EP2347115B1 - Injecteur permettant l'injection de carburant sous haute pression dans la chambre de combustion d'un moteur à combustion interne - Google Patents

Injecteur permettant l'injection de carburant sous haute pression dans la chambre de combustion d'un moteur à combustion interne Download PDF

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Publication number
EP2347115B1
EP2347115B1 EP09781113.7A EP09781113A EP2347115B1 EP 2347115 B1 EP2347115 B1 EP 2347115B1 EP 09781113 A EP09781113 A EP 09781113A EP 2347115 B1 EP2347115 B1 EP 2347115B1
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EP
European Patent Office
Prior art keywords
control chamber
bore
throttle
valve
control
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.)
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Application number
EP09781113.7A
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German (de)
English (en)
Other versions
EP2347115A1 (fr
Inventor
Martin Schoeppl
Gerhard Weiss
Michael Pressler
Gerald Thaller
Michael Rainer Schmid
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
Original Assignee
Robert Bosch GmbH
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Publication of EP2347115A1 publication Critical patent/EP2347115A1/fr
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Publication of EP2347115B1 publication Critical patent/EP2347115B1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/008—Arrangement of fuel passages inside of injectors
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus

Definitions

  • injectors for injecting high-pressure fuel into a combustion chamber of an internal combustion engine in injectors for injecting high-pressure fuel into a combustion chamber of an internal combustion engine, as are known from the field of storage injection systems, the control of the injection process in dependence on the position of a control valve, which is associated with a control chamber of a valve spool.
  • the control chamber is in this case connected via an inlet bore in terms of flow with a high-pressure line via which the injector is supplied with the high-pressure fuel.
  • the control chamber of the valve spool is connected via a drain hole with a pressure compensation chamber, wherein the drain hole is closed by the pressure-compensating control valve. With an opening of the control valve, the high-pressure fuel flows through the drain hole from the control chamber into the pressure compensation chamber of the injector, whereby the valve spool is released.
  • the release of the valve control piston opens a nozzle needle valve, via which the fuel is injected into the combustion chamber of the internal combustion engine.
  • the dynamic opening and closing behavior of the nozzle needle valve which is dependent on the change in the control volume in the control chamber of the valve spool, can be determined by the design of an inlet throttle provided in the inlet bore and an outlet bore provided in the drain hole.
  • the high-pressure fuel from the control chamber flows at a high flow rate through the drain hole in the direction of the pressure equalization chamber of the injector, resulting in a reduction of the cross section in the region of the drain hole and the drain throttle local changes in fuel pressure. Since in storage injection systems of the fuel with a pressure of about 100 MPa or 1000 bar is applied, it may come due to the highly dynamic fluid movement to a local pressure drop, which leads to the local formation of vapor bubbles. In the adjoining the cross-sectional reduction Kochden Overpressure phases implode these vapor bubbles, which is also called cavitation.
  • a high pressure injection fuel injection valve is known from a central high pressure accumulator used in internal combustion engines.
  • the high-pressure accumulator is connected via an inlet throttle bore with a control chamber in operative connection and controls an opening and closing of an injection nozzle.
  • the control chamber communicates via an outlet throttle bore with a switching valve.
  • the inlet throttle bore is also eccentrically aligned with respect to the control chamber.
  • the invention is therefore based on the object to provide an injector for the injection of high-pressure fuel into the combustion chamber of an internal combustion engine, in which caused by Kavitationserosion damage to the valve seat of a pressure-compensating control valve, which closes the drain hole of a control chamber is avoided.
