WO2009121647A1 - Amortissement hydraulique - Google Patents

Amortissement hydraulique Download PDF

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Publication number
WO2009121647A1
WO2009121647A1 PCT/EP2009/051218 EP2009051218W WO2009121647A1 WO 2009121647 A1 WO2009121647 A1 WO 2009121647A1 EP 2009051218 W EP2009051218 W EP 2009051218W WO 2009121647 A1 WO2009121647 A1 WO 2009121647A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pressure
valve member
solenoid valve
valve according
Prior art date
Application number
PCT/EP2009/051218
Other languages
German (de)
English (en)
Inventor
Matthias Burger
Hans-Christoph Magel
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2009121647A1 publication Critical patent/WO2009121647A1/fr

Links

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
    • 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
    • F02M47/027—Electrically actuated valves draining the chamber to release the 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
    • 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
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means

Definitions

  • fast-switching valves such as fast-switching solenoid valves.
  • fast-switching valves there is the problem that characteristic ripples occur due to bumping. Under bouncing unintentional relegation of the valve seat is understood by the higher impact energy striking the valve seat closing element and a due to the elasticity of the materials occurring rebounding in the opening direction. The bouncing of the valve member occurs in particular in hard running stroke stops in metal / metal contact in conjunction with a fast-switching valve needle of a fuel injector solenoid valve.
  • valve seat Unlike an upper stroke stop, for example, on a stop sleeve in the magnetic core, due to its sealing function no nip can be performed on the valve seat.
  • a high stop impulse of the valve needle in the valve seat not only leads to bumping when closing, but also to a significantly increased valve seat wear.
  • the overpressure or the negative pressure is used to exert an additional hydraulic force on the valve or the valve member of the solenoid valve, which is usually shaped like a needle.
  • the differential pressure is due to the inertia of the hydraulic fluid, i. of the fuel, in the hydraulic line that opens into the valve chamber.
  • the hydraulically generated, acting in the opening direction of the valve member hydraulic force arises at the time of opening and leads to an additional acceleration of the valve member of the solenoid valve, which leads to faster switching operations.
  • closing the valve member of the solenoid valve creates a closing supporting hydraulic force.
  • the main advantage of the additional closing force resulting from closing is the prevention of mechanical bounce.
  • a greater force is exerted on the armature and thus on the valve member in the closing direction, compared with the force acting on the valve member or the armature during the closing movement.
  • This is the decisive advantage of the proposed solution according to the invention, since a mechanical bouncing with a mere increase in the spring force the closing spring acting in the closing direction can not be prevented.
  • the mechanical bouncing is counteracted by a greater closing force acts on the armature at the time of closing of the valve member than during the running in the direction of the valve seat closing movement.
  • the diversion line is advantageously designed as a bore and designed by its length / width ratio so that the function of a hydraulic line is given.
  • this hydraulic line can be formed as a bore in a sleeve delimiting the high-pressure volume in front of the valve seat in the valve piece, and on the other hand as a bore having a long line length in a plurality of sections in the valve piece.
  • this hydraulic line which can be displayed in the two variants outlined above, arises at the time of opening of the valve member in the low pressure volume overpressure, since the hydraulic fluid is accelerated in the diversion line.
  • the overpressure generates a force acting in the opening direction on the valve member, so that its switching time is reduced in an advantageous manner.
  • the overpressure in the diversion line is only present for a short time until a stationary flow has set within the diversion line.
  • FIG. 1 shows a solenoid valve whose low-pressure volume is connected via a hydraulic line in a first embodiment with a valve chamber
  • Figure 2 shows a solenoid valve whose low pressure volume is connected via a hydraulic line in a second embodiment with a valve chamber
  • Figure 3 shows a further constructive variant in which the Ab Kunststofftechnisch is realized via a sleeve.
