EP0290797B1 - Fuel injection pump - Google Patents

Fuel injection pump Download PDF

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Publication number
EP0290797B1
EP0290797B1 EP88105775A EP88105775A EP0290797B1 EP 0290797 B1 EP0290797 B1 EP 0290797B1 EP 88105775 A EP88105775 A EP 88105775A EP 88105775 A EP88105775 A EP 88105775A EP 0290797 B1 EP0290797 B1 EP 0290797B1
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EP
European Patent Office
Prior art keywords
fuel injection
pump
valve
space
piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP88105775A
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German (de)
French (fr)
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EP0290797A3 (en
EP0290797A2 (en
Inventor
Anton Dipl.-Ing. Karle
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP0290797A3 publication Critical patent/EP0290797A3/en
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Publication of EP0290797B1 publication Critical patent/EP0290797B1/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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/06—Pumps peculiar thereto

Definitions

  • the invention is based on a fuel injection pump according to the preamble of the main claim.
  • the controlling member is designed as a cylindrical evasive piston which is tightly guided in a cylinder bore open to the pump work space.
  • the spring chamber which always remains separate from the pump work chamber, is opened when the internal combustion engine is idling through an electrically pneumatically actuated valve to the relief line, so that the evasive piston can be adjusted by a path determined by a stop through the pressure prevailing in the pump work chamber when pumping the piston. This reduces the delivery rate of the pump piston when the engine is idling, but never stops the fuel injection. Such devices serve to make the combustion process softer in fuel injection pumps with low speeds.
  • the relief line of the spring chamber is either permanently open when idling, or permanently closed at partial load or full load.
  • a fuel injection pump of the generic type is known from EP-A2 0 116 168.
  • the relief space is delimited by the controlling member in the form of a piston, which at the same time represents a sliding wall for changing the volume of the relief space.
  • the controlling member is moved against the force of a first and a second spring, both by one in one Cylinder bore tightly guided spring plate are separated.
  • the position of this spring plate and thus the resetting characteristic of the spring arrangement is determined by a control pressure which is introduced into the space receiving the spring directly acting on the controlling member.
  • the controlling member is thus moved against this control pressure and also against the spring clamped in this space.
  • the control pressure is changed in one embodiment by a pressure-dependent pressure of the pressure source and in the other case by clocked relief of the spring-receiving space, which is now decoupled from the pressure source by means of a throttle.
  • the pressure curve of the high-pressure delivery stroke of the fuel injection pump is to be subdivided into a pre-injection and a main injection, with the aid of the removal space and the controlled member, the injection pause between the pre-injection and the main injection and thus the amount of the fuel pre-injection is controlled.
  • the control pressure can be changed as a function of speed, temperature and load, so that depending on these parameters, a differently large extraction volume per delivery stroke of the pump piston is provided.
  • the high-pressure delivery phase of the pump piston is controlled independently of the control of the relief space by controlling a separate relief channel of the pump work space.
  • the point of use of the main injection or the end of the pre-injection depends on the dynamic behavior of the controlling member and the spring arrangement loading it in connection with the controlling control pressure. At different speeds, there may be deviations in the control times between the pilot injection quantity and the main injection quantity.
  • a fuel injection pump is also known, in which the fuel injection quantity takes place with the aid of a servo valve.
  • the relief line of the pump work space is again controlled to control the fuel injection quantity by means of a flat seat valve which consists of a piston which can be displaced in a cylinder and which opens the connection of the relief line to a relief space from a certain displacement path.
  • this piston encloses a volume which can also be connected to the relief chamber by means of a second relief line which is controlled by a solenoid valve.
  • the solenoid valve is closed, the volume behind the piston is locked in and prevents the piston from evading and thus opening of the relief line when the pump piston delivery stroke begins.
  • US-A-4 590 908 discloses a fuel injection pump in which the pump work space can also be connected to a relief space via a relief line controlled by a servo valve in order to control the fuel injection quantity.
  • the servo valve also consists here, as in the foregoing, of a piston sliding in a cylinder, the front edge of which, after lifting off a flat valve seat, opens the connection of the relief line to the relief chamber.
  • the piston is held in the closed position by a spring, which is on the pump working space attacks the rear of the piston.
  • This back of the piston in turn encloses in the cylinder receiving the piston a pressure chamber which can be relieved via a second relief line which is controlled by a solenoid valve.
  • the pump work space is constantly connected to the rear of the piston via a throttle connection.
  • this pressure is also effective on the rear of the piston when the pump working chamber pressure rises, so that the piston can be held in the closed position by the return spring without great difficulty. If the space on the back of the piston is relieved via the second relief line when the solenoid valve is opened, more fuel flows out there than can flow in via the throttle, so that the pump working chamber pressure brings the piston into the open position against the spring.
  • This servo valve arrangement is provided in the known fuel injection pump for controlling the start of injection and the end of injection.
  • the start of injection in the course of the delivery stroke of the pump piston is controlled by closing the solenoid valve, the return spring bringing the piston into the closed position, which is then held as a result of the pump working space pressure which continues to rise and is also effective in the rear space of the piston.
  • the solenoid valve opens, the fuel injection is ended, which also determines the fuel injection quantity. A pre-injection is not provided in this known pump.
  • the fuel injection pump according to the invention has the advantage that a pre-injection is possible in the entire speed-load range and the distance pre-injection to main injection can be set variably.
  • only one control device is required when using a plurality of injection nozzles.
  • the control device can work with a single pressure valve or a constant pressure valve and is constructed in such a way that the pump piston drive is also prevented from jumping off the drive cam.
  • FIG. 1 An embodiment of the invention is shown in the drawing and is explained in the following description.
  • the figure shows a partial section through a fuel injection pump.
  • the figure shows a part of a known distributor injection pump schematically in section.
  • the figure discloses a pump piston 1, which slides in a cylinder 9 and is set in a reciprocating, pumping and rotating movement by a cam drive, not shown.
  • the pump piston 1 delimits a pump work space 2.
  • This pump work space 2 is filled via filling grooves 14 which come into contact with a suction line 5 during the suction stroke of the pump piston 1.
  • the suction line 5 branches off from a suction space 6 which is filled with fuel which is subjected to speed-dependent pressure.
  • the pump piston 1 of this fuel injection pump acts as a distributor during operation, fuel being conveyed from the pump working chamber 2 via an injection line 12 to the injection valve 41 via a longitudinal or distributor bore 48 in the pump piston 1.
  • a relief line 4 leads away from the pump work space 2 and cooperates with a valve closing element 7 which controls the relief line 4.
  • This valve closing member 7 is part of a pressure valve 50 and has a valve cone 35 on the underside, which cooperates with a valve seat 32 attached to the relief line 4.
  • This valve closing member 7 slides back and forth with guide ribs 51 on its shaft in a cylinder 43 surrounding the pressure valve 50.
  • this valve closing member 7 is provided with longitudinal grooves 52, which begin at the valve cone 35.
  • the valve closing member 7 is acted upon by a return spring 8.
  • the return spring 8 is placed in a relief chamber 10 under tension so that it presses the closing member 7 onto the valve seat 32.
  • the return spring 8 is accommodated in the cylindrical space, in the relief space 10, from which a second relief line 22 with a valve seat 15 leads away.
  • This valve seat 15 acts with a valve closing member 18 of an electrically controlled valve, here a solenoid valve 11 together.
  • the valve closing member 18 is designed as an armature of the solenoid valve with a conical tip 44, which has a sealing surface 45, and comes to rest on the valve seat 15 of the second relief line 22.
  • a return line 16 leads from the relief chamber 10 to the suction chamber 6 via the valve seat 15 and the second relief line 22.
  • a spring 46 which cooperates with a part 47 connected to the armature, ensures that the armature of the solenoid valve 11 lifts off the valve seat 15 in the de-energized, non-activated state.
  • valve closing member 7 Only when the pressure in the pump work chamber 2 increases further is the force of the return spring 8 of the valve closing member 7 overcome, and now the fuel can pass through the longitudinal grooves 52 of the valve closing member 7 to the relief chamber 10, the second relief line 22, which is open in the uncontrolled state, and the return line 16 flow to the suction space 6. With the opening process, the valve closing member 7 is suddenly loaded on a larger area by the pressure of the pump work space and quickly brought into the fully open position. With this backflow of the fuel into the suction chamber 6, the pressure in the pump working chamber 2 is reduced again, so that the pressure drops below the level that was present at the beginning in order to push the valve needle 54 away from the valve seat 55 and that led to the pre-injection.
  • the solenoid valve 11 When the injection valve 41 is closed, the solenoid valve 11 is actuated at the same time, as a result of which the valve seat 45 on the armature 18 presses onto the valve seat 15 and closes the second relief line 22 Cam drive takes place, the above-mentioned pressurized parts are pressurized, and the valve closing member 7 is brought back into the closed position by the return spring 8.
  • the fuel that continues to be delivered can now only flow to the injection valve 41 via the longitudinal bore 48 in the pump piston 1, the distributor groove 30, the delivery line 12. Therefore, the valve needle 54 of the injection valve 41 lifts off the valve seat 55 and the main injection occurs.
  • the duration is determined by the time in which the solenoid valve 11 remains closed. If the solenoid valve 11 opens, the back of the valve closing member 7 is suddenly relieved and the valve closing member is opened immediately due to the high pressure in the pump work space, so that the pump work space is relieved and the injection is ended.
  • valve closing member 7 Another alternative embodiment is shown in dashed lines in the figure.
  • a through hole 56 is made, into which a pressure spring-loaded ball valve 57 is introduced on one side, through which the relief chamber 10 can flow.
  • no feed line 5 from the suction chamber 6 to the pump work chamber 2 is required.
  • a line with a ball valve leading around the valve closing element 7 could also be installed.
  • the fuel could get from the suction chamber 6 via the return line 16, the second relief line 22, the through bore 56, the ball valve 57, the first relief bore 4 into the pump work chamber 2.
  • the fuel injection pump according to the invention can also be operated without pre-injection if the solenoid valve 11 remains closed from the beginning.
  • the pump piston 2 is moved upward, so that the fuel entering the pump work chamber 2 via a feed line 5 and a filling groove 14 begins to compress and the pressure in the pump work chamber 2 increases.
  • the increase in pressure opens the injection valve 41.
  • the valve closing member 7 is closed and the solenoid valve 11 is closed.
  • the rotation of the cam continues, the pump piston 1 moves upward, compresses more and injects until the solenoid valve 11 opens.
  • the pressure in the pump work chamber 2 is reduced via the return line 16 and the injection valve 41 closes. A new cycle can begin.