  • the injector for injecting high-pressure fuel into the combustion chamber of an internal combustion engine comprises an at least approximately rotationally symmetrical control chamber to which a valve control piston is assigned.
  • the control chamber is connected via an inlet bore hydraulically connected to the high pressure side of an injection system.
  • the inlet bore comprises an inlet throttle, which limits the flow of high-pressure fuel into the control chamber.
  • the control chamber is further connected via a drain hole with a low pressure side of the injector, wherein the drain hole is closed by a control valve.
  • control valve For injecting high-pressure fuel into the combustion chamber of the internal combustion engine, the control valve can be opened, wherein the high-pressure fuel from the control chamber via the drain hole and one in the drain hole provided drain throttle flows and as a result, the valve spool is released to open an injector.
  • the high-pressure fuel is introduced eccentrically via the inlet bore into the control chamber, so that the inflowing fuel generates a swirl flow within the control chamber, which has a rotational and a translational component.
  • the rotating within the control chamber flow has an axis of rotation which is coaxial with the axis of the drain hole.
  • the rotating fuel flow which is generated by the off-center supply of high-pressure fuel into the control chamber, continues in the form of a swirl into the drain hole. Due to the swirl and the resulting flow creates a vortex filament, which extends along the axis of rotation of the rotating flow and in the vortex core forms a Totwasser (1).
  • the Totwasser is no longer available to transport the fuel, so that the fuel can flow only on the walls of the control chamber and the drain hole along.
  • the vapor bubbles that result in an open control valve due to the high flow rate of the fuel and the change in fuel pressure in the region of the drain hole are in the center of the rotating flow, d. H. pushed into the vortex core, where the implosion of the vapor bubbles takes place.
  • the inlet throttle of the inlet bore extends in a direction which is eccentric to the cross section of the control chamber.
  • the axis of the inlet throttle and preferably also the axis of the entire inlet bore thus do not intersect the cross-sectional center of the control chamber.
  • At least one section is provided with an impact surface, which deflects the high-pressure fuel, which flows into the control chamber via the inlet bore.
  • the at least one baffle can be associated, for example, a portion of the wall which limits the control room.
  • the drain hole comprises a diffuser which reduces the flow rate of the fuel and increases the fuel pressure.
  • the diffuser is arranged on the control valve side facing the outlet throttle in the drain hole and thus in the flow direction of the fuel after the outlet throttle.
  • the rotating flow continues as a vortex to the drain hole, the vortex is fully formed in the area of the outlet throttle and rotates at high speed.
  • the air venting area of the vortex widens conically, whereby the vapor bubbles present in the vortex core are purposefully brought to implosion.
  • the inventive arrangement of the diffuser after the outlet throttle thus results in the advantage that the cavitation takes place in the region of the drain hole in which it does not cause erosion.
  • the diffuser has an optimized opening angle in a range of less than 15 ° or is cylindrical.
  • the drain hole has a control chamber side bore portion which is arranged coaxially to the outlet throttle and has a larger inner diameter than the outlet throttle.
  • the cross-sectional transition from the bore section to the outlet throttle can in this case be stepped, conical or in a rounded shape.
  • the control-chamber-side bore portion which preferably has a cylindrical shape, stabilizes the vortex core, which results from the rotating in the control room flow. The vortex core continues as vortex filament into the outlet throttle, which adjoins the bore section.
  • the transition from the bore section to the outlet throttle has a conical shape, whereby flow turbulences in the transition region between the bore section and the outlet throttle are avoided.
