EP2519732A1 - Vanne de régulation de débit à commande électromagnétique, en particulier destinée à réguler le débit de refoulement d'une pompe de carburant haute pression - Google Patents

Vanne de régulation de débit à commande électromagnétique, en particulier destinée à réguler le débit de refoulement d'une pompe de carburant haute pression

Info

Publication number
EP2519732A1
EP2519732A1 EP10778969A EP10778969A EP2519732A1 EP 2519732 A1 EP2519732 A1 EP 2519732A1 EP 10778969 A EP10778969 A EP 10778969A EP 10778969 A EP10778969 A EP 10778969A EP 2519732 A1 EP2519732 A1 EP 2519732A1
Authority
EP
European Patent Office
Prior art keywords
stop
armature
control valve
moving part
quantity 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.)
Granted
Application number
EP10778969A
Other languages
German (de)
English (en)
Other versions
EP2519732B1 (fr
Inventor
Winfried Eckart
Valentin Szermutzky
Ersin Dogan
Juergen Koreck
Matthias Maess
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
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 EP2519732A1 publication Critical patent/EP2519732A1/fr
Application granted granted Critical
Publication of EP2519732B1 publication Critical patent/EP2519732B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means

Definitions

  • Electromagnetically actuated quantity control valve in particular for controlling the delivery rate of a high-pressure fuel pump
  • the invention relates to an electromagnetically actuated quantity control valve according to the preamble of claim 1.
  • an armature of the electromagnet for example, with longitudinal bores in order to adjust the damping occurring during the movement of the armature can. Through such axial bores in the armature fluid, so fuel, transported from one axial side of the armature to the other side.
  • an axial bore in the armature it is also known to provide axial grooves on a peripheral wall of the armature, which also allow a fluid exchange between the two sides of the armature.
  • the invention provides an electromagnetically actuated quantity control valve according to claim 1.
  • Advantageous developments are in
  • the quantity control valve according to the invention has a in one
  • Movement direction is limited by a stop.
  • the housing section can be filled with fluid. If the anchor abuts against the stop, then there is one
  • An advantage of the invention is that during an attraction movement, i. a movement of the armature on the stop, in the area of the contact surface before the contact in connection with the fluid forms a pressure cushion, L5 which determines the speed of movement before the impact of the armature on the
  • Another advantage of the invention is evident in a peel, i. a movement of the armature away from the stop, starting from a contact 20 of the armature to the stop. In the area of the contact surface arises
  • NVH Noise, Vibration & Harshness
  • the impact delay reduces the pulsation of the pressure during the tightening movement. Also Preller, ie a multiple impact in the tightening movement by resilient properties of the components involved, 35 are minimized. A reduction of cavitation tendency is due to the time damped pressure curve and thus a slight tendency to locally suddenly occurring pressure differences achieved.
  • Venting volume which is connected to an axial channel within the armature, to the fact that during the peeling movement, a rapid refilling 20 of the volume arising in the region of the contact surface is achieved.
  • Venting volume is also advantageous in the tightening movement, since the fluid, which is located in the region of the contact surfaces, can flow off quickly.
  • a dead volume which is included in the abutment of the armature at the stop between the two contact partners and has no connection to an axial channel.
  • the dead volume shortly before the abutment of the armature against the stopper causes the fluid in the dead volume to be pinched off and thus also acts as a pressure cushion between the armature 30 and the stop.
  • venting of the two venting volumes can be guaranteed and no further axial channels with openings in both venting volumes are necessary.
  • a surface of the armature or of the stop is made non-magnetic.
  • a non-magnetic material may have a higher strength than the material of the armature or the abutment, which increases the wear resistance and thus the life of the quantity control valve.
  • Texture of a surface which is the contact surface associated, characterized by a profiling.
  • profiling can be the
  • Figure 1 is a simplified diagram of a fuel injection system of a
  • Figure 2a is a sectional view of a simplified schematic of a
