EP2880297B1 - Pompe haute pression pour moteur à combustion interne - Google Patents

Pompe haute pression pour moteur à combustion interne Download PDF

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Publication number
EP2880297B1
EP2880297B1 EP13740010.7A EP13740010A EP2880297B1 EP 2880297 B1 EP2880297 B1 EP 2880297B1 EP 13740010 A EP13740010 A EP 13740010A EP 2880297 B1 EP2880297 B1 EP 2880297B1
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EP
European Patent Office
Prior art keywords
valve
pressure
closing body
armature
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.)
Active
Application number
EP13740010.7A
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German (de)
English (en)
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EP2880297A1 (fr
Inventor
Friedrich Boecking
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP2880297A1 publication Critical patent/EP2880297A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/20—Output circuits, e.g. for controlling currents in command coils
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • F02D41/3809—Common rail control systems
    • F02D41/3836—Controlling the fuel pressure
    • F02D41/3845—Controlling the fuel pressure by controlling the flow into the common rail, e.g. the amount of fuel pumped
    • 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
    • F02M59/368—Pump inlet valves being closed when actuated

Definitions

  • the invention relates to a suction valve for a high pressure pump, which is used in particular for air-compressing, self-igniting internal combustion engines, and a high pressure pump, in particular a radial or in-line piston pump.
  • the high pressure pump can also serve as a piston pump for pumping other suitable liquids.
  • a high pressure pump which is used in particular as a radial or in-line piston pump for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • an inlet valve is provided, by means of which a metering of a fuel fed into a pump working chamber is made possible.
  • the pump working space can be completely filled.
  • partial filling of the pump working chamber can also be achieved by suitable control of the inlet valve.
  • the actuation takes place by energizing a magnetic coil.
  • the solenoid is switched off, the force of a valve spring can initiate a closing of the inlet valve largely without delay.
  • the valve spring acts via a valve element and an adjusting washer on an armature which is connected to a valve tappet. The valve tappet is thus acted upon by the preload of the valve spring.
  • the valve spring urges the valve tappet against the valve seat surface.
  • the known high-pressure pump can thus be fed from a low-pressure chamber into the pump working chamber by actuating the inlet valve.
  • the inlet valve is activated during a suction stroke of the pump piston.
  • the inlet valve is preferably closed during the delivery stroke of the pump piston.
  • an inlet valve is implemented that is closed in the de-energized state.
  • High closing dynamics can be achieved via a correspondingly high spring preload of the valve spring.
  • this configuration has the disadvantage that to open and hold open the Inlet valve the solenoid must be energized.
  • a correspondingly strong magnetic field is required, which results in high currents and thus high power losses.
  • there are large control energies since the inlet valve must be kept open over the entire suction phase.
  • a pump with a valve which can be held in a closed position by a control unit via an actuator.
  • a dosage is achieved that is independent of the movement of a piston of the pump.
  • the disclosure document DE 10 2010 039 832 A1 discloses a pump which is designed in particular as a high pressure pump, preferably as a radial piston pump.
  • the high pressure pump according to the invention with the features of claim 1 has the advantage that an improved control for metering fuel is made possible. In particular, energy consumption and the control energy required can be reduced.
  • the valve closing body can be acted upon in the opening direction via the pressure stage.
  • the closing direction which is oriented opposite to the opening direction
  • the valve closing body can be acted upon by the magnetic closing force via the armature.
  • the magnetic closing force therefore serves to support the closing of the suction valve.
  • the closing movement is preferably initiated by the magnetic closing force to such an extent that the suction valve moves from a dethrottled state into the throttling. In the throttling, the closing is then supported or at least largely conditioned by the hydraulic forces.
  • the magnetic closing force is therefore advantageously no longer required at the end of the closing process. This improves the control of the suction valve. In particular, the power consumption and the control energy required for closing are reduced.
  • a guide diameter for guiding the valve closing body is smaller than a seat diameter of the sealing seat.