  • the drain hole has at its end facing the control chamber an inlet rounding.
  • the drain hole at its end facing the control chamber has an inlet edge, which forms the transition between the control chamber and the drain hole.
  • a further conical transition area is provided between the outlet throttle and the valve seat of the control valve.
  • the further conical transition region which is provided at the end of the drainage bore facing the control valve and thereby forms the transition from the drainage bore to the valve seat of the control valve, is in this case designed as a chamfer.
  • the control valve has a spherical valve body, which serves as a shut-off for the drain hole.
  • the spherical valve body is in this case rotatably received in a corresponding guide of the control valve and can thus be offset by the swirl pulse of the fuel flow in rotation.
  • the rotation of the valve ball has the advantage that the wear of the valve ball is reduced and extends the service life of the control valve.
  • valve control piston is received rotatably about its longitudinal axis in the injector.
  • the valve control piston is in this case displaceable by the swirl flow in a rotation, which advantageously reduces the wear of the valve spool and increases its life.
  • FIG. 1 shows a partial view of an axial section through an injector 1 with a valve piece 4, which is inserted into a housing 2 of the injector 1.
  • the valve piece 4 is arranged in a multi-stepped axial recess 6 of the housing 2, in which a valve spool 8 centered and axially and rotationally movably received.
  • injector 2 includes a FIG. 1 not shown nozzle body, in which a coaxial with the valve control piston 8 arranged nozzle needle is provided which opens an injection nozzle for injecting high-pressure fuel in the combustion chamber of an internal combustion engine in phases.
  • an axial bore 10 is provided, which extends in the axial direction of the valve member 4 therethrough and is divided into sections with different sized inner diameters.
  • the valve control piston 8 is movably received with its upper end in the axial direction, resulting in a comparatively small-volume control chamber 12 in the valve piece 4 above the valve spool 8.
  • the provided in the valve piece 4 axial bore 10 extends to a valve seat 16 of an in FIG. 1 not shown control valve.
  • the portion of the axial bore 10 between the control chamber 12 and the valve seat 16 is in this case designed as a drain hole 14 and is characterized by a in FIG.
  • control valve with respect to the arranged above the valve member 4 cavity of the axial recess 6 of the injector housing 2, which serves as a pressure equalization chamber, closed.
  • an inlet bore 20 is provided in the wall 18 of the valve member 4, which connects the control chamber 12 via an annular space 22 with a high pressure port 24.
  • the control chamber 12 is thus supplied with high-pressure fuel via the annular space 22 and the inlet bore 20, an inlet throttle 26 being provided in the inlet bore 20 for restricting the volume flow.
  • FIG. 2a and the FIG. 2b two cross-sectional views of a control chamber 12 of a valve piece 4 are shown, which comprises an inlet bore 20 with an inlet throttle 26.
  • the inlet bore 20 in this case connects the arranged within the valve member 4 control chamber 12 hydraulically with the in FIG. 1 shown annulus 22 of the injector 1.
  • the inlet bore 20 in addition to the inlet throttle 26, which merges into the control chamber 12, moreover, a counterbore with a cylindrical portion 28 and a conical portion 30.
  • centrally arranged inlet throttle are in the Figure 2a and 2b shown inlet throttles 26 arranged eccentrically.
  • FIG. 2a When in FIG. 2a shown cross-section of an eccentrically arranged inlet throttle 20, the axis of the inlet bore 20 and the inlet throttle 26 is rotated by an angle x relative to a radial orientation of the inlet bore.
  • the cylindrical portion 28 of the inlet bore 20 is in this case arranged coaxially to the inlet throttle 26. Due to the conical portion 30 of the inlet bore 20, which may also be arranged coaxially to the inlet throttle 26, resulting from the inflow of high-pressure fuel from the annular space 22 into the inlet bore 20 hydrodynamically advantageous Flow conditions.