Description

Stand der TechnikState of the art

Die Erfindung geht von einer Kraftstoffeinspritzpumpe nach der Gattung des Hauptanspruches aus. Bei einer durch die US-A 44 49 504 bekannten Kraftstoffeinspritzpumpe ist das steuernde Glied als zylindrischer Ausweichkolben ausgebildet, der in einer zum Pumpenarbeitsraum offenen Zylinderbohrung dicht geführt ist. Der vom Pumpenarbeitsraum immer getrennt bleibende Federraum wird bei Leerlaufbetrieb der Brennkraftmaschine durch ein elektrisch pneumatisch betätigtes Ventil zur Entlastungsleitung hin geöffnet, so daß der Ausweichkolben um einen durch einen Anschlag bestimmten Weg durch den im Pumpenarbeitsraum bei der Pumpenkolbenförderung herrschenden Druck verstellt werden kann. Damit wird bei Leerlaufbetrieb die Förderrate des Pumpenkolbens reduziert, nie jedoch die Kraftstoffeinspritzung unterbrochen. Solche Einrichtungen dienen dazu, bei Kraftstoffeinspritzpumpen mit niederen Drehzahlen den Verbrennungsablauf weicher zu gestalten. Dabei ist die Entlastungsleitung des Federraumes entweder ständig geöffnet, bei Leerlaufbetrieb, oder ständig geschlossen bei Teillast oder Vollastbetrieb.The invention is based on a fuel injection pump according to the preamble of the main claim. In a fuel injection pump known from US-A 44 49 504, the controlling member is designed as a cylindrical evasive piston which is tightly guided in a cylinder bore open to the pump work space. The spring chamber, which always remains separate from the pump work chamber, is opened when the internal combustion engine is idling through an electrically pneumatically actuated valve to the relief line, so that the evasive piston can be adjusted by a path determined by a stop through the pressure prevailing in the pump work chamber when pumping the piston. This reduces the delivery rate of the pump piston when the engine is idling, but never stops the fuel injection. Such devices serve to make the combustion process softer in fuel injection pumps with low speeds. The relief line of the spring chamber is either permanently open when idling, or permanently closed at partial load or full load.