  • a fuel injector 10 comprises an injector body 12 which is constructed symmetrically with respect to the injector axis 14.
  • a solenoid valve 16 is integrated in the fuel injector 10.
  • the injector body 12 of the fuel injector 10 is acted upon by a high pressure port 18 with fluid under a system pressure, preferably fuel.
  • the system pressure with which the fuel is present at the high-pressure port 18 of the injector body 12 of the fuel injector 10 is generated in a high-pressure accumulator body (common rail), for example via a hydraulic pump.
  • Reference numeral 20 denotes a return port, which is located above the solenoid valve 16 of the fuel injector 10.
  • the fuel injector 10 comprises a valve piece 22, which is fastened by means of a screwed in the interior of the injector body 12 valve clamping nut 36 in this.
  • a control chamber 24 is formed in the valve piece 22 in the valve piece 22, a control chamber 24 is formed.
  • the control chamber 24 is pressure-relieved via a drain passage 30, in which at least one outlet throttle 32 is received.
  • the control chamber 24 is supplied with fuel via an inlet throttle 34 from a high-pressure volume 38, which is supplied by fuel under system pressure, coming from the high-pressure port 18.
  • the control chamber 24 acts on an upper end face of a generally needle-shaped injection valve member 26.
  • the injection valve member 26 is guided in the injector body 12 of the fuel injector 10.
  • the injection valve member 26 is at the combustion chamber end the Kraftstoff ⁇ njektors 10 - not shown in Figure 1 - injection openings freely, via which with open injection valve member 26 of the fuel under system pressure from the high pressure volume 38 flows to the open injection ports at the combustion chamber end of the fuel injector 10.
  • the valve member 22 shown in Figure 1 comprises a flat surface 40 in which a valve seat 42 is executed.
  • the valve seat 42 is designed in the embodiment shown in Figure 1 as a flat seat.
  • the valve seat 42 is closed by a valve member 46, which is located below an armature 48.
  • the valve seat 42 is located at the discharge point of the discharge channel 30 for pressure relief of the control chamber 24, wherein the drainage channel 30 comprises at least one outlet throttle 32.
  • valve member 46 Above the plane surface 40 is a guide body 44, in which the valve member 46 is guided with a valve needle 52, which serves to position it. On the other hand, the valve member 46 is guided below the armature 48 via a high pressure-tight guide 50 to a pressure pin 54.
  • valve member 46 and the armature 48 are acted upon by a closing spring 56 which places the valve member 46 in the valve seat 42 formed on the flat surface 40 of the valve member 22.
  • the solenoid valve 16 which is located above the armature 48, comprises a magnet group 58, a magnetic core 60 and a magnetic coil 62 embedded therein. At the upper side of the armature 48 facing the magnetic coil 32 is a disc-shaped upper stroke stop 64.
  • the fuel injector 10 comprises further hydraulic spaces.
  • this includes a high-pressure volume 66, which is located behind the valve seat 42, limited by the inside of the valve member 46.
  • a low pressure volume 68 behind the valve seat 42 is about a in the illustrations according to Figures 1 and 2 in two different embodiments procured Ab Kunststoff Kunststoff 72 with a valve chamber 70 with connection to the return 20 hydraulically connected.
  • the diversion line 72 between the low-pressure volume 68 and the valve space 70 can be designed as a bore passing through the guide body 44 in the radial direction.
  • longer line lengths can be represented.
  • the operation of the fuel injectors 10 shown in Figures 1 and 2 is as follows:
  • the armature 48 of the solenoid valve 16 is the same pressure balanced in the closed state, which means that act on the armature 48 no pressure forces. This is achieved in that the sealing edge of the valve seat 42 acts on the same diameter as the high pressure-tight guide 50. The pressure force is thus absorbed via the pressure pin 54, on which the valve member 46 is guided.
  • the armature 48 opens, so that Abcontestedmenge flows from the control chamber 24 via the drain passage 30, in which at least one outlet throttle 32 is provided, flows through the high pressure volume 66 in the low pressure volume 68.
  • the low-pressure volume 68 is hydraulically connected via the diversion line 72 to the valve space 70.
  • the diversion line 72 which according to FIG. 1 may be formed as a bore in the guide body 44, is designed by its length / width ratio such that it assumes the function of a hydraulic line.
  • the illustration according to FIG. 2 shows the embodiment of the diversion line 72 in the valve piece 22.