  • the cross section of an injector according to the invention with an eccentrically arranged inlet bore 20 is in FIG. 2b shown.
  • the conical portion 30 and the cylindrical portion 28 of the inlet bore 20 are arranged centrally, whereas the inlet throttle 26 is eccentrically offset from a radial alignment by an offset e.
  • the inlet throttle 26 in the wall 18 of the valve member 4 of the high-pressure fuel flows from the in FIG. 1 shown annulus 22 tangentially into the control chamber 12, whereby a swirl flow with a translational and rotational component is formed.
  • the vortex filament represents the center line of the vortex core 38 extending in the axial direction of the axial bore 10 of the valve piece 4, which propagates along the flow direction.
  • FIG. 1 illustrated embodiment of the drain hole 14
  • this extends in several cross-sectional sections up to the conically shaped valve seat 16 of the control valve.
  • an outlet throttle 42 follows, followed by a diffuser 44.
  • a conical transition region 46 may be arranged, which has a smaller cone diameter than the adjoining valve seat 16.
  • the different sections 40, 42, 44 differ-Nach the embodiment of the drain hole 14 after FIG. 1 the transition from the control chamber 12 to the cylindrical bore portion 40, the transition from the cylindrical bore portion 40 to the outlet throttle 42 and the transition from the outlet throttle 42 to the diffuser 44 are made step-shaped.
  • FIG. 4 An alternative embodiment of the drain hole 14 is the FIG. 4 can be seen in which an axial longitudinal section through the valve member 4 in the region of the drain hole 14 is shown. Unlike the in FIG. 1 illustrated drain hole 14 made the transition from the control chamber 12 to the cylindrical bore portion 40 and the transition from the cylindrical bore portion 40 to the outlet throttle 42 is not in a stepped shape. Between the control chamber 12 and the cylindrical bore portion 40, a conical portion 48 of the drain hole 14 is arranged, which tapers from the control chamber 12 in the direction of the cylindrical bore portion 40 tapers.
  • a circumferential chamfer 50 which has a larger cone diameter in the transition from the control chamber 12 to the drain hole 14 by the arrangement of the circumferential chamfer 50 and the conical sections 48 in front of the cylindrical bore portion 40, a break in the flow in the region of the change in cross section between the control chamber 12 and the cylindrical bore portion 40 is prevented, whereby the vortex core 38 of the rotating flow is stabilized.
  • FIG. 4 illustrated embodiment may be provided as an alternative or in addition to an adjacent to the control chamber 12 circumferential chamfer 50 that the drain hole 14 at its end facing the control chamber 12 has an outlet opening whose edge is rounded.
  • the cylindrical bore section 40 has a conical shape in the transitional region 52 to the outlet throttle 42.
  • the transition from the outlet throttle 42 to the diffuser 44 is step-shaped.
  • the diffuser 44 may in this case have an optimized opening angle of preferably less than 15 °, whereby the speed level of the swirl flow is reduced and the pressure level is increased.
  • the vapor bubbles formed in the vortex core 38 of the swirl flow are due the increase in the pressure level in the region of the diffuser 44 is deliberately brought to implosion, without any damage being caused by cavitation erosion at the wall bounding the drainage bore 14.
  • the effect according to the invention that no damage to the conical valve seat 16 occurs.
  • a conical transition region 46 connects, which merges into a conical valve seat 16.
  • the conical transition region 46 has a smaller cone diameter than the conical valve seat 16.
  • the conical transition region 46 FIG. 1 and 4 represents a flow transition section, which can serve as a damage-relevant area for cavitation in front of the valve seat 16.
  • the drain hole 14 is closed by a spherical valve body 54, which by a in FIG. 1 and 4 not shown ball guide rotatably guided and actuated by an actuator, also not shown.
  • the swirl impulse of the swirl flow allows the spherical valve body 54 to be set in rotation.
  • the inlet bore 20 and the drain hole 14 have a combination of differently shaped transitions.
  • the transitions between the sections of different inner diameter preferably have a conical or conical shape, a step shape or a rounded shape.