Eine Kraftstoffeinspritzpumpe der gattungsgemäßen Art ist durch die EP-A2 0 116 168 bekannt. Dort wird der Entlastungsraum durch das steuernde Glied in Form eines Kolbens begrenzt, der zugleich eine verschiebbare Wand zur Veränderung des Entlastungsraumvolumens darstellt. Das steuernde Glied wird dabei gegen die Kraft einer ersten und einer zweiten Feder verschoben, die beide durch einen in einer Zylinderbohrung dicht geführten Federteller getrennt sind. Die Lage dieses Federtellers und damit die Rückstellcharakteristik der Federanordnung wird dabei durch einen Steuerdruck bestimmt, der in dem das steuernde Glied unmittelbar beaufschlagenden Feder aufnehmenden Raum eingeleitet wird. Das steuernde Glied wird somit gegen diesen Steuerdruck und auch gegen die in diesem Raum eingespannte Feder verschoben. Eine Änderung des Steuerdruckes erfolgt in der einen Ausführung durch einen drehzahlabhängig gesteuerten Druck der Druckquelle und im anderen Falle durch getaktete Entlastung des die Feder aufnehmenden Raumes, der nun mittels einer Drossel gegenüber der Druckquelle abgekoppelt ist. Mit einer solchen Einrichtung soll der Druckverlauf des Hochdruckförderhubes der Kraftstoffeinspritzpumpe in eine Vor- und eine Haupteinspritzung unterteilt werden, wobei mit Hilfe des Entnahmeraumes und des gesteuerten Gliedes die Spritzpause zwischen VOr- und Haupteinspritzung gesteuert wird und somit die Menge der Kraftstoffvoreinspritzung. Bei der Ausführungsform mit einem getaktet angesteuerten Magnetventil kann dabei der Steuerdruck sowohl drehzahl- als auch temperatur- und lastabhängig verändert werden, so daß in Abhängigkeit dieser Parameter ein unterschiedlich großes Entnahmevolumen pro Förderhub des Pumpenkolbens bereitgestellt wird. Bei dieser bekannten Einrichtung wird die Hochdruckförderphase des Pumpenkolbens unabhängig von der Steuerung des Entlastungsraumes durch Steuerung eines separaten Entlastungskanals des Pumpenarbeitsraumes gesteuert. Der Einsatzpunkt der Haupteinspritzung bzw. das Ende der Voreinspritzung hängt dabei von dem dynamischen Verhalten des steuernden Gliedes und der dieses belastenden Federanordnung ab in Verbindung mit den steuernden Steuerdruck. Hier kann es bei verschiedenen Drehzahlen zu Abweichungen der Steuerzeiten von Voreinspritzmenge und Haupteinspritzmenge kommen.A fuel injection pump of the generic type is known from EP-A2 0 116 168. There, the relief space is delimited by the controlling member in the form of a piston, which at the same time represents a sliding wall for changing the volume of the relief space. The controlling member is moved against the force of a first and a second spring, both by one in one Cylinder bore tightly guided spring plate are separated. The position of this spring plate and thus the resetting characteristic of the spring arrangement is determined by a control pressure which is introduced into the space receiving the spring directly acting on the controlling member. The controlling member is thus moved against this control pressure and also against the spring clamped in this space. The control pressure is changed in one embodiment by a pressure-dependent pressure of the pressure source and in the other case by clocked relief of the spring-receiving space, which is now decoupled from the pressure source by means of a throttle. With such a device, the pressure curve of the high-pressure delivery stroke of the fuel injection pump is to be subdivided into a pre-injection and a main injection, with the aid of the removal space and the controlled member, the injection pause between the pre-injection and the main injection and thus the amount of the fuel pre-injection is controlled. In the embodiment with a clocked solenoid valve, the control pressure can be changed as a function of speed, temperature and load, so that depending on these parameters, a differently large extraction volume per delivery stroke of the pump piston is provided. In this known device, the high-pressure delivery phase of the pump piston is controlled independently of the control of the relief space by controlling a separate relief channel of the pump work space. The point of use of the main injection or the end of the pre-injection depends on the dynamic behavior of the controlling member and the spring arrangement loading it in connection with the controlling control pressure. At different speeds, there may be deviations in the control times between the pilot injection quantity and the main injection quantity.