  • FIG. 2b shows a sectional view of the electromagnet (without coil) of the FIGURE
  • FIG. 3a shows a sectional view according to FIG. 2a with an armature with a circular contact surface
  • Figure 3b is an axial plan view corresponding to a direction of purple on the
  • FIG. 4a shows a sectional view according to Figure 2a with a stop with a
  • Figure 4b is an axial plan view corresponding to a direction IIIb on the
  • FIG. 5a shows a sectional view according to FIG. 2a with an armature with an annular contact surface
  • Figure 5b is an axial plan view corresponding to a direction of purple on the
  • FIG. 6a shows a sectional view according to FIG. 2a with an armature with an annular contact surface
  • Figure 6b is an axial plan view corresponding to a direction of purple on the
  • FIG. 7a shows a sectional view according to FIG. 2a with an armature with an annular contact surface and a groove;
  • Figure 7b is an axial plan view corresponding to a direction of purple on the
  • FIG. 7a Anchor according to FIG. 7a;
  • Figure 8 is a sectional view of a stopper body
  • Figure 9 is a sectional view of a stop anchor
  • Figure 10a is a sectional view of a stop anchor
  • Figure 10b is an axial plan view of a stop body according to
  • FIG. 1 shows a fuel injection system 1 of an internal combustion engine in a much simplified representation.
  • a fuel tank 9 is connected via a suction line 4, a Vorforderpumpe 5 and a low-pressure line 7 with a (not explained in detail) high-pressure pump 3.
  • a high-pressure accumulator 13 (“common rail”) is connected via a high-pressure line 1 1.
  • a quantity control valve 14 with an electromagnetic actuator 15 - hereinafter referred to as an electromagnet 15 - is arranged hydraulically in the course of the low pressure line 7 between the Vorforderpumpe 5 and the high pressure pump 3.
  • Other elements, like are, like.
  • valves of the high-pressure pump 3 are not shown in the figure 1. It is understood that the quantity control valve 14 may be formed as a unit with the high-pressure pump 3. For example, an intake valve of the high-pressure pump 3 can be forcibly opened by the quantity control valve 14.
  • the pre-demand pump 5 delivers fuel from the fuel tank 9 into the low-pressure line 7.
  • the quantity control valve 14 determines the quantity of fuel supplied to the high-pressure pump 3.
  • Figure 2a shows a simplified representation of a section of
  • Quantity control valve 14, and the electromagnet 15 have a rotational symmetry about a central longitudinal axis of a housing portion 20 substantially. Shown is the substantially hollow cylindrical housing portion 20, and in this a generally markable as a moving part, displaceable in the direction of the longitudinal axis anchor 22 and fixed to the armature 22
  • the housing portion 20 is limited in the right part of the drawing by a stop 26. In one in the
  • Housing portion 20 formed and generally as a movement space
  • markable armature space 28 is located on both sides of the armature 22, a non-visible in the drawing fluid 30. Between an inner
  • the armature 22 has four axial channels 38, two of which are visible in the sectional view of FIG. 2a.
  • the channels 38 can either be designed as bores in the armature 22 or as a groove on the peripheral wall 34 of the armature 22, as shown.
  • the end face of the armature 22 is located on the stop 26 in the region of a contact surface directly.
  • the contact surface is defined in the apparatus of Figure 2a by the front surface of the armature 22 and interrupted only by the mouths of the channels 38.
  • the contact surface is generally composed of the overlapping surfaces of armature 22 and stop 26.
  • the individual surfaces can in the
  • the armature 22 is moved together with the valve element 24 in the drawing to the right, which corresponds to the tightening movement. This is symbolized by an arrow 42.
  • the tightening movement is characterized in that the moving part, here the armature 22, on a non-movable part, here the
  • Stop 26 too moved. After concern of the anchor 22 on the stop 26, the armature 22 is moved away from the stop 26 or pulled away. This is the stripping movement. An opening or closing of the valve is not meant with the tightening or Abziehdoch.
  • the total area of the armature 22 on the front side, that is to say on the side facing the stop 26, corresponds to the plan view surface from the direction IIIa.
  • the plan view surface takes neither the mouths of the axial channels 38 nor the annular gap 36.
  • the total area is thus defined by a plan view surface from the direction of the opposite contact partner, here the armature 22 or the stopper 26.
  • Anchor space 28 steadily reduced.