  • the valve closing body is connected to the armature via a connecting bolt (valve bolt) in such a way that the connecting bolt is guided in a guide bore with the guide diameter, so that a valve chamber is formed between the guide bore and the sealing seat, into which fuel under a pre-feed pressure can be fed.
  • a connecting bolt valve bolt
  • an armature chamber in which the armature is arranged, is separated from the valve chamber by the connecting bolt guided in the guide bore, and that the armature chamber is relieved of pressure in relation to the prefeed pressure.
  • the pre-delivery pressure of the fuel in the valve chamber can thus advantageously bring about an effective force in the opening direction, which, however, is counteracted in the closing direction by a force that is dependent on the pressure in the pump working chamber.
  • a valve spring can be provided which acts on the valve closing body at least indirectly in the closing direction. It is also advantageous here that the valve spring is arranged in an armature space in which the armature is arranged and / or that the valve spring acts on the valve closing body by means of the armature and / or a valve pin that connects the armature to the valve closing body.
  • the closing spring defines an initial position of the suction valve.
  • the spring constant of the closing spring as well as a predetermined preload, a spring force that increases with the deflection and thus the opening stroke can be generated in the closing direction. This enables the suction valve to be tuned.
  • a control which effects the magnetic actuation of the armature by energizing a magnetic coil during a closing stroke of the valve closing body, the control switching the magnetic coil in a currentless state before the sealing seat is completely closed. This reduces the control energy required. This also reduces the cooling requirement for the magnet coil. It is also advantageous here that the control actuates the valve closing body by energizing the magnetic coil during the closing stroke of the valve closing body, to a throttling is achieved at the sealing seat. When the throttling on the sealing seat is reached, then the further closing stroke can be closed purely mechanically by the increasing interior pressure of the pump working space.
  • valve closing body can be actuated by the pressure in the pump working chamber in the closing direction if the valve closing body is actuated so far in the closing direction by the magnetic actuation of the armature that a throttling is reached at the sealing seat.
  • Fig. 1 shows a high-pressure pump 1 in a partial, schematic sectional view according to an embodiment of the invention.
  • the high pressure pump 1 can in particular be designed as a radial or in-line piston pump.
  • the high-pressure pump 1 is particularly suitable as a fuel pump for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • the high pressure pump 1 has a suction valve 2.
  • a preferred use of the high-pressure pump 1 and the suction valve 2 is for a fuel injection system with a fuel rail that stores diesel fuel under high pressure.
  • suitable liquids that is to say also liquids other than fuel, can also be controlled by the suction valve 2 and conveyed by the high-pressure pump 1.
  • the high-pressure pump 1 has a cylinder head 3 in which a pump working space 4 of a pump assembly 5 is formed.
  • a cylinder bore 6 is configured in the cylinder head 3, in which a pump piston 7 is guided.
  • the pump piston 7 delimits the pump working space 4 in the cylinder bore 6.
  • a drive shaft 8 with a cam 9 is mounted in a housing (not shown). In operation, the drive shaft 8 rotates about its axis of rotation 10. In this case, the pump piston 7 is actuated via the cam 9, which is illustrated by the double arrow 11. Actuation can take place, for example, via a roller mounted in a roller shoe.
  • the suction valve 2 has a valve seat body 12 on which a sealing seat 13 is configured.
  • the sealing seat 13 is circular with a seat diameter 14.
  • a valve closing body 15 is provided which interacts with the sealing seat 13 of the valve seat body 12.
  • valve seat body 12 is fixed to the cylinder head 3 via a screw plug. In this case, a seal is formed between the valve seat body 12 and the cylinder head 3, so that the pump working space 4 is sealed against the environment in a high-pressure resistant manner.
  • the suction valve 2 has a valve chamber 20 into which fuel which is under a pre-feed pressure is fed via one or more bores 21, 22.
  • the valve closing body 15 rests on the one hand against the sealing seat 13 with the seat diameter 14.
  • the valve closing body 15 is connected to a valve pin 23 or is designed in one piece with it.
  • the valve pin 23 is guided in a guide bore 24 of a body 25, which can be designed as a magnetic core.
  • the guide bore 24 has a guide diameter 26 which is smaller than the seat diameter 14 of the sealing seat 13.