Durch die US-A-4 549 749 ist ferner eine Kraftstoffeinspritzpumpe bekannt, bei der die Kraftstoffeinspritzmenge mit Hilfe eines Servoventils erfolgt. Die Entlastungsleitung des Pumpenarbeitsraumes wird wieder zur Steuerung der Kraftstoffeinspritzmenge mit Hilfe eines Flachsitzventils gesteuert, das aus einem in einem Zylinder verschiebbaren Kolben besteht, der ab einem bestimmten Verschiebeweg die Verbindung der Entlastungsleitung zu einem Entlastungsraum aufsteuert. Dieser Kolben schließt auf einer Rückseite ein Volumen ein, das durch eine zweite Entlastungsleitung, die über ein Magnetventil gesteuert wird, ebenfalls mit dem Entlastungsraum verbindbar ist. Bei geschlossenem Magnetventil wird somit hinter dem Kolben das Volumen eingesperrt und verhindert eine Ausweichbewegung des Kolbens und damit ein Öffnen der Entlastungsleitung bei beginnendem Pumpenkolbenförderhub. Erst wenn das Magnetventil öffnet, weicht der Kolben aus und öffnet dabei schlagartig die Entlastungsleitung des Pumpenarbeitsraumes. Damit wird das Ende der Kraftstoffhochdruckeinspritzung gesteuert. Mit dieser Einrichtung ist es jedoch nicht möglich, pro Pumpenkolbenförderhub eine unterteilte Kraftstoffeinspritzung zu bewirken, da, wenn der Kolben die Entlastungsleitung geöffnet hat, ein Wiederschließen des Magnetventils den Kolben nicht wieder in seine Schließlage zurückbringt, so daß der Pumpenarbeitsraum weiterhin entlastet bleibt.From US-A-4 549 749 a fuel injection pump is also known, in which the fuel injection quantity takes place with the aid of a servo valve. The relief line of the pump work space is again controlled to control the fuel injection quantity by means of a flat seat valve which consists of a piston which can be displaced in a cylinder and which opens the connection of the relief line to a relief space from a certain displacement path. On the rear side, this piston encloses a volume which can also be connected to the relief chamber by means of a second relief line which is controlled by a solenoid valve. When the solenoid valve is closed, the volume behind the piston is locked in and prevents the piston from evading and thus opening of the relief line when the pump piston delivery stroke begins. Only when the solenoid valve opens does the piston evade and suddenly open the relief line of the pump work space. This controls the end of high-pressure fuel injection. With this device, however, it is not possible to effect a divided fuel injection per pump piston delivery stroke, since when the piston has opened the relief line, reclosing the solenoid valve does not bring the piston back into its closed position, so that the pump working space remains relieved.

Durch die US-A-4 590 908 ist schließlich eine Kraftstoffeinspritzpumpe bekannt, bei der ebenfalls zur Steuerung der Kraftstoffeinspritzmenge der Pumpenarbeitsraum über eine von einem Servoventil gesteuerte Entlastungsleitung mit einem Entlastungsraum verbindbar ist. Das Servoventil besteht auch hier wie im vorstehenden aus einem in einem Zylinder gleitenden Kolben, der mit seiner Stirnkante nach Abheben von einem Flachventilsitz die Verbindung der Entlastungsleitung zum Entlastungsraum aufsteuert. Der Kolben wird dabei von einer Feder in Schließstellung gehalten, die auf der dem Pumpenarbeitsraum abgewandten Rückseite des Kolbens angreift. Diese Rückseite des Kolbens schließt wiederum in dem den Kolben aufnehmenden Zylinder einen Druckraum ein, der über eine zweite Entlastungsleitung, die durch ein Magnetventil gesteuert wird, entlastbar ist. Dabei ist jedoch der Pumpenarbeitsraum mit der Rückseite des Kolbens ständig über eine Drosselverbindung verbunden. Auf diese Weise wird bei steigendem Pumpenarbeitsraumdruck dieser Druck auch auf der Rückseite des Kolbens wirksam, so daß ohne große Schwierigkeiten der Kolben durch die Rückstellfeder in Schließstellung gehalten werden kann. Wird der auf der Rückseite des Kolbens befindliche Raum über die zweite Entlastungsleitung bei Öffnen des Magnetventils entlastet, so fließt dort mehr Kraftstoff ab, als über die Drossel zufließen kann, so daß der Pumpenarbeitsraumdruck den Kolben gegen die Feder in öffnungsstellung bringt. Diese Servoventilanordnung ist bei der bekannen Kraftstoffeinspritzpumpe zur Steuerung des Einspritzbeginns und des Einspritzendes vorgesehen. Der Einspritzbeginn im Laufe des Förderhubes des Pumpenkolbens wird dabei durch Schließen des Magnetventils gesteuert, wobei die Rückstellfeder den Kolben in Schließstellung bringt und dieser dann infolge durch den weiterhin ansteigenden und auch in rückwärtigen Raum des Kolbens wirksamen Pumpenarbeitsraumdruck gehalten wird. Mit öffnen des Magnetventils erfolgt eine Beendigung der Kraftstoffeinspritzung, womit auch die Kraftstoffeinspritzmenge bestimmt wird. Eine Voreinspritzung ist bei dieser bekannten Pumpe nicht vorgesehen.Finally, US-A-4 590 908 discloses a fuel injection pump in which the pump work space can also be connected to a relief space via a relief line controlled by a servo valve in order to control the fuel injection quantity. The servo valve also consists here, as in the foregoing, of a piston sliding in a cylinder, the front edge of which, after lifting off a flat valve seat, opens the connection of the relief line to the relief chamber. The piston is held in the closed position by a spring, which is on the pump working space attacks the rear of the piston. This back of the piston in turn encloses in the cylinder receiving the piston a pressure chamber which can be relieved via a second relief line which is controlled by a solenoid valve. In this case, however, the pump work space is constantly connected to the rear of the piston via a throttle connection. In this way, this pressure is also effective on the rear of the piston when the pump working chamber pressure rises, so that the piston can be held in the closed position by the return spring without great difficulty. If the space on the back of the piston is relieved via the second relief line when the solenoid valve is opened, more fuel flows out there than can flow in via the throttle, so that the pump working chamber pressure brings the piston into the open position against the spring. This servo valve arrangement is provided in the known fuel injection pump for controlling the start of injection and the end of injection. The start of injection in the course of the delivery stroke of the pump piston is controlled by closing the solenoid valve, the return spring bringing the piston into the closed position, which is then held as a result of the pump working space pressure which continues to rise and is also effective in the rear space of the piston. When the solenoid valve opens, the fuel injection is ended, which also determines the fuel injection quantity. A pre-injection is not provided in this known pump.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzpumpe hat den Vorteil, daß eine Voreinspritzung im gesamten Drehzahl-Lastbereich möglich ist und der Abstand Voreinspritzung zu Haupteinspritzung variabel eingestellt werden kann. Es ist bei Kraftstoffeinspritzpumpen der erfindungsgemäßen Art nur eine Steuereinrichtung beim Einsatz mehrerer Einspritzdüsen erforderlich. Die Steuereinrichtung kann mit Einzeldruckventil oder Gleichdruckventil arbeiten und ist so aufgebaut, daß außerdem ein Abspringen des Pumpenkolbenantriebes von dem Antriebsnocken verhindert wird.The fuel injection pump according to the invention has the advantage that a pre-injection is possible in the entire speed-load range and the distance pre-injection to main injection can be set variably. In fuel injection pumps of the type according to the invention, only one control device is required when using a plurality of injection nozzles. The control device can work with a single pressure valve or a constant pressure valve and is constructed in such a way that the pump piston drive is also prevented from jumping off the drive cam.

