EP0840009B1 - High pressure pump - Google Patents

High pressure pump Download PDF

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Publication number
EP0840009B1
EP0840009B1 EP97110986A EP97110986A EP0840009B1 EP 0840009 B1 EP0840009 B1 EP 0840009B1 EP 97110986 A EP97110986 A EP 97110986A EP 97110986 A EP97110986 A EP 97110986A EP 0840009 B1 EP0840009 B1 EP 0840009B1
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EP
European Patent Office
Prior art keywords
pressure
valve
pump
low
pressure pump
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
EP97110986A
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German (de)
French (fr)
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EP0840009A2 (en
EP0840009A3 (en
Inventor
Manfred Kraemer
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0840009A3 publication Critical patent/EP0840009A3/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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/464—Inlet valves of the check valve type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • 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
    • F02M59/367—Pump inlet valves of the check valve type being open when actuated
    • 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
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing
    • F04B49/243—Bypassing by keeping open the inlet valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/0076—Piston machines or pumps characterised by having positively-driven valving the members being actuated by electro-magnetic means

Definitions

  • the invention relates to a high pressure pump according to the Genus of the main claim.
  • a high pressure pump is known (EP 0 481 964 A2).
  • Such high pressure pumps are used for fuel injection Diesel engines used. You are between a low pressure tank and a high-pressure accumulator (rail) arranged and ensure that there is sufficient fuel in the high-pressure accumulator Amount and under sufficient high pressure available stands to control the working cylinders via injectors to supply the internal combustion engine with fuel.
  • FIG. 1 shows a first embodiment of the High pressure pump in the suction stroke
  • Figure 2 after the high pressure pump 1 before the start of delivery
  • 3 the high pressure pump according to FIG. 1 after the start of funding
  • FIG. 4 another embodiment the high pressure pump
  • Figure 5 shows a second variant the high pressure pump.
  • a high pressure pump 1 is used as a diesel injection pump and is for filling a high pressure accumulator 2 (also Rail called) determined.
  • a high pressure accumulator 2 also Rail called
  • Injectors not shown, connected via which in a manner not shown, the working cylinder an internal combustion engine with precisely measured quantities powered by diesel fuel.
  • the high-pressure pump 1 has a pump piston 3, which has a Tappet, not shown, in a pump cylinder 4 and is movable here and that as a movable wall is a working chamber 5 of the high pressure pump 1 limited.
  • a high pressure line 6 leads from the working chamber 5 to the high pressure accumulator 2; in it is an opening to the high pressure accumulator 2 Check valve 7 used.
  • a solenoid valve 9 is used so that it is designed as a ball Closing body 10 against the force of a valve spring 11 alone from the suction pressure in the inlet line 8 from its valve seat 12 can be lifted off. Closing body 10, valve spring 11 and Valve seat 12 thus form an independent check valve.
  • a valve lifter 13 is connected, which can be moved under magnetic force and then keeps the closing body 10 away from its valve seat 12.
  • a low pressure pump 14 belongs to the device, a low pressure tank 15 and a check valve or Low pressure relief valve 16 in a low pressure circuit 17th
  • FIG 1 shows the high pressure pump 1 during the suction stroke.
  • fuel from the low pressure circuit 17 passes through the inlet line 8 (arrow direction) and against the force of the Valve spring 11 lifted from its valve seat 12 valve closing body 10 into the working chamber 5.
  • the solenoid valve 9 is without electricity.
  • the solenoid valve 9 switched off. As shown in Figure 3 arrives the closing body 10 under the influence of the force of Valve spring 11 and under flow forces on its valve seat 12. The solenoid valve is closed. In the work chamber 5 of the high pressure pump 1 begins to build up pressure, and Diesel fuel is released through the check valve that opens 7 and via the high pressure line 6 (arrow direction) in the High pressure accumulator 2 promoted. The low pressure pump 14 promotes into the low pressure circuit 17.
  • the high-pressure pump 1 constructed according to the invention with the one described Mode of operation has the following advantages: It is enough a relatively small and simple magnet to make it through the Liquid flow already closed valve closing body 10 to keep in its open position.
  • a change in delivery rate is due to the quick response the pressure control when closing the solenoid valve 9 slightly perform.
  • the structure of the high-pressure pump 1 is also notable Simplicity out by neither a handlebar regulation nor a Control edge still a control bore another control magnet for a position control loop is necessary. Furthermore, the Tappet for high pressure pump 1 must be installed from above. The high-pressure pump 1 can also be without bottom capsules be carried out.
  • FIG 4 shows using the same reference numbers for the execution according to Figures 1 to 3 corresponding Share another type of high pressure pump 18.
  • a pump piston 19 is provided with a connecting channel 20, via the connection in the TDC, i.e. at the end of the delivery stroke between a working chamber 21 of the high pressure pump 18 and the low pressure container 15 is produced.
  • the connecting channel 20 consists in detail of a Longitudinal channel 22 and an annular groove 23 in the pump piston 19. Die Annular groove 23 forms one with a bore 24 in a wall 25 Pump cylinder 26 a spool valve 27, by the edges of the annular groove 23 the mouth of the bore 24 run over in the wall 25 of the pump cylinder 26.
  • the This type of construction differs from the following Figures 1 to 3 in that here a metering for the High-pressure accumulator 2 and a shutdown before TDC enables is. There is also a larger diameter of the pump piston conceivable.
  • FIG. 5 shows a type with a high pressure pump 28, which does not have its own fuel connection.
  • a pressure valve assembly 29 are a combined solenoid valve 30 with closing body 31, valve spring 32 and valve seat 33 and a check valve 34 summarized, and this Pressure valve assembly is with a working chamber 35 High pressure pump 28 in connection.
  • Check valve 34 monitors the high pressure line 6 to the high pressure accumulator 2, and a ring connection 36 is provided on the solenoid valve 30, to which the low pressure circuit 17 is connected. In the Operation is the same as that of FIGS. 1 to 3, so that a repeated description is unnecessary.