  • the negative pressure arising in the low-pressure volume 68 acts on the armature 48 or on the valve member 46 as a force acting in the closing direction Occurring force prevents the mechanical bouncing of the valve member 46, ie its unintentional leaving the valve seat 42. Also, this pressure difference, which supports the force acting in the closing direction, is only of short duration, so that the solenoid valve 16 after a short time again pressure balanced, respectively works hydraulically without force.
  • FIG. 3 shows a further structural design of the fuel injector proposed according to the invention, in which the diversion line is designed in an integrated sleeve.
  • a sleeve 80 is integrated.
  • the integrated sleeve 80 has an upper surface 82 which is arranged in a concave contour 84.
  • the concave contour 84 at the top 82 of the integral sleeve 80 provides the advantage that the compressive forces on the entire anchor surface, i. act on the entire underside of the armature 48 and thereby creates a larger force.
  • the concave contour 84 on the upper side 82 of the integrated sleeve 80 also causes the flow cross-section 86, as seen in the radial direction, can be kept substantially constant. In the illustration according to FIG.
  • valve needle guide 72 instead of the valve needle guide 72 shown in FIG. 1 is realized in the guide body 44, here via a polygonal guide 88 which is attached to the integrated sleeve 80.
  • the valve member 46, or the armature 48 is comprised without contact.
  • the valve needle guide 52 shown in connection with Figure 1 is omitted within the guide body 44 above the valve member 22. The positioning of the armature 48, or the valve member 46 is taken over by the high pressure-tight guide 50 on the pressure pin 54.
  • the injector body 12 comprises the injector body 12 analogously to the variants of embodiment already discussed above in connection with FIGS. 1 and 2. This is formed symmetrically with respect to the injector axis 14 and comprises the solenoid valve 16.
  • the injector body 12 of the fuel injector 10 is acted upon by the fuel under system pressure via the high-pressure port 18.
  • the fuel is via a return port 20 in the upper Area of the fuel injector 10 is returned to a low pressure region of the fuel injection system.
  • the fuel injector 10 comprises the valve piece 22 in which the control space 24, which is acted upon by fuel under system pressure, is formed.
  • the pressure prevailing in the control chamber 24 pressure level acts on an upper end face of a preferably needle-shaped injection valve member 26.
  • the valve member 22 is screwed by means of a valve clamping nut 36 in the interior of the injector body 12 and placed against a shoulder thereof.
  • the preferably needle-shaped injection valve member 26 is guided, wherein the valve member 22, the injection valve member 26 enclosing, a closing spring 28 is supported. This is, supported by the system pressure prevailing in the control chamber, the preferably needle-shaped injection valve member 26 in its running at the combustion chamber end of the fuel injector 10 - in Figure 3, however, not shown - seat.
  • the valve piece 22 comprises the upper planar surface 40, in which the valve seat 42 is executed.
  • the valve seat 42 is also in the embodiment shown in Figure 3 as a flat seat, but could also be a conical seat or a ball seat or the like.
  • the valve seat 42 is located at the discharge point of the discharge channel 30 below the valve member 46.
  • the valve member 46 which is attached to the underside of the armature 48, in the high-pressure-tight guide 50 on the pressure pin 54th guided.
  • the valve needle guide 52 for positioning the valve member 46 in the guide body 44 is omitted. This function has been taken over by the integrated sleeve 80, the upper side 82 of which - as shown in FIG. 3 - has the concave contour 84, which makes possible a flow cross-section 86 for the hydraulic fluid which is essentially constant in the radial direction.
  • the magnetic valve 16 comprises the magnet group 58, the magnetic core 60 and the magnet coil 62.
  • the upper stroke stop 64 On the upper plan side of the armature 48 is the upper stroke stop 64, which is disc-shaped analogous to the embodiment of Figure 1.
  • the high-pressure volume 66 Above the valve seat 42, enclosed by the valve member 46, the high-pressure volume 66 is located when the valve member 46 is closed, which is connected to the low-pressure volume 68 when the solenoid valve 16 is opened.
  • the hydraulic connection between the low-pressure volume 68 and the valve space 70 takes place in the embodiment according to FIG. 3 via the upper side 82 of the integrated sleeve 80.
  • current discharge line 72 whose flow cross-section is characterized in the radial direction by position 86.