  • the existing in the section 44 fluid 30 is displaced.
  • the fluid 30 flows out of this section 44 in accordance with the arrows 46 drawn.
  • Quetsch free means a hindrance to the displacement of the fluid 30. This is indicated in Figure 2a by double arrows 48. With the squeezing effect, an impact damping of the armature 22 is made possible. That the armature 22 can fly at high speed on the stop 26 and the impact of the armature 22 on the stop 26 is damped by the crushing effect and a pressure pad resulting therefrom.
  • the crushing effect depends on the contact surface between anchor 22 and stop 26.
  • the pressure pad extends in the illustrated in Figure 2a quantity control valve 14 corresponding to the illustrated double arrows 48 between the overlapping surfaces of the armature 22 and the
  • Anchor 22 and the stopper 26 The volume is filled with the fluid 30 via the axial channels 38 corresponding to the arrows 47.
  • a so-called hydraulic bonding may occur, which is the
  • FIG. 3a shows a section of the quantity control valve L5 14 with an electromagnet 15 in a simplified representation, following the representation principle of Figure 2a.
  • the armature 22 in this case has a cylindrical projection 62 with a circular surface 60.
  • the circular surface 60 defines the contact surface.
  • the surface 60 is smaller than the total area of the armature 22.
  • the material of one of the contact surface forming surfaces of the armature 22 or the stopper 26 is made non-magnetic. This can be done for example by a chrome plating, which also represents a wear-resistant surface.
  • the surface 60 in contrast to Figure 3a also have a different shape, in which case the opposite stop 26 has a corresponding, the shape of the surface 60 receiving shape.
  • the surface 60 may have a concave shape and the stop in the corresponding area may have a convex shape.
  • the surface 60 may be configured such that when a gap between the armature 22 and the stop 26 is present. For example, if a radially outwardly increasing distance from the surface 35 60 and stop 26 is provided in the region of the contact surface, the gap is created radially outwards. This gap allows fluid from a radial outside the contact surface lying in the area of the volume
  • the surface 60 may be characterized by a profiling. This can be designed differently. For example, a profile in the form of concentric circles makes it difficult for the fluid 30 to flow in the radial direction during the application and removal movement. This means that compared to a smooth surface during the tightening movement
  • FIG. 3b shows the axial plan view of the armature 22 corresponding to the direction lilac in FIG. 3a. For graphic reasons, only the upper half of the armature 22 is shown. The lower half, not drawn, is mirror-symmetrical. In FIG. 3b, the axial channels 38 and the cylindrical projection 62 with the circular surface 60 can be seen. Furthermore, one half of the double arrow 48 can be seen, which is the
  • Pressure pad represents.
  • the peripheral wall 34 limits the anchor 22.
  • the operating situation in FIG. 3 a is as follows: According to the operating situation in FIG. 2 a, the tightening movement, the armature 22 is moved to the right with a valve element 24 corresponding to an arrow 42 in the drawing. The volume of the portion 44 of the armature space 28 is steadily reduced and the fluid flows in accordance with arrows 46 from the
  • the crushing effect arises between the circular surface 60 and the overlapping part of the surface of the stop 26.
  • the crushing effect creates a pressure pad according to the double arrow 48 and an impact damping of the armature 22 is ensured. Because the surface 60 is smaller than the total area of the armature 22, this results
  • Pressure pad not in the area of the total surface of the armature 22, but only in the area of the smaller contact surface.
  • FIG. 4a The sectional view of Figure 4a shows a section of the quantity control valve 14 in a simplified representation, following the representation principle of Figure 25 2a.
  • the stop 26 has a cylindrical projection 62 with a
  • the circular surface 60 is smaller than the total area of the abutment 26.
  • the contact area decreases in comparison to FIG. 2a.
  • Peripheral wall 32 of the housing portion 20 limits the plan view shown
  • FIG. 4a substantially corresponds to that of FIG. 3a.
  • a pull-off movement, not shown, essentially corresponds to the explanations regarding FIGS. 3a and 3b.
  • the cylindrical projection 62 and thus the circular contact surface 60 are formed on the armature 22 in FIGS. 3a and 3b, and on the stop 26 in FIGS. 4a and 4b.