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

Description

Stand der TechnikState of the art

Die Erfindung bezieht sich auf eine Hochdruckpumpe nach der Gattung des Hauptanspruches. Eine derartige Hochdruckpumpe ist bekannt (EP 0 481 964 A2).The invention relates to a high pressure pump according to the Genus of the main claim. Such a high pressure pump is known (EP 0 481 964 A2).

Solche Hochdruckpumpen werden zur Kraftstoffeinspritzung bei Dieselmotoren eingesetzt. Sie sind zwischen einem Niederdruckbehälter und einem Hochdruckspeicher (Rail) angeordnet und sorgen dafür, daß im Hochdruckspeicher Kraftstoff in genügender Menge und unter ausreichendem Hochdruck zur Verfügung steht, um über Einspritzventile gesteuert die Arbeitszylinder der Brennkraftmaschine mit Kraftstoff zu versorgen.Such high pressure pumps are used for fuel injection Diesel engines used. You are between a low pressure tank and a high-pressure accumulator (rail) arranged and ensure that there is sufficient fuel in the high-pressure accumulator Amount and under sufficient high pressure available stands to control the working cylinders via injectors to supply the internal combustion engine with fuel.

Bei der bekannten Hochdruckpumpe ist zwischen dem Niederdruckbehälter und dem Pumpenzylinder ein Elektromagnetventil angeordnet, das stromlos offen ist. Durch einen Stromimpuls wird es zur Festlegung des Beginns der Hochdruckförderung geschlossen. Im übrigen bleibt es unerregt. Zum Schließen des Elektromagnetventils sind vom Magneten verhältnismäßig große Kräfte aufzubringen, wobei die Kraft der dem Schließen entgegenwirkenden Ventilfeder überwunden werden muß. Dadurch sind Aufwand und Strombedarf des Magneten verhältnismäßig groß. In the known high pressure pump is between the low pressure container and the pump cylinder an electromagnetic valve arranged, which is open when de-energized. By a current pulse it will determine the start of high pressure production closed. For the rest, it remains unexcited. To close of the solenoid valve are proportional to the magnet to exert great forces, the force of which is closing counteracting valve spring must be overcome. Thereby the effort and power requirements of the magnet are proportional large.

