EP2156044B1 - Injecteur comprenant une soupape de commande à compensation de pression - Google Patents

Injecteur comprenant une soupape de commande à compensation de pression Download PDF

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Publication number
EP2156044B1
EP2156044B1 EP08736614A EP08736614A EP2156044B1 EP 2156044 B1 EP2156044 B1 EP 2156044B1 EP 08736614 A EP08736614 A EP 08736614A EP 08736614 A EP08736614 A EP 08736614A EP 2156044 B1 EP2156044 B1 EP 2156044B1
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EP
European Patent Office
Prior art keywords
valve
approximately
diameter
actuator
injector
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
EP08736614A
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German (de)
English (en)
Other versions
EP2156044A1 (fr
Inventor
Thomas Pauer
Andreas Rettich
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 EP2156044A1 publication Critical patent/EP2156044A1/fr
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02Fuel-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/0012Valves
    • F02M63/007Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/0012Valves
    • F02M63/007Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008Hollow valve members, e.g. members internally guided

Definitions

  • the invention relates to an injector for injecting fuel in a combustion chamber of an internal combustion engine, in particular a common rail injector according to the preamble of claim 1.
  • Injectors with a pressure-balanced in the axial direction control valve are known in two fundamentally different designs. Due to the pressure balance of the control valve, such injectors are particularly suitable for switching high fuel pressures, in particular beyond 2000 bar.
  • the actuator of the control valve is designed as a valve sleeve.
  • the valve sleeve defines a valve chamber formed on a diameter-reduced portion of a guide pin only radially outward, so that act from the located within the valve chamber, under high pressure fuel no forces in the axial direction on the valve sleeve.
  • injectors are known in which the valve sleeve of the control valve is guided not on its inner circumference, but on its outer periphery.
  • valve sleeve In a variant of these injectors, only a pressurized pressure pin in the axial direction is arranged within the valve sleeve, which seals the valve chamber provided within the valve chamber in the axial direction upwards. In this variant too, the high-pressure fuel within the valve chamber does not act on the valve sleeve in the axial direction.
  • the valve chamber In another variant of the control valve with valve sleeve, the valve chamber is arranged radially outside the valve sleeve. When lifted from the valve seat valve sleeve, the valve chamber is connected via a channel formed by the valve sleeve with the low pressure region of the injector.
  • the actuator is designed as a valve pin, wherein a valve chamber of the control valve is provided at a reduced diameter portion of the valve pin.
  • This design of axially balanced control valves is characterized in that the effective in two opposite axial directions, the valve chamber limiting pressure application surfaces on the valve pin are the same size, so that the forces acting in the opposite axial directions compressive forces cancel each other.
  • the invention is therefore based on the object to propose an injector, in which the wear effects on the opening and closing behavior are minimized.
  • the sealing diameter of the actuator is less than 3 mm, at least immediately after production, ie before the use of the injector.
  • Under sealing diameter in the context of the invention is understood to mean the valve seat fitting, the valve chamber directly limiting diameter of the actuator.
  • the sealing diameter is chosen so that the sealing diameter does not exceed 3 mm also due to wear during operation of the injector.
  • the provision of a sealing diameter of less than 3 mm has the advantage that the surface of a pressure stage which arises during operation is comparatively small, and consequently also the compressive force acting on the actuator in the opening direction. This is particularly due to the fact that the area of the resulting pressure stage square increases with increasing sealing diameter.
  • control valves in the axial direction are understood in the sine of the invention also control valves, in which already in the production of a minimum pressure level, i. a one-sided pressure application surface is provided, for example in order to counteract a wear caused by resulting diameter stage, or to selectively generate a low opening force, in particular to use actuators with lower power can.
  • a minimum pressure level i. a one-sided pressure application surface is provided, for example in order to counteract a wear caused by resulting diameter stage, or to selectively generate a low opening force, in particular to use actuators with lower power can.