  • the contact surface and thus the pressure pad can, according to the double arrows 48 of the corresponding figures 3a to 4b, that is also achieved by a correspondingly reversed profiling of the armature 22 and the stopper 26.
  • the following exemplary embodiments are therefore to be understood as meaning that an approximately equivalent function with respect to the contact surfaces and the pressure pad can also be achieved by a correspondingly inverted shape or profiling of the opposing contact partners. When profiling a desired ventilation through the axial channels 38 is also to be considered.
  • FIG. 5a shows in a simplified representation a detail of the quantity control valve 14 with an electromagnet 15.
  • the armature 22 has one
  • hollow cylindrical projection 64 with an annular surface 61, wherein axial channels 38 are radially outside of the hollow cylindrical projection 64.
  • the annular surface 61 is smaller than the total area of the armature 22.
  • the contact area of FIG. 5a is smaller in comparison to the contact area in FIG. 3a, assuming the same circular outside diameter of the cylindrical projection 62 in FIG. 3a and the hollow cylindrical projection 64 in FIG. 5a.
  • FIG. 5b shows the axial plan view of the armature 22 corresponding to a direction lilac according to FIG. 5a with the hollow-cylindrical projection 64, the annular surface 61 and the dead volume 66.
  • the armature 22 is bounded by the peripheral wall 34 and further includes the axial channels 38.
  • the arrows 48 represent the pressure pad.
  • the operating situation in FIG. 5a essentially corresponds to that of FIG. 2a.
  • the fluid 30, which is located in the dead volume 66 is closed by the venting volume 65 located radially outside 5.
  • the fluid 30 in the dead volume acts as a pressure pad, resulting in a similar effect, as in a circular surface 60 of Figure 3a and 3b. This means that in this case the effective pressure pad surface is greater than the contact surface.
  • a pull-off movement essentially corresponds to the
  • FIG. 6a shows, following the representation principle of Figure 2a, in a simplified representation of a section of the quantity control valve 14 with an electromagnet 15.
  • the armature 22 in this case has a hollow cylindrical projection 64 with an annular surface 61, wherein the axial channels 38th radially inside the hollow cylindrical projection
  • the annular surface 61 is smaller than the total area of the armature 22.
  • FIG. 6b the axial plan view of the armature 22 corresponding to a direction lil to the figure 6a with the hollow cylindrical projection 64 and the annular surface 61 can be seen.
  • the armature 22 is bounded by a peripheral wall 34 and further includes the axial channels 38 radially inwardly of the hollow cylindrical projection 64.
  • the arrows 48 represent the pressure pad.
  • FIG. 6a The operating situation in FIG. 6a is as follows: Due to the movement of the armature 22 in the direction of the arrow 42, a pressure cushion according to the double arrows 48 forms shortly before the abutment of the armature 22 against the stop 26. In the radially inside of the hollow cylindrical projection 64 lying mouths 35 of the axial channels 38 exists within the annular surface 61 a
  • Vent volume 65 The armature 22 has no dead volume 66 as in Figure 5a and 5b and the fluid 30 may be radially inside the hollow cylindrical
  • Projection 64 flow through the axial channels 38. Since the annular surface 61 is closed with the annular gap 36, the fluid 30 can flow when applying the armature 22 to the stop 26 substantially only in a direction 5 and that radially inwardly.
  • the design of the armature 22 means that a filling of the volume, which arises in the removal movement in the region of the annular surface 61, by the fluid 30 L0 occurs, which is radially within the hollow cylindrical projection 64, ie in the vent volume 65, is located.
  • the vent volume 65 is filled via the channels 38.
  • FIG. 7a shows a representation similar to that of L5 Figure 5a, but with additional grooves 68 in the hollow cylindrical projection
  • the annular surface 61 is thus interrupted by the radial grooves 68.
  • the armature 22 has only two axial channels 38 in this case.
  • the annular surface 61 is smaller than the
  • FIG. 7b shows the axial plan view of the armature 22 corresponding to the direction lil to that of FIG. 7a with the hollow cylindrical projection 64, the interrupted annular surface 61 and the radial groove 68.
  • the armature 22 is bounded by the peripheral wall 34 and further includes the axial channels 38 radially outwardly of the hollow cylindrical projection 64.
  • the double arrows 48 represent the pressure pad.