Landscapes

  • 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)
  • Magnetically Actuated Valves (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne une électrovanne (16) pour un injecteur de carburant (10), destinée à actionner un élément de soupape d'injection (26) en créant une décompression dans une chambre de commande (24). Cette dernière (24) est alimentée en carburant se trouvant à la pression du système. L'électrovanne (16) comprend un obturateur (46) qui ouvre ou ferme un siège de soupape (42). Entre une chambre à basse pression (68) et une chambre de soupape (70) se trouve une liaison hydraulique (72; 74, 76, 86) qui produit une force agissant sur l'obturateur (46) pour assister le mouvement respectif de ce dernier.
PCT/EP2009/051218 2008-04-02 2009-02-04 Amortissement hydraulique WO2009121647A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810000929 DE102008000929A1 (de) 2008-04-02 2008-04-02 Hydraulische Dämpfung
DE102008000929.6 2008-04-02

Publications (1)

Publication Number Publication Date
WO2009121647A1 true WO2009121647A1 (fr) 2009-10-08

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ID=40457346

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2009/051218 WO2009121647A1 (fr) 2008-04-02 2009-02-04 Amortissement hydraulique

Country Status (2)

Country Link
DE (1) DE102008000929A1 (fr)
WO (1) WO2009121647A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016209546A1 (de) * 2016-06-01 2017-12-07 Robert Bosch Gmbh Kraftstoffeinspritzventil
DE102018202107A1 (de) * 2018-02-12 2019-08-14 Robert Bosch Gmbh Elektromagnetisch betätigbares Steuerventil für einen Kraftstoffinjektor und Kraftstoffinjektor
DE102018202916A1 (de) * 2018-02-27 2019-08-29 Robert Bosch Gmbh Kraftstoffinjektor

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10052604A1 (de) * 2000-10-24 2002-05-02 Bosch Gmbh Robert Magnetventil zur Steuerung eines Einspritzventils einer Brennkraftmaschine
EP1612403A1 (fr) * 2004-06-30 2006-01-04 C.R.F. Societa' Consortile per Azioni Soupape servo pour controller l'injecteur d'un moteur à combustion interne
DE102006021741A1 (de) * 2006-05-10 2007-11-15 Robert Bosch Gmbh Kraftstoffinjektor mit druckausgeglichenem Steuerventil
DE102007018472A1 (de) * 2007-04-19 2008-10-23 Robert Bosch Gmbh Kraftstoffinjektor mit Magnetventil

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10052604A1 (de) * 2000-10-24 2002-05-02 Bosch Gmbh Robert Magnetventil zur Steuerung eines Einspritzventils einer Brennkraftmaschine
EP1612403A1 (fr) * 2004-06-30 2006-01-04 C.R.F. Societa' Consortile per Azioni Soupape servo pour controller l'injecteur d'un moteur à combustion interne
DE102006021741A1 (de) * 2006-05-10 2007-11-15 Robert Bosch Gmbh Kraftstoffinjektor mit druckausgeglichenem Steuerventil
DE102007018472A1 (de) * 2007-04-19 2008-10-23 Robert Bosch Gmbh Kraftstoffinjektor mit Magnetventil

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Publication number Publication date
DE102008000929A1 (de) 2009-10-08

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