  • An armature chamber 27 into which the valve pin 23 protrudes is relieved of pressure in relation to the prefeed pressure in the valve chamber 20.
  • a pressure level is formed which is determined by the seat diameter 14 of the sealing seat 13 and the guide diameter 26 of the guide bore 24. Because of the The pre-delivery pressure therefore results in a force directed in an opening direction 28 along an axis 29 of the valve pin 23 at the pressure stage.
  • the suction valve 2 also has an armature 30, which is connected to the valve pin 23 and is arranged in the armature chamber 27.
  • a magnetic coil 31 is provided, which can be energized by a controller 32.
  • the solenoid 31 When the solenoid 31 is energized, it generates a magnetic force on the armature 30, as a result of which the valve closing body 15 is acted upon in a closing direction 33, which is oriented counter to the opening direction 28, in the direction of the sealing seat 13 of the valve seat body 12.
  • a valve spring 34 is also provided, which acts on the valve closing body 15 via the armature 30 and the valve pin 23 in the closing direction 33.
  • FIG. 2 the stroke of the valve closing body in the opening direction 28 is plotted on the abscissa, while the flow rate dependent on the stroke is plotted on the ordinate.
  • the stroke of the valve closing body 15 in the opening direction 28 is plotted on the abscissa, while the forces acting on the valve closing body 15 in the closing direction 33 are plotted on the ordinate.
  • the time is plotted on the abscissa, while a pressure in the pump working chamber 4, the stroke of the valve closing body 15 in the opening direction 28 and a current flow to the solenoid 31 are plotted on the ordinate.
  • a curve 40 is shown as an example, which illustrates the flow 40 between the valve closing body 15 and the sealing seat 13 from the valve chamber 20 into the pump working chamber 4. If the stroke exceeds a value 41, then the suction valve 2 is in the dethrottled phase, which is in the Fig. 2 is illustrated by area 42. Below the value 41, the suction valve 2 is in the throttling, which is illustrated by a region 43. When the stroke disappears, the flow 40 also disappears.
  • a state 44 is assumed in which the suction valve 2 is located in the dethrottled area 42 and in which a comparatively large, in particular maximum, stroke of the valve closing body 15 is achieved.
  • a curve 45 shows a possible course of the spring force of the valve spring 34, which in the Closing direction 33 acts on valve closing body 15.
  • the ordinate intersection 46 of the curve 45 with the ordinate indicates a non-zero preload.
  • the bias of the valve spring 44 can be selected appropriately.
  • the slope of the curve 45 can also be specified via the spring constant of the valve spring 34.
  • the restoring force is initially applied essentially by valve spring 34.
  • valve closing body 15 already closes due to the restoring force of the valve spring 34, so that a curve 47 initially close to curve 45 is traversed, the direction of the curve traversing is indicated by the arrow 47.
  • the control 32 energizes the solenoid 31.
  • the closing force acting on the valve closing body 15 in the closing direction 33 rises steeply, which is illustrated by the arrow 49.
  • a maximum force 50 is exerted on the valve closing body 15.
  • the value falls below 41, so that the suction valve 2 reaches the throttled area 43.
  • the energization 54 is therefore characterized by a curve 54 with rapidly rising and falling edges.
  • the pressure in the pump working space 4 is illustrated by a curve 55.
  • This increases in the time intervals 48 ', 48 ", whereby the closing of the suction valve 2 in the throttled area 43 is supported by the increasing pressure in the pump working chamber 4.
  • the curve 56 illustrates the course of the stroke of the valve closing body 15. To simplify the illustration, go the curves 54, 55, 56 from a common level, the output values at this level not necessarily being zero.
  • the suction valve 2 is thus designed as an outwardly opening valve 2 with a pressure stage. If the interior pressure in the pump working space 4 is less than the pre-delivery pressure upstream of the suction valve 2, the valve closing body 15 opens against the valve spring 34. The pump working space 4 is filled until the suction valve 2 is electrically pulled out of the dethrottled phase by energizing the solenoid 31. The further closing stroke can then take place purely mechanically through the increasing interior pressure of the pump working chamber 4, since the suction valve 2 is throttling. The advantage of this is a very short activation time with a small stroke delta in order to activate the closing movement of the suction valve 2.
  • the area 48 can thus also include the initial state 44.
  • the closing of the suction valve 2 is then initiated directly by energizing the solenoid 31.