  • the arrow 67 in FIG. 7b indicates how the fluid 30 moves out of the first vent volume 65 into the second vent volume 65 during the tightening movement of the armature 22 and drains off directly via the axial channel 38.
  • the resulting volume in the area of the annular contact surface 61 fills radially from two directions: on the one hand radially from the outside through the second
  • Figure 8 shows a simplified representation of a section of
  • Quantity control valve 14 Shown is the housing portion 20 and in this the armature 22, connected to the valve element 24 as in Figure 2a. Furthermore, a fixed to the housing portion 20 stop body 73 is shown with a stop 27. The contact area between the armature 22 and stop 27 according to the arrows 48 is smaller than the total area of the armature 22.
  • a pull-off movement of the valve element 24 with the armature 22 is characterized in that the armature 22 moves in the direction of the arrow 43 toward the stop 26. Between the armature 22 and the stopper body 73, the pressure pad according to the double arrows 48 builds up before an impact or concern of the armature 22. In this case, the fluid 30 can flow off via the vent volume 65 and the channels 38 in accordance with the arrows 46.
  • FIG. 9 shows a section of a quantity control valve 14 with two
  • Valve element 24 firmly connected stop anchor 72 serve.
  • Stop anchor 72 is movable in the housing portion 20 along the longitudinal axis.
  • the valve member 24 is connected in a manner not shown with the armature 22, wherein the armature 22 is located on the right side of FIG 9.
  • the annular contact surface between the stop anchor 72 and the stop 26 according to the arrows 48 is smaller by the venting volumes 65 in the stopper body 73 than the total area of the stop anchor
  • the operating situation in FIG. 9 shows the moment shortly before abutment of the stop anchor 72 against the stop 26, i. the dressing movement.
  • a pressure pad according to the double arrows 48 formed between the overlapping surfaces of the stop anchor 72 and the stopper 26 and the stopper body 73 and the fluid 30 is on the
  • Stop 26 opposite to the arrow 42 has the result that in the region of the contact surface resulting volume between stop anchor 72 and
  • Stop 26 is filled with the fluid 30 from the venting volumes 65.
  • 10a shows a simplified representation of a section of the quantity control valve 14, or the electromagnet 15. Shown is the housing portion 20, and in this a longitudinal axis along the slidable stop anchor 72 with a peripheral wall 74.
  • Stop anchor 72 is fixedly connected to the valve element 24.
  • Valve element 24 is guided radially in the stationary stop body 73.
  • An inner circumferential wall 78 of the stopper body 73 defines with an outer peripheral wall 80 of the valve element 24 a guide gap 79 for guiding the valve element 24.
  • the guide gap is shown exaggeratedly large.
  • the stopper body 73 is characterized in that it in a direction purple, ie in the direction of the stop armature 72, a conical
  • the conical diameter jump 82 corresponds to an enlargement of the inner diameter in the direction of purple starting from the peripheral wall 78 and continues until the stop 26. Furthermore, the stop body 73 on the stop armature 72 side facing a groove 68th
  • the groove 68 extends from the diameter jump 82 in radial
  • the groove 68 connects the vent volume 65 within the diameter jump 82 with the armature space 28.
  • Contact area is smaller than the total area of the armature 22.
  • valve element 24 to see.
  • the radial bearing of the valve element 24 is shown with the limited by the peripheral walls 78 and 79 guide gap 79. Radially starting from the peripheral wall 78 via the diameter jump 82 of the stop body 73 goes over into the stop 26. Double arrows 48 represent the pressure pad and show with the indicated peripheral wall
  • FIGS. 10a and 10b The operating situation in FIGS. 10a and 10b is as follows:
  • the stop anchor 72 moves in the form of a tightening movement with the
  • valve element 24 to the stop 26 and thus the valve body 73 to.
  • the fluid 30 is interrupted by the groove 68, annular pressure pad corresponding to the contact surface and the double arrows 48.
  • the broken, annular contact surface is reduced by the diameter jump 82 and
  • Guide gap 79 can flow substantially no fluid 30.
  • a resulting volume in the area of the interrupted, annular contact surface is filled radially from the inside and from the outside by the venting volumes 65 with the fluid 30.
  • the fluid 30 flows over the armature space 28 radially from the outside. Furthermore, the fluid 30 flows over the inside diameter jump 82 and the groove 68 to.