  • the sealing diameter ie the valve chamber on the valve seat directly limiting diameter of the actuator is selected from a range between 2.5 mm and 2.95 mm. Even more advantageous is the sealing diameter from a diameter range between about 1.5 mm and about 2.0 mm. Of particular advantage is an embodiment in which the sealing diameter is selected from a diameter range between about 1.0 mm and about 1.5 mm. Particularly advantageous effects on minimized wear have a sealing diameter ranging between about 0.5 mm and about 1.0 mm.
  • the valve chamber on the opposite axial side limiting diameter of the actuator is also smaller than 3.0 mm.
  • This diameter is a guide diameter of the actuator, wherein the actuator is designed as a valve sleeve and is guided on a radially inner guide pin.
  • the control valve With guided on the outer circumference of the valve sleeve and disposed within the valve sleeve pressure pin, it is in this, in the axial direction of the voltage applied to the valve seat sealing diameter to a second sealing diameter with which the valve sleeve rests against the edge of the underside of the pressure pin.
  • the guide diameter or the second Dicht carefullyinesser of the actuator is selected from a range between about 2.5 mm and about 2.95 mm.
  • the guide diameter or the second sealing diameter is selected from a range between about 2.0 mm and about 2.5 mm.
  • Particularly advantageous is an embodiment with a guide diameter or a second sealing diameter from a range between about 1.0 mm and about 1.5 mm.
  • a particularly preferred embodiment is formed with a guide diameter or a second sealing diameter from a range between about 0.5 mm to about 1.0 mm.
  • the sealing diameter of the actuator resting against the valve seat is the same as that of the axially spaced guide diameter or the same as the second sealing diameter spaced in the axial direction.
  • control valve is, at least immediately after production, a control valve which is completely pressure-balanced in the axial direction.
  • The. Provision of a sealing diameter of less than 3 mm is realized in a control valve in which the actuator is designed as a valve sleeve.
  • the sealing diameter is the inner diameter of the valve sleeve with which the valve sleeve bears against the valve seat, for example a conical seat.
  • the valve sleeve is guided on its inner circumference on a guide pin, which is preferably formed integrally with a valve piece, which preferably carries the valve seat.
  • a valve chamber in the axial direction is limited by the voltage applied to the valve seat sealing diameter (inner diameter of the valve sleeve) and a spaced apart in the axial direction guide diameter with which the valve sleeve to the guide pin is guided.
  • the guide diameter preferably corresponds to the sealing diameter.
  • the outer diameter of the guide pin corresponds approximately to the inner diameter of the valve sleeve minus a minimum guide clearance.
  • valve sleeve is guided on its outer circumference.
  • a pressure pin is located inside the valve sleeve, wherein the inner diameter of the valve sleeve bearing against the pressure pin is a second sealing diameter (not the guide diameter).
  • valve chamber is arranged on the outer circumference of the valve sleeve.
  • sealing diameter of less than 3.0 mm is the outer diameter of the valve sleeve lying against the valve seat.
  • the invention can be realized in an injector with a control valve whose actuator is designed as a valve pin.
  • the sealing diameter preferably corresponds to the voltage applied to the valve seat outer diameter of the valve pin, which is preferably formed by a conical portion of the guide pin.
  • the valve chamber of such a control valve is limited by a guide diameter (outer diameter) of the valve pin.
  • the diameter of the valve pin within the valve chamber of the control valve is smaller, preferably by at least about 0.5 mm is less than the sealing diameter of the valve pin and thus also less than the axially spaced guide diameter of the valve pin.
  • Fig. 1 is a detail of a not erfindungsgemä ⁇ es common rail injector trained injector 1 for injecting fuel into a combustion chamber, not shown, of an internal combustion engine shown.
  • the injector 1 comprises an adjustable in the axial direction one or more parts valve element 2, which is adjustable between a closed position of the fuel flow from a nozzle hole arrangement not shown releasing opening position.
  • the valve element 2 delimits with an upper end face 3 a control chamber 4 radially inside a sleeve 5.
  • an inlet throttle 6 is introduced, via which the control chamber 4 is permanently supplied with high-pressure fuel.
  • the control chamber 4 is connected via an introduced into a valve piece 7 outlet throttle 8 with a valve chamber 9 of a control valve 10.
  • control valve 10 With the control valve 10 open, fuel can flow from the control chamber 4 into a low-pressure region 11 of the injector and from there to an injector return not shown.