Durch die in den übrigen Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen der erfindungsgemäßen Kraftstoffeinspritzpumpe gegeben. Sie werden anhand eines Ausführungsbeispieles mit seinen Vorteilen in der nachfolgenden Beschreibung erläutet.The measures listed in the remaining subclaims provide advantageous developments of the fuel injection pump according to the invention. They are explained with the aid of an exemplary embodiment with its advantages in the following description.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und wird in der nachfolgenden Beschreibung erläutert. Es zeigt die Figur einen Teilschnitt durch eine Kraftstoffeinspritzpumpe.An embodiment of the invention is shown in the drawing and is explained in the following description. The figure shows a partial section through a fuel injection pump.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Die Figur zeigt einen Teil einer an sich bekannten Verteilereinspritzpumpe schematisch im Schnitt. Die Figur offenbart einen Pumpenkolben 1, der in einem Zylinder 9 gleitet und von einem nicht dargestellten Nockenantrieb in eine hin- und hergehende, pumpende und in eine rotierende Bewegung versetzt wird. Der Pumpenkolben 1 begrenzt einen Pumpenarbeitsraum 2. Gefüllt wird dieser Pumpenarbeitsraum 2 über Füllnuten 14, die beim Saughub des Pumpenkolbens 1 im Wechsel mit einer Saugleitung 5 in Verbindung kommen. Die Saugleitung 5 zweigt von einem Saugraum 6 ab, der mit drehzahlabhängigem Druck beaufschlagten Kraftstoff gefüllt ist. In bekannter Weise wirkt der Pumpenkolben 1 dieser Kraftstoffeinspritzpumpe, während des Betriebes als Verteiler, wobei über eine Längs- oder Verteilerbohrung 48 im Pumpenkolben 1 Kraftstoff aus dem Pumpenarbeitsraum 2 über eine Einspritzleitung 12 zum Einspritzventil 41 gefördert wird. Vom Pumpenarbeitsraum 2 führt eine Entlastungsleitung 4 weg, die mit einem die Entlastungsleitung 4 steuernden Ventilschließglied 7 zusammenarbeitet. Dieses Ventilschließglied 7 ist Teil eines Druckventils 50 und weist an der Unterseite einen Ventilkegel 35 auf, der mit einem an der Entlastungsleitung 4 angebrachten Ventilsitz 32 zusammenwirkt. Dieses Ventilschließglied 7 gleitet mit Führungsrippen 51 an seinen Schaft in einem das Druckventil 50 umgebenden Zylinder 43 hin- und her. Am Umfang ist dieses Ventilschließglied 7 mit Längsnuten 52 versehen, die am Ventilkegel 35 beginnen. Auf der dem Ventilkegel 35 gegenüberliegenden Seite wird das Ventilschließglied 7 mit einer Rückstellfeder 8 beaufschlagt. Die Rückstellfeder 8 ist in einem Entlastungsraum 10 so unter Spannung eingebracht, daß sie das Schließglied 7 auf den Ventilsitz 32 preßt. Die Rückstellfeder 8 ist in dem zylindrischen Raum, im Entlastungsraum 10 untergebracht, von dem aus eine zweite Entlastungsleitung 22 mit einem Ventilsitz 15 weg führt. Dieser Ventilsitz 15 wirkt mit einem Ventilschließglied 18 eines elektrisch gesteuerten Ventils, hier ein Magnetventil 11 zusammen. Das Ventilschließglied 18 ist als Anker des Magnetventils ausgebildet mit einer kegelförmigen Spitze 44, die eine Dichtfläche 45 hat, und zur Anlage auf den Ventilsitz 15 der zweiten Entlastungsleitung 22 kommt. Vom Entlastungsraum 10 führt über den Ventilsitz 15 und die zweite Entlastungsleitung 22 eine Rücklaufleitung 16 zum Saugraum 6 zurück. Daß der Anker des Magnetventils 11 im stromlosen, nicht angesteuerten Zustand vom Ventilsitz 15 abhebt, dafür sorgt eine Feder 46, die mit einem mit dem Anker verbundenen Teil 47 zusammenwirkt.The figure shows a part of a known distributor injection pump schematically in section. The figure discloses a pump piston 1, which slides in a cylinder 9 and is set in a reciprocating, pumping and rotating movement by a cam drive, not shown. The pump piston 1 delimits a pump work space 2. This pump work space 2 is filled via filling grooves 14 which come into contact with a suction line 5 during the suction stroke of the pump piston 1. The suction line 5 branches off from a suction space 6 which is filled with fuel which is subjected to speed-dependent pressure. In a known manner, the pump piston 1 of this fuel injection pump acts as a distributor during operation, fuel being conveyed from the pump working chamber 2 via an injection line 12 to the injection valve 41 via a longitudinal or distributor bore 48 in the pump piston 1. A relief line 4 leads away from the pump work space 2 and cooperates with a valve closing element 7 which controls the relief line 4. This valve closing member 7 is part of a pressure valve 50 and has a valve cone 35 on the underside, which cooperates with a valve seat 32 attached to the relief line 4. This valve closing member 7 slides back and forth with guide ribs 51 on its shaft in a cylinder 43 surrounding the pressure valve 50. On the circumference, this valve closing member 7 is provided with longitudinal grooves 52, which begin at the valve cone 35. On the side opposite the valve cone 35, the valve closing member 7 is acted upon by a return spring 8. The return spring 8 is placed in a relief chamber 10 under tension so that it presses the closing member 7 onto the valve seat 32. The return spring 8 is accommodated in the cylindrical space, in the relief space 10, from which a second relief line 22 with a valve seat 15 leads away. This valve seat 15 acts with a valve closing member 18 of an electrically controlled valve, here a solenoid valve 11 together. The valve closing member 18 is designed as an armature of the solenoid valve with a conical tip 44, which has a sealing surface 45, and comes to rest on the valve seat 15 of the second relief line 22. A return line 16 leads from the relief chamber 10 to the suction chamber 6 via the valve seat 15 and the second relief line 22. A spring 46, which cooperates with a part 47 connected to the armature, ensures that the armature of the solenoid valve 11 lifts off the valve seat 15 in the de-energized, non-activated state.