Abstract

L'invention concerne une vanne de régulation de débit à commande électromagnétique, en particulier destinée à réguler le débit de refoulement d'une pompe de carburant haute pression. La vanne de régulation de débit comprend un espace de mouvement (28) pouvant être rempli d'un fluide (30) et dans lequel est placé un élément mobile (22) d'un dispositif de commande électromagnétique, ainsi qu'une butée (26). Lorsque l'élément mobile (22) repose contre la butée (26), on observe une surface de contact entre l'élément de contact (22) et la butée (26). La surface de contact est déterminée par une surface de l'élément mobile (22) et une surface de la butée (26). La surface de contact est plus petite que la surface totale de l'élément mobile (22) ou de la butée (26).
EP10778969.5A 2009-12-29 2010-11-04 Vanne de controle du debit de commande electrique, destinee en particulier a commander le debit d'une pompe haute pression a carburant Active EP2519732B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009055356A DE102009055356A1 (de) 2009-12-29 2009-12-29 Elektromagnetisch betätigtes Mengensteuerventil, insbesondere zur Steuerung der Fördermenge einer Kraftstoff-Hochdruckpumpe
PCT/EP2010/066797 WO2011079989A1 (fr) 2009-12-29 2010-11-04 Vanne de régulation de débit à commande électromagnétique, en particulier destinée à réguler le débit de refoulement d'une pompe de carburant haute pression

Publications (2)

Publication Number Publication Date
EP2519732A1 true EP2519732A1 (fr) 2012-11-07
EP2519732B1 EP2519732B1 (fr) 2018-10-10

Family

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Family Applications (1)

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EP10778969.5A Active EP2519732B1 (fr) 2009-12-29 2010-11-04 Vanne de controle du debit de commande electrique, destinee en particulier a commander le debit d'une pompe haute pression a carburant

Country Status (6)

Country Link
EP (1) EP2519732B1 (fr)
KR (2) KR101506475B1 (fr)
CN (1) CN102686868B (fr)
DE (1) DE102009055356A1 (fr)
ES (1) ES2704993T3 (fr)
WO (1) WO2011079989A1 (fr)

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WO2019051767A1 (fr) * 2017-09-15 2019-03-21 Robert Bosch Gmbh Injecteur de carburant et soupape de commande associée

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ES2704993T3 (es) 2019-03-21
WO2011079989A1 (fr) 2011-07-07
EP2519732B1 (fr) 2018-10-10
KR101736081B1 (ko) 2017-05-16
KR20120096934A (ko) 2012-08-31
CN102686868A (zh) 2012-09-19
KR101506475B1 (ko) 2015-03-27
CN102686868B (zh) 2015-06-17
KR20140140131A (ko) 2014-12-08
DE102009055356A1 (de) 2011-06-30

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