Bei herkömmlichen Einspritzanlagen mit paralleler Versorgung mehrerer Pumpen-Arbeitsräume aus dem Niederdruckkreislauf gibt es bereits eine sogenannte Saugdrosselregelung, bei welcher die Pumpe mit variabler Teilführung betrieben wird. Dabei besteht aber Kavitationsgefahr durch Hohlraumbildung, außerdem entsteht bei Förderbeginn ein sehr schneller Druckaufbau.With conventional injection systems with parallel supply several pump work rooms from the low pressure circuit there is already a so-called suction throttle control, at which the pump is operated with variable partial guidance. However, there is a risk of cavitation due to the formation of cavities, in addition, pressure builds up very quickly at the start of delivery.

Ähnliche Nachteile treten auch auf, wenn bei einer Saugdrosselregelgung statt der Drossel ein Magnetventil und mit diesem eine Magnetventilzumessung zur Anwendung kommt.Similar disadvantages also occur when using a suction throttle control instead of the throttle a solenoid valve and with this a solenoid valve metering is used.

Die aufgezeigten Nachteile werden gemäß der Erfindung behoben durch die kennzeichnenden Merkmale des Hauptanspruch. Das hat bei einer Hochdruckpumpe der eingangs genannten Art den Vorteil, daß als Elektromagnetventil nur ein kleines und billiges Ventil benötigt wird, ohne daß dabei die Sicherheit der Einrichtung beeinträchtigt wäre.The disadvantages indicated are eliminated according to the invention by the characteristic features of the main claim. This has a high pressure pump of the type mentioned the advantage that as a solenoid valve only a small and cheap valve is needed without sacrificing safety the facility would be affected.

Vorteilhafte Weiterbildungen des Gegenstands des Anspruches 1 ergeben sich aus den Merkmalen der Unteransprüche sowie aus der Beschreibung und der Zeichnung. So ist es gemäß den Ansprüchen 2 und 3 von Vorteil, daß durch den Verbindungskanal, der im OT aufgesteuert wird, ein zu hoher Druck im Hochdruckbehälter vermeidbar ist. Eine solche Druckbegrenzung kann bei einem Fehler im System vor Schäden schützen.Advantageous further developments of the subject matter of the claim 1 result from the features of the subclaims as well from the description and the drawing. So it is according to claims 2 and 3 advantageous that through the connecting channel, which is opened in TDC, too high a pressure is avoidable in the high pressure container. Such a pressure limitation can protect against damage in the event of a fault in the system.

Zeichnungdrawing

Drei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen: Figur 1 eine erste Ausführung der Hochdruckpumpe im Saughub, Figur 2 die Hochdruckpumpe nach der Figur 1 vor Förderbeginn, Figur 3 die Hochdruckpumpe nach der Figur 1 nach Förderbeginn, Figur 4 eine andere Ausführung der Hochdruckpumpe und Figur 5 eine zweite Variante der Hochdruckpumpe.Three embodiments of the invention are in the drawing shown and in the description below explained. FIG. 1 shows a first embodiment of the High pressure pump in the suction stroke, Figure 2 after the high pressure pump 1 before the start of delivery, 3 the high pressure pump according to FIG. 1 after the start of funding, FIG. 4 another embodiment the high pressure pump and Figure 5 shows a second variant the high pressure pump.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Eine Hochdruckpumpe 1 wird als Diesel-Einspritzpumpe eingesetzt und ist zum Befüllen eines Hochdruckspeichers 2 (auch Rail genannt) bestimmt. An den Hochdruckspeicher 2 sind nicht dargestellte Einspritzventile angeschlossen über welche in ebenfalls nicht dargestellter Weise die Arbeitszylinder einer Brennkraftmaschine mit genau zugemessenen Mengen von Diesel-Kraftstoff versorgt werden.A high pressure pump 1 is used as a diesel injection pump and is for filling a high pressure accumulator 2 (also Rail called) determined. To the high pressure accumulator 2 are Injectors, not shown, connected via which in a manner not shown, the working cylinder an internal combustion engine with precisely measured quantities powered by diesel fuel.

