WO2019051767A1 - Injecteur de carburant et soupape de commande associée - Google Patents

Injecteur de carburant et soupape de commande associée Download PDF

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Publication number
WO2019051767A1
WO2019051767A1 PCT/CN2017/101867 CN2017101867W WO2019051767A1 WO 2019051767 A1 WO2019051767 A1 WO 2019051767A1 CN 2017101867 W CN2017101867 W CN 2017101867W WO 2019051767 A1 WO2019051767 A1 WO 2019051767A1
Authority
WO
WIPO (PCT)
Prior art keywords
bolt
control valve
armature
guiding segment
valve
Prior art date
Application number
PCT/CN2017/101867
Other languages
English (en)
Inventor
Zeynep SERAN
Emre TERZI
Holger Rapp
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
Priority to PCT/CN2017/101867 priority Critical patent/WO2019051767A1/fr
Priority to CN201780093474.7A priority patent/CN110945231B/zh
Publication of WO2019051767A1 publication Critical patent/WO2019051767A1/fr

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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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0664—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding
    • F02M51/0685—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature and the valve being allowed to move relatively to each other or not being attached to each other
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • 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
    • F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"

Definitions

  • the disclosure relates to a control valve used in a fuel injector and a fuel injector, in particular a common rail fuel injector, comprising such a control valve.
  • a fuel injector generally comprises a control valve and an injection valve, the fuel injection action of the injection valve being controlled by means of the switching action of the control valve between its opened and closed states.
  • Figure 1 schematically shows a partial structure of such a control valve, the control valve comprising an armature bolt 1 which is inserted through an inner bore 2a (see Figure 2) of an armature guide 2 and is slidable with respect to the armature guide 2.
  • the control valve further comprises an electromagnetic coil (not shown) which can be energized and deenergized. When the electromagnetic coil is deenergized, the armature bolt 1, under the action of a pushing force from a spring (not shown) , pushes a ball type valve element 3 against a valve seat 4 to close a valve hole 5 formed in the valve seat 4.
  • An object of the disclosure is to suppress the hydraulic sticking between the armature bolt and the armature guide of a fuel injector to improve the performance of the fuel injector.
  • a control valve used in a fuel injector which comprises: a valve element and a valve seat cooperating with each other; an armature guide comprising an inner bore therethrough which is defined by an inner peripheral surface; and an armature bolt inserted through the inner bore, the armature bolt being movable forwards with respect to the armature guide to apply a pushing force on the valve element to close the control valve and being movable backwards with respect to the armature guide to release the pushing force applied on the valve element so that the control valve is opened.
  • the inner peripheral surface of the armature guide comprises a bolt guiding segment which guides the forward and backward movements of the armature bolt and a non-guiding segment which has a diameter larger than that of the bolt guiding segment.
  • the diameter of the non-guiding segment is designed to be so larger than the diameter of the bolt guiding segment that the fuel in the clearance between the non-guiding segment and the armature bolt applies no or little dragging force on the armature bolt when the armature bolt moves respective to the armature guide.
  • the diameter of the non-guiding segment is larger than that of the bolt guiding segment by at least 0.04 mm, for example, in a range of 0.04 mm to 0.2 mm, preferably 0.05 mm to 0.15 mm, and in particular, about 0.1 mm.
  • the bolt guiding segment comprises a front bolt guiding segment and a back bolt guiding segment, with the non-guiding segment located axially between the two bolt guiding segments.
  • transition portions between the non-guiding segment and the front and back bolt guiding segments form front and back tapered surfaces respectively, each tapered surface defining a taper angle with the bolt guiding segment.
  • the taper angle of the back tapered surface is smaller than the taper angle of the front tapered surface.
  • the taper angle of the back tapered surface is in a range of 10 degrees to 40 degrees, such as about 30 degrees
  • the taper angle of the front tapered surface is in a range of 40 degrees to 75 degrees, such as about 45 degrees.
  • the bolt guiding segment comprises a single bolt guiding segment with a non-guiding segment axially neighboring it or with two non-guiding segments located axially opposite of it.
  • the bolt guiding segment comprises three or more bolt guiding segments which are separated axially by a corresponding non-guiding segment therebetween.
  • the axial length of the non-guiding segment or the total axial length of all the non-guiding segments is larger than that of the single bolt guiding segment or the total axial length of all the bolt guiding segments.
  • the armature guide comprises a flange portion having a front surface and a back surface and a tubular portion extending backwards from a central portion of the back surface
  • the armature bolt comprises a cylindrical main body which is inserted through the inner bore and a circular flange formed around the main body adjacent to a front end of the main body, the circular flange being pushed against the front surface of the flange portion in the opened state of the control valve and being separated from the front surface of the flange portion in the closed state of the control valve.
  • the flange portion of the armature guide comprises a circular recess recessed from the front surface, with one or more through holes extending from the bottom of the circular recess to the back surface.