Im Betrieb arbeiten die oben beschriebenen Organe folgendermaßen:
Wird der Pumpenkolben 1 durch den Nockenantrieb nach unten bewegt, so wird dadurch Kraftstoff über die Zuleitung 5 und die Füllnuten 14 in den Pumpenarbeitsraum gefördert. Beim anschließenden Förderhub des Pumpenkolbens baut sich im Pumpenarbeitsraum 2, in der Längsbohrung 48 des Pumpenkolbens 1, der ersten Entlastungsleitung 4, der Verteilernut 30, der Förderleitung 12 und an der mit einer Druckfeder 53 belasteten Ventilnadel 54 des Einspritzventils 41 ein Druck auf, bis ein Druck erreicht ist, der die Ventilnadel 54 gegen die Kraft der Feder 53 vom Ventilsitz 55 abhebt, so daß eine Einspritzung erfolgt. Erst bei weiterem Druckanstieg im Pumpenarbeitsraum 2 wird die Kraft der Rückstellfeder 8 des Ventilschließgliedes 7 überwunden, nun kann der Kraftstoff über die Längsnuten 52 des Ventilschließgliedes 7 dem Entlastungsraum 10, der zweiten Entlastungsleitung 22, die im nicht angesteuerten Zustand geöffnet ist, und die Rücklaufleitung 16 zu dem Saugraum 6 fließen. Mit dem Öffnungsvorgang wird das Ventilschließglied 7 plötzlich auf einer größeren Fläche vom Druck des Pumpenarbeitsraumes belastet und schnell in ganz geöffnete Stellung gebracht. Mit diesem Zurückfließen des Kraftstoffes in den Saugraum 6 wird der Druck im Pumpenarbeitsraum 2 wieder abgebaut, so daß der Druck unter das Niveau fällt, das anfangs vorhanden war, um die Ventilnadel 54 vom Ventilsitz 55 wegzudrücken und das zu der Voreinspritzung führte. Während des Schließens des Einspritzventils 41 der wird zeitgleich das Magnetventil 11 angesteuert, dadurch drückt der am Anker 18 vorhandene Ventilsitz 45 sich auf den Ventilsitz 15 und verschließt die zweite Entlastungsleitung 22. Durch den nunmehr wiederum ansteigenden Druck im Pumpenarbeitsraum 2, der durch weitere Drehung des Nockensantriebs erfolgt, werden die obig bereits erwähnten druckbeaufschlagten Teile mit Druck beaufschlagt, und das Ventilschließglied 7 wieder durch die Rückstellfeder 8 in Schließstellung gebracht. Der nun weiterhin geförderte Kraftstoff kann nun nur noch über die Längsbohrung 48 im Pumpenkolben 1, der Verteilernut 30, der Förderleitung 12 zum Einspritzventil 41 abfließen. Daher hebt sich die Ventilnadel 54 des Einspritzventils 41 vom Ventilsitz 55 ab und es kommt zu der Haupteinspritzung. Die Dauer wird bestimmt durch die Zeit in der das Magnetventil 11 geschlossen bleibt. Öffnet das Magnetventil 11, so wird die Rückseite des Ventilschließgliedes 7 schlagartig entlastet und das Ventilschließglied aufgrund des hohen Drucks im Pumpenarbeitsraum unmittelbar geöffnet, so daß der Pumpenarbeitsraum entlastet wird und die Einspritzung beendet wird.The organs described above work as follows:
If the pump piston 1 is moved downward by the cam drive, fuel is thereby conveyed into the pump work space via the feed line 5 and the filling grooves 14. During the subsequent delivery stroke of the pump piston, a pressure builds up in the pump work chamber 2, in the longitudinal bore 48 of the pump piston 1, the first relief line 4, the distributor groove 30, the delivery line 12 and on the valve needle 54 of the injection valve 41 loaded with a compression spring 53 until a Pressure is reached, which lifts the valve needle 54 against the force of the spring 53 from the valve seat 55, so that an injection takes place. Only when the pressure in the pump work chamber 2 increases further is the force of the return spring 8 of the valve closing member 7 overcome, and now the fuel can pass through the longitudinal grooves 52 of the valve closing member 7 to the relief chamber 10, the second relief line 22, which is open in the uncontrolled state, and the return line 16 flow to the suction space 6. With the opening process, the valve closing member 7 is suddenly loaded on a larger area by the pressure of the pump work space and quickly brought into the fully open position. With this backflow of the fuel into the suction chamber 6, the pressure in the pump working chamber 2 is reduced again, so that the pressure drops below the level that was present at the beginning in order to push the valve needle 54 away from the valve seat 55 and that led to the pre-injection. When the injection valve 41 is closed, the solenoid valve 11 is actuated at the same time, as a result of which the valve seat 45 on the armature 18 presses onto the valve seat 15 and closes the second relief line 22 Cam drive takes place, the above-mentioned pressurized parts are pressurized, and the valve closing member 7 is brought back into the closed position by the return spring 8. The fuel that continues to be delivered can now only flow to the injection valve 41 via the longitudinal bore 48 in the pump piston 1, the distributor groove 30, the delivery line 12. Therefore, the valve needle 54 of the injection valve 41 lifts off the valve seat 55 and the main injection occurs. The duration is determined by the time in which the solenoid valve 11 remains closed. If the solenoid valve 11 opens, the back of the valve closing member 7 is suddenly relieved and the valve closing member is opened immediately due to the high pressure in the pump work space, so that the pump work space is relieved and the injection is ended.