Die Hochdruckpumpe 1 hat einen Pumpenkolben 3, der über einen nicht dargestellten Stößel in einem Pumpenzylinder 4 hin und her beweglich ist und der als bewegliche Wand eine Arbeitskammer 5 der Hochdruckpumpe 1 begrenzt. Eine Hochdruckleitung 6 führt von der Arbeitskammer 5 zum Hochdruckspeicher 2; in sie ist ein zum Hochdruckspeicher 2 hin öffnendes Rückschlagventil 7 eingesetzt.The high-pressure pump 1 has a pump piston 3, which has a Tappet, not shown, in a pump cylinder 4 and is movable here and that as a movable wall is a working chamber 5 of the high pressure pump 1 limited. A high pressure line 6 leads from the working chamber 5 to the high pressure accumulator 2; in it is an opening to the high pressure accumulator 2 Check valve 7 used.

Im Hinblick auf die vorliegende Erfindung ist zur Arbeitskammer 5 eine Einlaßleitung 8 geführt, in die ein Magnetventil 9 so eingesetzt ist, daß sein als Kugel ausgebildeter Schließkörper 10 gegen die Kraft einer Ventilfeder 11 allein vom Saugdruck in der Einlaßleitung 8 von seinem Ventilsitz 12 abhebbar ist. Schließkörper 10, Ventilfeder 11 und Ventilsitz 12 bilden auf diese Weise ein selbständiges Rückschlagventil. Mit dem nichtdargestellten Angriff des Ankers des Magneten des Magnetventils 9 ist ein Ventilstößel 13 verbunden, der unter Magnetkraft nach unten bewegbar ist und dann den Schließkörper 10 von seinem Ventilsitz 12 fernhält. Desweiteren gehört zur Einrichtung eine Niederdruckpumpe 14, ein Niederdruckbehälter 15 und ein Rückschlagventil oder Niederdruckbegrenzungsventil 16 in einem Niederdruckkreislauf 17.With regard to the present invention is the working chamber 5 led an inlet line 8 into which a solenoid valve 9 is used so that it is designed as a ball Closing body 10 against the force of a valve spring 11 alone from the suction pressure in the inlet line 8 from its valve seat 12 can be lifted off. Closing body 10, valve spring 11 and Valve seat 12 thus form an independent check valve. With the anchor not shown attack of the magnet of the solenoid valve 9 is a valve lifter 13 connected, which can be moved under magnetic force and then keeps the closing body 10 away from its valve seat 12. Furthermore, a low pressure pump 14 belongs to the device, a low pressure tank 15 and a check valve or Low pressure relief valve 16 in a low pressure circuit 17th

Wirkungsweisenmodes of action

Die Figur 1 zeigt die Hochdruckpumpe 1 beim Saughub. Kraftstoff aus dem Niederdruckkreislauf 17 gelangt über die Einlaßleitung 8 (Pfeilrichtung) und den gegen die Kraft der Ventilfeder 11 von seinem Ventilsitz 12 abgehobenen Ventilschließkörper 10 in die Arbeitskammer 5. Das Magnetventil 9 ist ohne Strom.Figure 1 shows the high pressure pump 1 during the suction stroke. fuel from the low pressure circuit 17 passes through the inlet line 8 (arrow direction) and against the force of the Valve spring 11 lifted from its valve seat 12 valve closing body 10 into the working chamber 5. The solenoid valve 9 is without electricity.