Claims (6)

  1. Pompe à haute pression (1), en particulier pompe à piston radiale ou en ligne destinée à des systèmes d'injection de carburant de moteurs à combustion interne à compression d'air et à autoallumage, ladite pompe comprenant au moins une culasse (3), un ensemble pompe (5) qui comprend une chambre de travail de pompe (4) ménagée dans la culasse (3), et au moins une soupape d'aspiration (2), le carburant pouvant être guidé jusque dans la chambre de travail de pompe (4) par le biais du siège d'étanchéité (13) de la soupape d'aspiration (2), la soupape d'aspiration (2) comportant un corps de fermeture de soupape (15) qui coopère avec un siège d'étanchéité (13) et un induit (30), actionnable magnétiquement, qui est relié au corps de fermeture de soupape (15) et l'induit (30) pouvant être actionné magnétiquement de telle sorte que le corps de fermeture de soupape (15) puisse être appliqué par le biais de l'induit (30) contre le siège d'étanchéité (13) par une force de fermeture magnétique dans un sens de fermeture (33), un étage de pression étant prévu qui permet d'actionner le corps de fermeture de soupape (15) dans un sens d'ouverture (28), et le corps de fermeture de soupape (15) pouvant être actionné dans le sens d'ouverture (28) par le biais d'une pression de prérefoulement agissant sur l'étage de pression pendant une course d'aspiration de l'ensemble de pompe (5) au cours de laquelle une pression dans la chambre de travail de pompe (4) est réduite, caractérisé en ce qu'un diamètre de guidage (26) de la soupape d'aspiration (2) pour guider le corps de fermeture de soupape (15) est inférieur à un diamètre de siège (14) du siège d'étanchéité (13), en ce que le corps de fermeture de soupape (15) est relié à l'induit (30) par le biais d'une tige de soupape (23), en ce que la tige de soupape (23) est guidée dans un alésage de guidage (24) ayant le diamètre de guidage (26), en ce qu'une chambre de soupape (20) de la soupape d'aspiration (2), dans laquelle du carburant, qui est sous une pression de prérefoulement, peut être guidé, est formée entre l'alésage de guidage (24) et le siège d'étanchéité (13), en ce qu'une chambre d'induit (27) de la soupape d'aspiration (2), dans laquelle l'induit (30) est disposée, est séparée de la chambre de soupape (20) par la tige de soupape (23) guidée dans l'alésage de guidage (24) et en ce que l'espace d'induit (27) est libéré de la pression par rapport à la pression de prérefoulement.
  2. Pompe à haute pression selon la revendication 1,
    caractérisée en ce que
    un ressort de soupape (34) de la soupape d'aspiration (2) est prévu qui agit sur le corps de fermeture de soupape (15) au moins indirectement dans le sens de fermeture (33).
  3. Pompe à haute pression selon la revendication 2,
    caractérisée en ce que
    le ressort de soupape (34) est disposé dans une chambre d'induit (27) de la soupape d'aspiration (2) dans laquelle l'induit (30) est disposée et/ou en ce que le ressort de soupape (34) contraint le corps de soupape (15) par le biais de l'induit (30) et/ou d'une tige de soupape (23) de la soupape d'aspiration (2), qui relie l'induit (30) au corps de fermeture de soupape (15).
  4. Pompe à haute pression selon l'une des revendications 1 à 3,
    caractérisée en ce que
    une commande (32) est prévue qui commande l'actionnement magnétique de l'induit (30) en excitant une bobine magnétique (31) de la soupape d'aspiration (2) pendant une course de fermeture du corps de fermeture de soupape (15), la commande (32) de la soupape d'aspiration (2) fait commuter sans courant la bobine magnétique (31) avant que le siège d'étanchéité (13) ne soit complètement fermé.
  5. Pompe à haute pression selon la revendication 4,
    caractérisée en ce que
    la commande (32) actionne le corps de fermeture de soupape (15) en excitant la bobine magnétique (31) pendant la course de fermeture du corps de fermeture de soupape (15) jusqu'à ce qu'un étranglement soit obtenu au niveau du siège d'étanchéité (13).
  6. Pompe à haute pression selon l'une des revendications 1 à 5,
    caractérisée en ce que,
    pendant une course de refoulement de l'ensemble de pompe (5) lors de laquelle une pression dans la chambre de travail de pompe (4) est augmentée, le corps de fermeture de soupape (15) est actionné par la pression dans la chambre de travail de pompe (4) dans le sens de fermeture (33) lorsque l'actionnement magnétique de l'induit (30) du corps de fermeture de soupape (15) est actionnée dans le sens de fermeture (33) jusqu'à ce qu'un étranglement soit obtenu au niveau du siège d'étanchéité (13).
EP13740010.7A 2012-08-01 2013-07-24 Pompe haute pression pour moteur à combustion interne Active EP2880297B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012213546.4A DE102012213546A1 (de) 2012-08-01 2012-08-01 Hochdruckpumpe für Brennkraftmaschinen
PCT/EP2013/065587 WO2014019904A1 (fr) 2012-08-01 2013-07-24 Pompe haute pression pour moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP2880297A1 EP2880297A1 (fr) 2015-06-10
EP2880297B1 true EP2880297B1 (fr) 2020-10-07