Eine weitere alternative Ausführung ist in der Figur gestrichelt eingezeichnet. Im Ventilschließglied 7 ist eine Durchgangsbohrung 56 eingebracht, in die ein einseitig, vom Entlastungsraum 10 durchströmbar, druckfederbelastetes Kugelventil 57 eingebracht ist. Bei dieser Ausführungsform ist keine Zuleitung 5 vom Saugraum 6 zum Pumpenarbeitsraum 2 erforderlich. Statt das Kugelventil 57 in das Ventilschließglied 7 einzubringen, könnte auch eine um das Ventilschließglied 7 führende Leitung mit einem Kugelventil eingebaut werden.Another alternative embodiment is shown in dashed lines in the figure. In the valve closing member 7, a through hole 56 is made, into which a pressure spring-loaded ball valve 57 is introduced on one side, through which the relief chamber 10 can flow. In this embodiment, no feed line 5 from the suction chamber 6 to the pump work chamber 2 is required. Instead of introducing the ball valve 57 into the valve closing element 7, a line with a ball valve leading around the valve closing element 7 could also be installed.

Durch die zuvor erläuterten Einrichtungen könnte der Kraftstoff vom Saugraum 6 über die Rücklaufleitung 16, die zweite Entlastungsleitung 22, die Durchgangsbohrung 56, das Kugelventil 57, die erste Entlastungsbohrung 4 in den Pumpenarbeitsraum 2 gelangen.By means of the devices explained above, the fuel could get from the suction chamber 6 via the return line 16, the second relief line 22, the through bore 56, the ball valve 57, the first relief bore 4 into the pump work chamber 2.

Eine weitere mögliche Alternative besteht darin, daß mittels eines zweistufigen Magnetventils die Abstimmung mit dem Ventilschließglied 7 in der Weise erfolgen kann, daß nach dem Öffnen des Ventilschließgliedes 7 die erste Stufe des Magnetventils geöffnet wird und der Druck nicht vollständig abbaut wird, sondern der Druck kurze Zeit in bestimmter Höhe gehalten wird, um dann mit der zweiten Stufe zur Beendigung der Haupteinspritzung den Druck vollständig abzubauen.Another possible alternative is that by means of a two-stage solenoid valve, the coordination with the valve closing member 7 can take place in such a way that after opening the valve closing member 7, the first stage of the solenoid valve is opened and the pressure is not completely reduced, but the pressure is short Time is held at a certain level, in order to then release the pressure completely with the second stage to complete the main injection.

Im übrigen kann die erfindungsgemäße Kraftstoffeinspritzpumpe auch ohne Voreinspritzung betrieben werden, wenn das Magnetventil 11 von Anfang an geschlossen bleibt. Bei beginnender Nockendrehung wird der Pumpenkolben 2 nach oben bewegt, so daß sich der sich über eine Zuleitung 5 und eine Füllnut 14 in den Pumpenarbeitsraum 2 gelangende Kraftstoff zu verdichten beginnt und sich der Druck im Pumpenarbeitsraum 2 erhöht. Die Erhöhung des Drucks öffnet das Einspritzventil 41. Das Ventilschließglied 7 ist geschlossen und das Magnetventil 11 ist geschlossen. Die Drehung des Nockens geht weiter, der Pumpenkolben 1 bewegt sich weiter nach oben, verdichtet mehr und spritzt so lange ein bis das Magnetventil 11 öffnet. Über die Rücklaufleitung 16 wird der Druck im Pumpenarbeitsraum 2 abgebaut, das Einspritzventil 41 schließt. Ein neuer Zyklus kann beginnen.Otherwise, the fuel injection pump according to the invention can also be operated without pre-injection if the solenoid valve 11 remains closed from the beginning. At the beginning of the cam rotation, the pump piston 2 is moved upward, so that the fuel entering the pump work chamber 2 via a feed line 5 and a filling groove 14 begins to compress and the pressure in the pump work chamber 2 increases. The increase in pressure opens the injection valve 41. The valve closing member 7 is closed and the solenoid valve 11 is closed. The rotation of the cam continues, the pump piston 1 moves upward, compresses more and injects until the solenoid valve 11 opens. The pressure in the pump work chamber 2 is reduced via the return line 16 and the injection valve 41 closes. A new cycle can begin.

Claims (6)