Wenn der Pumpenkolben 3 seinen unteren unteren Totpunkt UT erreicht hat, wird seine Bewegungsrichtung umgekehrt. Dieser Moment vor dem Förderbeginn der Hochdruckpumpe 1 ist in der Figur 2 unter Verwendung der gleichen Bezugszahlen wie in der Figur 1 dargestellt. Der Magnet des Magnetventils 9 wird bestromt, der Ventilstößel 13 schiebt sich gegen den Ventilschließkörper 10 und hält ihn entfernt von seinem Ventilsitz 12. Ein Teil des angesaugten Kraftstoffes wird vom Pumpenkolben 3 der Hochdruckpumpe 1 aus der Arbeitskammer 5 über die Einlaßleitung 8 zurück (Pfeilrichtung) zum Niederdruckkreislauf 17 und von dort über das Rückschlagventil 16 in den Niederdruckbehälter 15 gefördert.When the pump piston 3 has its lower bottom dead center UT has reached, its direction of movement is reversed. This The moment before the start of delivery of the high pressure pump 1 is in the Figure 2 using the same reference numerals as in shown in Figure 1. The magnet of the solenoid valve 9 is energized, the valve lifter 13 pushes against the valve closing body 10 and holds it away from its valve seat 12. Part of the fuel drawn in is from the pump piston 3 of the high pressure pump 1 from the working chamber 5 the inlet line 8 back (arrow direction) to the low pressure circuit 17 and from there via the check valve 16 in promoted the low pressure container 15.

Wenn der Pumpenkolben 3 auf seinem anschließenden Weg in Förderrichtung einen von dem Drehwinkel der Nockenwelle bestimmten Hub zurückgelegt hat, wird das Magnetventil 9 stromlos geschaltet. Wie in der Figur 3 dargestellt ist, gelangt der Schließkörper 10 unter Einwirkung der Kraft der Ventilfeder 11 und unter Strömungskräften auf seinen Ventilsitz 12. Das Magnetventil ist geschlossen. In der Arbeitskammer 5 der Hochdruckpumpe 1 beginnt der Druckaufbau, und Dieselkraftstoff wird über das sich öffnende Rückschlagventil 7 und über die Hochdruckleitung 6 (Pfeilrichtung) in den Hochdruckspeicher 2 gefördert. Die Niederdruckpumpe 14 fördert in den Niederdruckkreislauf 17.If the pump piston 3 on its subsequent path in Delivery direction determined by the angle of rotation of the camshaft Stroke, the solenoid valve 9 switched off. As shown in Figure 3 arrives the closing body 10 under the influence of the force of Valve spring 11 and under flow forces on its valve seat 12. The solenoid valve is closed. In the work chamber 5 of the high pressure pump 1 begins to build up pressure, and Diesel fuel is released through the check valve that opens 7 and via the high pressure line 6 (arrow direction) in the High pressure accumulator 2 promoted. The low pressure pump 14 promotes into the low pressure circuit 17.

Die erfindungsgemäß aufgebaute Hochdruckpumpe 1 mit der beschriebenen Wirkungsweise hat folgende Vorzüge: Es genügt ein relativ kleiner und einfacher Magnet, um den durch den Flüssigkeitsstrom bereits abgehobenen Ventilschließkörper 10 in seiner Offenstellung zu halten.The high-pressure pump 1 constructed according to the invention with the one described Mode of operation has the following advantages: It is enough a relatively small and simple magnet to make it through the Liquid flow already closed valve closing body 10 to keep in its open position.

Eine Fördermengenänderung ist durch das schnelle Ansprechen der Druckregelung beim Schließen des Magnetventils 9 leicht durchzuführen.A change in delivery rate is due to the quick response the pressure control when closing the solenoid valve 9 slightly perform.

Es gibt keine Steuerkanten. Infolge großer Überdeckungslänge gibt es auch nur ganz geringe Leckagen.There are no control edges. As a result of the large overlap there are only very few leaks.