Family

ID=48856630

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13740010.7A Active EP2880297B1 (fr) 2012-08-01 2013-07-24 Pompe haute pression pour moteur à combustion interne

Country Status (5)

Country Link
EP (1) EP2880297B1 (fr)
CN (1) CN104508293B (fr)
DE (1) DE102012213546A1 (fr)
IN (1) IN2014DN10748A (fr)
WO (1) WO2014019904A1 (fr)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008018018A1 (de) * 2008-04-09 2009-10-15 Continental Automotive Gmbh Pumpe zur Förderung eines Fluids
DE102010039832A1 (de) * 2010-08-26 2012-03-01 Continental Automotive Gmbh Verfahren und Vorrichtung zum Erkennen eines Erreichens eines Schließpunkts eines hydraulischen Ventils

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3818607B2 (ja) * 1997-01-27 2006-09-06 株式会社小松製作所 カム駆動式の電子制御ユニットインジェクタの制御装置及びその制御方法
EP2295774A1 (fr) * 2009-08-18 2011-03-16 Delphi Technologies Holding S.à.r.l. Procédé et appareil de commande pour une pompe d'un système d'injection à rampe d'alimentation commune
JP5401360B2 (ja) * 2010-02-26 2014-01-29 日立オートモティブシステムズ株式会社 高圧燃料供給ポンプ
DE102010027745A1 (de) 2010-04-14 2011-10-20 Robert Bosch Gmbh Hochdruckpumpe

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008018018A1 (de) * 2008-04-09 2009-10-15 Continental Automotive Gmbh Pumpe zur Förderung eines Fluids
DE102010039832A1 (de) * 2010-08-26 2012-03-01 Continental Automotive Gmbh Verfahren und Vorrichtung zum Erkennen eines Erreichens eines Schließpunkts eines hydraulischen Ventils

Also Published As

Publication number Publication date
IN2014DN10748A (fr) 2015-09-04
CN104508293B (zh) 2018-07-03
WO2014019904A1 (fr) 2014-02-06
EP2880297A1 (fr) 2015-06-10
CN104508293A (zh) 2015-04-08
DE102012213546A1 (de) 2014-02-06

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