  • the flow cross-sections of the outlet throttle and the inlet throttle 6 are matched to one another such that when the control valve 10 is open, a net outflow of fuel from the control chamber 4 results, whereby the forces acting on the valve element 2 closing forces decrease and thus the valve element 2 lifts from its valve seat, not shown, and releases the fuel flow into the combustion chamber. If the control valve 10 is closed, flows through the inlet throttle 6 continue to fuel in the control chamber 4, so that the pressure in the control chamber 4 and thus increase the force acting on the valve element 2 axial closing forces, so that the injection process is interrupted.
  • the control valve 10 comprises an adjustable in the axial direction as a valve pin formed actuator 12, which is formed integrally with an anchor plate 13 in this embodiment.
  • the armature plate 13 is part of an electromagnetic actuator, not shown, for opening the actuator 12.
  • a closing spring 14 is provided to close the bolt-shaped actuator 12.
  • the valve chamber 9 is partially formed within the valve member 7 and partially on a reduced diameter portion 15 of the actuator 12, wherein the pressure in opposite axial directions pressure application surfaces of the actuator 12 are equal.
  • a valve seat 16 is formed for engaging a conical portion 17 of the actuator 12.
  • the actuator 12 is located with a sealing diameter D on the valve seat 16.
  • the sealing diameter D of about 2.5 mm is an outer diameter of the actuator 12 at its conical portion 17th
  • the valve chamber 9 is delimited by a guide diameter D F of the actuator 12.
  • the actuator 12 With the guide diameter D F , the actuator 12 is radially on the outside of a guide bore 18 in the valve piece 7 at.
  • the amount of guide diameter D F corresponds to the amount of the sealing diameter D of the actuator 12th
  • the lower end face 19 of the actuator 12 defines a compensation chamber 20 which is connected via a connecting channel 21 to the low pressure region 11 of the injector, so that the pressure in the expansion chamber 20 during an adjusting movement of the actuator 12 is at least approximately constant.
  • Fig. 2 shows a further, not according to the invention erfindungsgemä ⁇ es example of an injector 1, wherein the basic operation of the injector shown the operation of the injector 1 according to Fig. 1 equivalent.
  • the actuator 12 is not formed as a valve pin, but as an axially adjustable valve sleeve 12 which is integrally formed with an anchor plate 13.
  • the actuator 12 is guided radially inwardly on an axially extending guide pin 22, which is integral with a valve piece 7 is formed, on which also the valve seat 16 of the control valve 10 is located.
  • the valve chamber 9 is formed on a reduced diameter portion 15 of the guide pin 22 and is supplied via an outlet throttle 8 with fuel from the control chamber 6.
  • the sleeve-shaped actuator limits the control chamber 6 only radially outward and lies with a guide diameter D, which is formed by an inner diameter of the sleeve-shaped actuator 12 to the valve seat 16 at.
  • the sealing diameter is in this embodiment about 2.3 mm.
  • valve chamber 9 On the axial side opposite the sealing diameter D, the valve chamber 9 is delimited by a guide diameter D F , which corresponds to the sealing diameter D.
  • the erfindungsgemä ⁇ e embodiment according to Fig. 3 corresponds in its operation to the embodiments according to the Fig. 1 and 2 ,
  • the sleeve-shaped actuator 12 is guided on its outer circumference, wherein in the valve piece 7, an axial channel 23 is formed, can flow through the fuel in the lifted off the valve seat 16 actuator 12 in the low pressure region 11 of the injector.
  • a pressure pin 24 which is supported in the axial direction on a holding body 25 of an electromagnetic actuator.
  • the sleeve-shaped actuator 12 bears against the valve seat 16 with a sealing diameter D formed by an inner diameter.
  • the valve chamber 9 is bounded on the opposite axial side by a second sealing diameter D 2 .
  • the sealing diameter D and the second sealing diameter D 2 are each 2.8 mm.
  • Fig. 4 is another, not according to the invention injector 1 shown. Also in this injector 1 corresponds to the basic operation in the Fig. 1 to 3 described injectors.
  • the actuator 12 is designed as a valve sleeve, wherein the valve seat 16 is formed on a valve member 7.
  • the valve chamber 9 is arranged radially outside the valve sleeve 12, so that the sealing diameter D, with which the sleeve-shaped actuator 12 bears against its valve seat 16, is formed by an outer diameter of the actuator 12.
  • the sealing diameter D is about 1.9 mm in this embodiment. Spaced in the axial direction of the sealing diameter D, the control chamber 9 is limited by a guide diameter D F of the sleeve-shaped actuator 12.