Auch zeichnet sich der Aufbau der Hochdruckpumpe 1 durch Einfachheit aus indem weder eine Lenkerregulierung noch eine Steuerkante noch eine Steuerbohrung noch ein Stellmagnet für einen Lageregelkreis notwendig ist. Desweiteren kann der Stößel für die Hochdruckpumpe 1 von oben montiert werden. Auch kann die Hochdruckpumpe 1 ohne Bodenverschlußkapseln ausgeführt werden.The structure of the high-pressure pump 1 is also notable Simplicity out by neither a handlebar regulation nor a Control edge still a control bore another control magnet for a position control loop is necessary. Furthermore, the Tappet for high pressure pump 1 must be installed from above. The high-pressure pump 1 can also be without bottom capsules be carried out.

Schließlich gibt es beim Umschalten keinen Druckstoß und infolgedessen auch keine Kavitation.After all, there is no pressure surge when switching, and as a result also no cavitation.

Die Figur 4 zeigt unter Verwendung der gleichen Bezugszahlen für der Ausführung nach den Figuren 1 bis 3 entsprechenden Teile eine andere Bauart einer Hochdruckpumpe 18. Dabei sind aber die Hochdruckseite und die Niederdruckseite gerade so ausgeführt wie bei der Bauart nach den Figuren 1 bis 3. Hier ist ein Pumpenkolben 19 mit einem Verbindungskanal 20 versehen, über den im OT, also am Ende des Förderhubes, eine Verbindung zwischen einer Arbeitskammer 21 der Hochdruckpumpe 18 und dem Niederdruckbehälter 15 hergestellt wird.Figure 4 shows using the same reference numbers for the execution according to Figures 1 to 3 corresponding Share another type of high pressure pump 18. Here are but the high pressure side and the low pressure side just like that executed as in the design according to Figures 1 to 3. Here a pump piston 19 is provided with a connecting channel 20, via the connection in the TDC, i.e. at the end of the delivery stroke between a working chamber 21 of the high pressure pump 18 and the low pressure container 15 is produced.

Der Verbindungskanal 20 besteht im einzelnen aus einem Längskanal 22 und einer Ringnut 23 im Pumpenkolben 19. Die Ringnut 23 bildet mit einer Bohrung 24 in einer Wand 25 eines Pumpenzylinders 26 ein steuerschieberartiges Ventil 27, indem die Kanten der Ringnut 23 die Ausmündung der Bohrung 24 in der Wand 25 des Pumpenzylinders 26 überfahren. Die Wirkungsweise dieser Bauart unterscheidet sich von der nach den Figuren 1 bis 3 dadurch, daß hier eine Zumessung für den Hochdruckspeicher 2 und eine Absteuerung vor OT ermöglicht ist. Außerdem ist ein größerer Durchmesser des Pumpenkolbens denkbar.The connecting channel 20 consists in detail of a Longitudinal channel 22 and an annular groove 23 in the pump piston 19. Die Annular groove 23 forms one with a bore 24 in a wall 25 Pump cylinder 26 a spool valve 27, by the edges of the annular groove 23 the mouth of the bore 24 run over in the wall 25 of the pump cylinder 26. The This type of construction differs from the following Figures 1 to 3 in that here a metering for the High-pressure accumulator 2 and a shutdown before TDC enables is. There is also a larger diameter of the pump piston conceivable.

Die Figur 5 zeigt schließlich eine Bauart mit einer Hochdruckpumpe 28, die keinen eigenen Kraftstoffanschluß hat. In einem Druckventilverbund 29 sind ein kombiniertes Magnetventil 30 mit Schließkörper 31, Ventilfeder 32 und Ventilsitz 33 und ein Rückschlagventil 34 zusammengefaßt, und dieser Druckventilverbund steht mit einer Arbeitskammer 35 der Hochdruckpumpe 28 in Verbindung. Das Rückschlagventil 34 überwacht die Hochdruckleitung 6 zu dem Hochdruckspeicher 2, und am Magnetventil 30 ist ein Ringanschluß 36 vorgesehen, an den der Niederdruckkreislauf 17 angeschlossen ist. In der Wirkungsweise gleicht diese Bauart der nach den Figuren 1 bis 3, so daß sich eine nochmalige Beschreibung erübrigt.Finally, FIG. 5 shows a type with a high pressure pump 28, which does not have its own fuel connection. In a pressure valve assembly 29 are a combined solenoid valve 30 with closing body 31, valve spring 32 and valve seat 33 and a check valve 34 summarized, and this Pressure valve assembly is with a working chamber 35 High pressure pump 28 in connection. Check valve 34 monitors the high pressure line 6 to the high pressure accumulator 2, and a ring connection 36 is provided on the solenoid valve 30, to which the low pressure circuit 17 is connected. In the Operation is the same as that of FIGS. 1 to 3, so that a repeated description is unnecessary.