  1. Fuel injection pump for internal combustion engines having at least one pump piston (1) and a pump working space (2) which is delimited by the latter and which can be connected to a fuel injection valve (41) via a fuel injection line (12) during the delivery stroke of the pump piston (1) and via a first relief line (4) controlled by a controlling member (7) to a relief space (10), the controlling member (7) being loaded in the opening direction by the pressure in the pump working space on an area which is smaller in the closed position of the member than in the open position of the member in opposition to the force of a restoring spring (8) which is arranged in a spring space (10) which can be relieved via a second relief line (22) which contains an electrically controlled valve, characterised in that the spring space (10), in the closed position of the member (7), is a space which can only be relieved via the second relief line (22) and is otherwise closed and, in the open position of the member (7), the spring space (10) is connected via overflow cross sections (52) to the first relief line (4), the opening pressure of the controlling member (7) being higher than the opening pressure of the injection valve (41) when the second relief line (22) is open.
  2. Fuel injection pump according to Claim 1, characterised in that the spring space (10) can be connected to the first relief line (4) via a return valve (57) opening in the direction of the pump working space (2).
  3. Fuel injection pump according to Claim 1 or 2, characterised in that the member (7) is loaded with a restoring spring (8) which can be adjusted in dependence on operating characteristics of the internal combustion engine.
  4. Fuel injection pump according to one of the preceding claims, characterised in that the flow cross section of the second relief line (22) can be changed in steps by the electrically controlled valve in the course of a fuel injection process.
  5. Fuel injection pump according to one of the preceding claims, characterised in that the electrically controlled valve is opened in a first working area of the fuel injection pump for controlling a fuel preinjection volume at the beginning of the delivery stroke of the pump piston, is closed for controlling the beginning of the main injection from a particular pump piston delivery stroke and is opened again for ending the fuel injection and in that in a second working area the electrically controlled valve (11) is closed at the beginning of the delivery stroke of the pump piston and is opened for ending the fuel injection.
  6. Fuel injection pump according to one of the preceding claims, characterised in that the fuel injection pump is constructed as a distributor injection pump.
EP88105775A 1987-05-11 1988-04-12 Fuel injection pump Expired - Lifetime EP0290797B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19873715614 DE3715614A1 (en) 1987-05-11 1987-05-11 FUEL INJECTION PUMP
DE3715614 1987-05-11

Publications (3)

Publication Number Publication Date
EP0290797A2 EP0290797A2 (en) 1988-11-17
EP0290797A3 EP0290797A3 (en) 1989-10-18
EP0290797B1 true EP0290797B1 (en) 1992-04-01

Family

ID=6327245

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88105775A Expired - Lifetime EP0290797B1 (en) 1987-05-11 1988-04-12 Fuel injection pump

Country Status (4)

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US (1) US4840155A (en)
EP (1) EP0290797B1 (en)
JP (1) JPS63295854A (en)
DE (2) DE3715614A1 (en)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3722264A1 (en) * 1987-07-06 1989-01-19 Bosch Gmbh Robert FUEL INJECTION SYSTEM FOR INTERNAL COMBUSTION ENGINES
DE3819996A1 (en) * 1988-06-11 1989-12-14 Bosch Gmbh Robert HYDRAULIC CONTROL DEVICE, IN PARTICULAR FOR FUEL INJECTION SYSTEMS OF INTERNAL COMBUSTION ENGINES
US5033443A (en) * 1988-06-27 1991-07-23 Nippondenso Co., Ltd. Pilot injection device for fuel injection pump
DE3929747A1 (en) * 1989-09-07 1991-03-14 Bosch Gmbh Robert METHOD AND DEVICE FOR CONTROLLING FUEL INJECTION
DE3934953A1 (en) * 1989-10-20 1991-04-25 Bosch Gmbh Robert SOLENOID VALVE, ESPECIALLY FOR FUEL INJECTION PUMPS
FR2678025A1 (en) * 1991-06-21 1992-12-24 Bosch Gmbh Robert METHOD AND DEVICE FOR CONTROLLING A FUEL FILLING SYSTEM CONTROLLED BY A SOLENOID VALVE, IN PARTICULAR FOR AN INTERNAL COMBUSTION DIESEL ENGINE.
GB9203636D0 (en) * 1992-02-19 1992-04-08 Lucas Ind Plc Fuel pumping apparatus
GB9322850D0 (en) * 1993-11-05 1993-12-22 Lucas Ind Plc Control valve
US5873527A (en) * 1997-02-19 1999-02-23 Caterpillar Inc. Fuel injector with regulated plunger motion
US5979415A (en) * 1997-11-12 1999-11-09 Caterpillar Inc. Fuel injection pump with a hydraulically-spill valve
US6102004A (en) * 1997-12-19 2000-08-15 Caterpillar, Inc. Electronic control for a hydraulically activated, electronically controlled injector fuel system and method for operating same
JP2000186649A (en) * 1998-12-24 2000-07-04 Isuzu Motors Ltd Variable discharge quantity control type high pressure fuel pump
US6347614B1 (en) 1999-07-23 2002-02-19 Lawrence W. Evers Mechanical fuel injection system
US6824081B2 (en) 2002-06-28 2004-11-30 Cummins Inc. Needle controlled fuel injector with two control valves
JP6222623B2 (en) * 2015-12-24 2017-11-01 マツダ株式会社 Fuel injection control method and fuel injection control device for compression self-ignition engine
DE102018206334A1 (en) * 2018-04-25 2019-10-31 Robert Bosch Gmbh Fuel delivery device for cryogenic fuels
CN117738826B (en) * 2024-02-19 2024-05-03 江苏中奕和创智能科技有限公司 Diesel generator with oil control assembly

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3211877A1 (en) * 1982-03-31 1983-10-06 Bosch Gmbh Robert FUEL INJECTION PUMP
JPS58149566U (en) * 1982-03-31 1983-10-07 株式会社デンソー distribution type fuel injection pump
JPS5951139A (en) * 1982-09-17 1984-03-24 Nippon Soken Inc Fuel supply device
DE3245142A1 (en) * 1982-12-07 1984-06-07 Robert Bosch Gmbh, 7000 Stuttgart METHOD AND DEVICE FOR INJECTING FUEL
DE3300876A1 (en) * 1983-01-13 1984-07-19 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION PUMP
JPS6098146A (en) * 1983-11-02 1985-06-01 Nippon Soken Inc Fuel control method of internal-combustion engine
DE3629751C2 (en) * 1986-09-01 1998-07-02 Bosch Gmbh Robert Pre-injection device for internal combustion engines

Also Published As

Publication number Publication date
US4840155A (en) 1989-06-20
DE3869652D1 (en) 1992-05-07
JPS63295854A (en) 1988-12-02
DE3715614A1 (en) 1988-11-24
EP0290797A3 (en) 1989-10-18
EP0290797A2 (en) 1988-11-17

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