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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)

Claims (4)

  1. Injecteur pour injecter du carburant dans une chambre de combustion d'un moteur à combustion interne, en particulier injecteur à rampe commune, comprenant un élément de soupape (2) déplaçable entre une position de fermeture et une position d'ouverture libérant le flux de carburant dans la chambre de combustion, et comprenant une soupape de commande (10) compensée en pression au moins approximativement dans la direction axiale, avec un actionneur (12) réglable sur un siège de soupape (16), l'actionneur (12) étant réalisé sous forme de douille de soupape, qui est guidée sur sa périphérie interne sur un boulon de guidage (22), caractérisé en ce que l'actionneur (12) réalisé sous forme de douille de soupape est guidé sur sa périphérie extérieure et un diamètre d'étanchéité (D) de l'actionneur (12) s'appliquant contre le siège de soupape (16) est inférieur à 3 mm et un diamètre de guidage (DF) ou deuxième diamètre d'étanchéité (D2) de l'actionneur (12), limitant une chambre de soupape (16) de la soupape de commande (10), espacé du diamètre d'étanchéité (D) dans la direction axiale, est inférieur à 3,0 mm.
  2. Injecteur selon la revendication 1, caractérisé en ce que le diamètre d'étanchéité (D) est sélectionné à partir d'une plage comprise entre approximativement 2,5 mm et approximativement 2,95 mm, de préférence à partir d'une plage comprise entre environ 2,0 mm et environ 2,5 mm, en particulier à partir d'une plage comprise entre environ 1,5 mm et environ 2,0 mm, particulièrement préférablement à partir d'une plage comprise entre environ 1,0 mm et environ 1,5 mm, en particulier à partir d'une plage comprise entre environ 0,5 mm et environ 1,0 mm.
  3. Injecteur selon la revendication 1, caractérisé en ce que le diamètre de guidage (DF) ou le deuxième diamètre d'étanchéité (D2) est sélectionné à partir d'une plage comprise entre environ 2,5 mm et environ 2,95 mm, de préférence à partir d'une plage comprise entre environ 2,0 mm et environ 2,5 mm, en particulier à partir d'une plage comprise entre environ 1,5 mm et environ 2,0 mm, particulièrement préférablement à partir d'une plage comprise entre environ 1,0 mm et environ 1,5 mm, en particulier à partir d'une plage comprise entre environ 0,5 mm et environ 1,0 mm.
  4. Injecteur selon l'une quelconque des revendications 1 ou 3, caractérisé en ce que le diamètre d'étanchéité (D) est égal au diamètre de guidage (DF) ou est égal au deuxième diamètre d'étanchéité (D2).
EP08736614A 2007-05-14 2008-04-29 Injecteur comprenant une soupape de commande à compensation de pression Active EP2156044B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710022587 DE102007022587A1 (de) 2007-05-14 2007-05-14 Injektor mit druckausgeglichenem Steuerventil
PCT/EP2008/055204 WO2008138742A1 (fr) 2007-05-14 2008-04-29 Injecteur comprenant une soupape de commande à compensation de pression

Publications (2)

Publication Number Publication Date
EP2156044A1 EP2156044A1 (fr) 2010-02-24
EP2156044B1 true EP2156044B1 (fr) 2012-10-31

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ID=39705342

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08736614A Active EP2156044B1 (fr) 2007-05-14 2008-04-29 Injecteur comprenant une soupape de commande à compensation de pression

Country Status (3)

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EP (1) EP2156044B1 (fr)
DE (1) DE102007022587A1 (fr)
WO (1) WO2008138742A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015211705A1 (de) * 2015-06-24 2016-12-29 Robert Bosch Gmbh Kraftstoffinjektor mit Steuerventil
DE102016223287A1 (de) * 2016-11-24 2018-05-24 Robert Bosch Gmbh Steuerventil für einen Kraftstoffinjektor, Kraftstoffinjektor

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2336628A (en) * 1998-04-24 1999-10-27 Lucas Ind Plc A fuel injector, for an I.C. engine, having a three way two position needle control valve
DE10132249A1 (de) * 2001-07-04 2003-01-23 Bosch Gmbh Robert Kraftstoffinjektor mit kraftausgeglichenem Steuerventil
JP4019934B2 (ja) * 2002-12-26 2007-12-12 株式会社デンソー 制御弁および燃料噴射弁
ES2277229T3 (es) 2004-06-30 2007-07-01 C.R.F. Societa Consortile Per Azioni Servovalvula para controlar el inyector de combustible de un motor de combustion interna.

Also Published As

Publication number Publication date
EP2156044A1 (fr) 2010-02-24
DE102007022587A1 (de) 2008-11-27
WO2008138742A1 (fr) 2008-11-20

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