Claims (5)

  1. High-pressure pump, in particular for fuel injection for diesel engines, with a tappet-operated pump piston (3; 19) which is moveable back and forth in a pump cylinder (4; 26), and with an electromagnetic valve (9; 30) which consists of a magnet and of a non-return valve and which monitors both the inflow of fuel from a low-pressure circuit (17) to a working chamber (5; 21; 35) in the pump cylinder (4; 26) and a return of fuel out of the working chamber (5; 21; 35) to the low-pressure circuit (17), and also with a non-return valve (7; 34) inserted into a high-pressure line (6) leading from the working chamber (5; 21; 35) to a high-pressure accumulator (2), characterized in that the non-return valve of the electromagnetic valve (9; 30) has a closing body (10; 31) which, with the magnet live, can be held in the valve-open position by a valve tappet (13) of the electromagnetic valve (9; 30), and in that the start of high-pressure feed of the high-pressure pump (1; 18; 28) can be initiated by a de-energization of the magnet of the electromagnetic valve (9; 30).
  2. High-pressure pump according to Claim 1, characterized in that the pump piston (19) has provided in it a connecting duct (20), via which a connection between the working chamber (21) of the high-pressure pump (18) and a low-pressure tank (15) of the low-pressure circuit (17) can be made at top dead centre (TDC) at the end of feed.
  3. High-pressure pump according to Claim 2, characterized in that the connecting duct (20) is formed by at least one longitudinal duct (22) and one annular groove (23) in the pump piston (19), and in that the connection of the working chamber (21) to the low-pressure tank (15) can be made by means of a valve of the control-slide type which is formed by the edges of the annular groove (23) and by a bore (24) in a wall (25) of the pump cylinder (26).
  4. High-pressure pump according to Claim 1, characterized in that it has a composite delivery-valve structure (29) which contains the electromagnetic valve (30) and the non-return valve (34) opening towards the high-pressure accumulator (2) and which is connected to the working chamber (35) of the high-pressure pump (28), and in that both the low-pressure circuit (17) and the high-pressure accumulator (2) are connected to the composite delivery-valve structure (29).
  5. High-pressure pump according to Claim 4, characterized in that the low-pressure circuit (17) is connected to the composite delivery-valve structure (29) via an annular connection (36).
EP97110986A 1996-10-29 1997-07-02 High pressure pump Expired - Lifetime EP0840009B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19644915A DE19644915A1 (en) 1996-10-29 1996-10-29 high pressure pump
DE19644915 1996-10-29

Publications (3)

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EP0840009A2 EP0840009A2 (en) 1998-05-06
EP0840009A3 EP0840009A3 (en) 1999-12-01
EP0840009B1 true EP0840009B1 (en) 2003-10-15

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EP97110986A Expired - Lifetime EP0840009B1 (en) 1996-10-29 1997-07-02 High pressure pump

Country Status (5)

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US (1) US6116870A (en)
EP (1) EP0840009B1 (en)
JP (1) JPH10141177A (en)
KR (1) KR100514275B1 (en)
DE (2) DE19644915A1 (en)

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Also Published As

Publication number Publication date
DE19644915A1 (en) 1998-04-30
DE59710857D1 (en) 2003-11-20
KR100514275B1 (en) 2005-11-25
EP0840009A2 (en) 1998-05-06
US6116870A (en) 2000-09-12
JPH10141177A (en) 1998-05-26
EP0840009A3 (en) 1999-12-01
KR19980032334A (en) 1998-07-25

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