so that all or almost all of the fuel that can be delivered by the pump piston arrives from the working area for injection, because only a very small or no residual stroke with relaxation to the pump suction area occurs. Furthermore, there is the danger if, due to the spray adjustment, the delivery stroke of the pump piston is late in relation to its rotational position, so that the filling grooves 8 already establish the connection between the pump work chamber and the suction line 10 or 31, 32, 33 at the top dead center of the pump piston. As a result, fuel suddenly enters the recess 32 and the subsequent stepped bore part with a smaller diameter 31 under high pressure, which acts abruptly on the closing part 28 and attempts to lift it off. Due to the storage capacity of the elastic fuel medium, a relatively large amount of fuel can therefore be stored in the space between the cylinder bore 3 and the valve seat 29, in particular when negative pressures are again compensated for via the suction line 10 when the closing part 28 is open. This stored quantity flows to the pump work space during the following suction stroke, the pressure of the fuel in the recess 32 and adjacent areas 31, 33 and in the pump work space being reduced accordingly. After the suction line section 33 has been closed by the filling groove, a volume with a relatively low pressure remains in the area up to the valve seat and a large part of the fuel previously stored therein under high pressure has reached the pump work space. From this, the fuel can be injected again during the subsequent pressure stroke, in particular if the pump work space cannot be relieved via the ring slide. At the end of the delivery stroke when the suction line section 33 or the subsequent spaces are opened again, the pressure surge can in turn cause the closing portion 28 to open, followed by pressure equalization and a reflow of fuel to the pump work space as previously described. These processes are largely avoided by the solution according to the invention. This ensures that the fuel injection is switched off safely.

Claims (5)

  1. A fuel injection pump for supplying internal combustion engines, having a pump piston bounding a pump working space, having a suction conduit which connects the pump working space of the fuel injection pump to a fuel supply source, has flow through it in the direction of the pump working space and can be shut off by a magnetic valve during the suction stroke of the pump piston in order to shut off the fuel injection, the magnetic valve having a magnet coil, a magnet core and an armature which acts simultaneously as a valve part of the magnetic valve, which valve part includes a closing part which can be held in the closed position, by a return spring supported on a fixed location, on a valve seat which divides the suction conduit into a suction conduit part leading from the valve seat to the pump working space of the fuel injection pump and a suction conduit part leading from the fuel supply source of the fuel injection pump to the valve seat, and the closing element being acted on, in the closed position, by the pressure present in the suction conduit part leading to the pump working space of the fuel injection pump against the force of the return spring and being able to be brought into the open position by the armature, and the closing part having a hole connecting the two suction conduit parts together, which hole can be closed by a valve element acted on by a closing spring, which valve element is acted on by the pressure in the suction conduit part leading to the pump working space against the force of the closing spring, wherein the closing spring is supported in the closing part and the valve element is opened by pressure pulses which occur in the suction conduit part leading to the pump working space before these pulses are capable of opening the closing part against the force of the return spring.
  2. The magnetic valve as claimed in claim 1, wherein the hole in the closing part is an axial hole which opens via a conical or spherical valve seat into an accommodation hole in which the valve element and the closing spring are arranged, the accommodation hole axially penetrating the closing part and the armature and having a permanently inserted intermediate spring plate which acts, at one end, as the support for the return spring supported on the stationary core of the magnet of the magnetic valve and, at the other end, as the support for the closing spring.
  3. The magnetic valve as claimed in claim 2, wherein the valve element is a ball which is supported on a recess in a spring plate which has, at the other end, a pin which is fed through a central opening of the intermediate spring plate.
  4. The magnetic valve as claimed in claim 3, wherein the spring plate is manufactured from plastic.
  5. The magnetic valve as claimed in one of the claims 2 to 4, wherein the intermediate spring plate is pressed into the accommodation hole, which is connected to the suction conduit via a transverse opening.
EP90914055A 1989-10-20 1990-09-28 Fuel injection pump Expired - Lifetime EP0451227B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE3934953 1989-10-20
DE3934953A DE3934953A1 (en) 1989-10-20 1989-10-20 SOLENOID VALVE, ESPECIALLY FOR FUEL INJECTION PUMPS
PCT/DE1990/000740 WO1991005950A1 (en) 1989-10-20 1990-09-28 Magnetic valve, especially for fuel injection pumps

Publications (2)

Publication Number Publication Date
EP0451227A1 EP0451227A1 (en) 1991-10-16
EP0451227B1 true EP0451227B1 (en) 1994-12-14

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EP90914055A Expired - Lifetime EP0451227B1 (en) 1989-10-20 1990-09-28 Fuel injection pump

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US (1) US5150688A (en)
EP (1) EP0451227B1 (en)
JP (1) JP3145108B2 (en)
DE (2) DE3934953A1 (en)
ES (1) ES2066225T3 (en)
RU (1) RU2018758C1 (en)
WO (1) WO1991005950A1 (en)

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DE3819996A1 (en) * 1988-06-11 1989-12-14 Bosch Gmbh Robert HYDRAULIC CONTROL DEVICE, IN PARTICULAR FOR FUEL INJECTION SYSTEMS OF INTERNAL COMBUSTION ENGINES

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0928893A2 (en) 1998-01-12 1999-07-14 Robert Bosch Gmbh Electromagnetic valve
US6138986A (en) * 1998-01-12 2000-10-31 Robert Bosh Gmbh Solenoid valve for a fuel injection system for a vehicle
US6148796A (en) * 1998-01-12 2000-11-21 Robert Bosch Gmbh Switching magnet for a high pressure pump

Also Published As

Publication number Publication date
WO1991005950A1 (en) 1991-05-02
US5150688A (en) 1992-09-29
EP0451227A1 (en) 1991-10-16
JP3145108B2 (en) 2001-03-12
DE3934953A1 (en) 1991-04-25
JPH04502502A (en) 1992-05-07
ES2066225T3 (en) 1995-03-01
DE59008029D1 (en) 1995-01-26
RU2018758C1 (en) 1994-08-30

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