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

Claims (8)

  1. Injecteur pour moteurs à combustion interne comprenant un espace de commande (12) d'un piston de commande de soupape (8) auquel est associé un alésage d'amenée (20) présentant un étranglement d'amenée (26) pour l'alimentation en carburant sous haute pression et un alésage de sortie (14) présentant un étranglement de sortie (42), lequel peut être fermé par une soupape de commande, l'étranglement d'amenée (26) s'étendant dans une direction excentrée par rapport à l'espace de commande (12), en ce que le carburant sous haute pression s'écoulant à travers l'alésage d'amenée (20) est introduit de manière excentrique dans l'espace de commande (12), caractérisé en ce que l'alésage d'amenée (20) comprend, en plus de l'étranglement d'amenée (26) qui se prolonge par l'espace de commande (12), une portion cylindrique (28) et une portion conique (30), et en ce que la portion conique (30) et la portion cylindrique (28) de l'alésage d'amenée (20) sont disposées centralement, tandis que l'étranglement d'amenée (26) est décalé de manière excentrique d'un déport e par rapport à une orientation radiale.
  2. Injecteur selon la revendication 1, caractérisé en ce qu'au moins une portion comprenant une surface d'impact est prévue dans l'espace de commande (12), laquelle portion dévie le carburant affluant dans l'espace de commande (12).
  3. Injecteur selon la revendication 1, caractérisé en ce que l'alésage de sortie (14) comprend un diffuseur (44), lequel est disposé du côté de l'étranglement de sortie (42) tourné vers la soupape de commande.
  4. Injecteur selon la revendication 3, caractérisé en ce que le diffuseur (44) présente un angle d'ouverture dans une plage optimisée inférieure à 15°.
  5. Injecteur selon les revendications 3 ou 4, caractérisé en ce que l'alésage de sortie (14) présente une portion d'alésage (40) du côté de l'espace de commande, laquelle présente un diamètre intérieur plus grand que l'étranglement de sortie (42), la transition de section transversale de la portion d'alésage (40) à l'étranglement de sortie (42) étant sous forme étagée, sous forme conique ou arrondie.
  6. Injecteur selon l'une quelconque des revendications 3 à 5, caractérisé en ce que l'alésage de sortie (14) présente, au niveau de son extrémité tournée vers l'espace de commande (12), un arrondi d'entrée.
  7. Injecteur selon l'une quelconque des revendications 3 à 6, caractérisé en ce que l'alésage de sortie (14) présente, au niveau de son extrémité tournée vers l'espace de commande (12), une portion conique (48) qui s'élargit dans la direction de l'espace de commande (12).
  8. Injecteur selon l'une quelconque des revendications 3 à 7, caractérisé en ce qu'entre l'étranglement de sortie (42) et le siège de soupape (16) de la soupape de commande est prévue une région de transition conique (46).
EP09781113.7A 2008-09-23 2009-07-27 Injecteur permettant l'injection de carburant sous haute pression dans la chambre de combustion d'un moteur à combustion interne Active EP2347115B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810042293 DE102008042293A1 (de) 2008-09-23 2008-09-23 Injektor zur Einspritzung von mit Hochdruck beaufschlagtem Kraftstoff in den Brennraum einer Brennkraftmaschine
PCT/EP2009/059649 WO2010034544A1 (fr) 2008-09-23 2009-07-27 Injecteur permettant l'injection de carburant sous haute pression dans la chambre de combustion d'un moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP2347115A1 EP2347115A1 (fr) 2011-07-27
EP2347115B1 true EP2347115B1 (fr) 2013-09-11

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP09781113.7A Active EP2347115B1 (fr) 2008-09-23 2009-07-27 Injecteur permettant l'injection de carburant sous haute pression dans la chambre de combustion d'un moteur à combustion interne

Country Status (4)

Country Link
EP (1) EP2347115B1 (fr)
CN (1) CN102165176B (fr)
DE (1) DE102008042293A1 (fr)
WO (1) WO2010034544A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3218094B1 (fr) * 2014-11-11 2020-01-08 Robert Bosch GmbH Soupape d'injection avec chambre de commande
CN110822106B (zh) * 2018-08-09 2022-10-28 罗伯特·博世有限公司 用于制冷阀的传动装置和制冷阀

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19859592C1 (de) * 1998-12-22 2000-05-04 Bosch Gmbh Robert Kraftstoffeinspritzventil
DE19939939A1 (de) * 1999-08-23 2001-04-19 Bosch Gmbh Robert Injektor für ein Common-Rail-Einspritzsystem für Brennkraftmaschinen mit kompakter Bauweise
DE19940290A1 (de) * 1999-08-25 2001-03-01 Bosch Gmbh Robert Steuerventil für ein Kraftstoffeinspritzventil
DE10123775B4 (de) * 2001-05-16 2005-01-20 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung für Brennkraftmaschinen, insbesondere Common-Rail-Injektor, sowie Kraftstoffsystem und Brennkraftmaschine
JP2003113761A (ja) * 2001-08-01 2003-04-18 Denso Corp 燃料噴射弁
DE10259950A1 (de) * 2002-12-20 2004-07-01 Robert Bosch Gmbh Steuerventil für Injektoren, insbesondere Common-Rail-Injektoren von Brennkraftmaschinen

Also Published As

Publication number Publication date
WO2010034544A1 (fr) 2010-04-01
DE102008042293A1 (de) 2010-03-25
CN102165176B (zh) 2014-02-19
EP2347115A1 (fr) 2011-07-27
CN102165176A (zh) 2011-08-24

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