  • the circular recess is delimited by an inner periphery and an outer periphery, the inner periphery having a diameter smaller than the diameter of the circular flange, and the outer periphery having a diameter larger than the diameter of the circular flange.
  • the disclosure in another aspect provides a fuel injector, in particular a common rail fuel injector, comprising a control valve as described above, and an injection valve assembled to be in combination with the control valve.
  • the injection valve performs fuel injection in responsive to the opened/closed state of the control valve.
  • the inner bore of the armature guide comprises a bolt guiding segment and a non-guiding segment, so the guiding area of the armature guide for guiding the armature bolt is reduced with respect to that of the prior art, and thus hydraulic sticking between the armature bolt and the armature guide is suppressed. Desired closing time of the control valve and expected fuel injection quantity of the fuel injector can be achieved. Further, closing behavior of the armature bolt becomes more stable, and deviation of fuel injection quantity from shot to shot can be reduced.
  • Figure 1 is a partial schematic sectional view of a control valve used in a fuel injector according to prior art
  • Figure 2 is a sectional view of an armature guide of the control valve shown in Figure 1;
  • Figure 3 is a partial schematic sectional view of a fuel injector according to a possible embodiment of the disclosure.
  • Figure 4 is a sectional view of an armature guide of a control valve of the fuel injector shown in Figure 3;
  • Figures 5 and 6 are top and bottom views respectively of the armature guide shown in Figure 4;
  • Figure 7 is an enlarged partial sectional view of the armature guide shown in Figure 4 for illustrating some important dimensions of the armature guide.
  • Figure 8 is a diagram showing the comparison between the fuel injection amounts of the fuel injector according to prior art and that of the disclosure.
  • Figure 3 shows in partial view a fuel injector for injecting fuel into an engine according to a possible embodiment of the disclosure, in particular a fuel injector used in a common rail diesel injection system.
  • the fuel injector comprises a control valve and an injection valve assembled together, for example, assembled in a common fuel injector casing 100 (only schematically illustrated in Figure 3) .
  • the improvements made in the disclosure relate mainly to the control valve, and so Figure 3 mainly shows corresponding portions of the control valve.
  • the injection valve is assembled to a front side (lower side in Figure 3) of the control valve, facing towards the engine (not shown) .
  • the control valve is switchable between an opened state and a closed state, and the fuel injection actions (shots) of the injection valve are controlled by means of switching the control valve between the opened and closed states of the control valve.
  • the control valve comprises an armature bolt 1 which has a main body 1a substantially in the form of a cylinder extending in an axial direction and a circular flange 1b formed around the main body 1a adjacent to a front end (lower end in Figure 3) of the main body 1a and extending radially outwards.
  • the control valve further comprises an armature guide 2 (see Figures 4-7 for details) which comprises a flange portion 21 having a first front surface 21a and a second back surface 21b and a tubular portion 22 extending from a central portion of the back surface 21b of the flange portion 21 in the axial direction perpendicular to the flange portion 21.
  • the armature guide 2 defines an inner bore 2a extending axially through the flange portion 21 and the tubular portion 22.
  • the flange portion 21 is formed with a circular recess 21c recessed from its front surface 21a, a circular protrusion 21d protruded axially from the back surface 21b, and one or more (two in the illustrated embodiment) through holes 21e extending axially from the bottom of the circular recess 21c to the back surface 21b.
  • the main body 1a of the armature bolt 1 is inserted through the inner bore 2a of the armature guide 2 and is slidable to reciprocate with respect to the armature guide 2, with the circular flange 1b located adjacent to the front surface 21a of the flange portion 21 of the armature guide 2.
  • the front end of the main body 1a of the armature bolt 1 is configured for pushing a ball type valve element 3 against a valve seat 4 to close a valve hole 5 formed in the valve seat 4.
  • a holding block 6 is disposed axially between the front end of the main body 1a and the valve element 3. The holding block 6 is adhered to the front end of the main body 1a and is formed with an accommodating recess for accommodating substantially half of the valve element 3 therein.
  • the valve hole 5 extends axially in the valve seat 4 and is opened into an injection chamber 7 formed in the valve seat 4.
  • An injection needle 8 is inserted and slidable in the injection chamber 7.
  • the injection chamber 7 and the corresponding portion of the valve seat 4, as well as the injection needle 8, belong to the injection valve.
  • An intermediate ring 9 is clamped axially between the flange portion 21 of the armature guide 2 and the valve seat 4.
  • the thickness of the intermediate ring 9 in the axial direction is selected for adjusting the reciprocating stroke of the armature bolt 1.
  • An assembling nut 10 is disposed behind the flange portion 21 of the armature guide 2 and is engaged in the fuel injector casing 100 by screw threads to be clamped onto the circular protrusion 21d of the armature guide 2, so that the armature guide 2, the intermediate ring 9 and the valve seat 4 are fixed by the assembling nut 10 in the fuel injector casing 100.
  • An armature plate 11 is disposed behind the armature bolt 1.
  • the armature plate 11 comprises a tubular portion 11a facing towards the tubular portion 22 of the armature guide 2 and a flange portion 11b extending out from a back end part of the tubular portion 11a.
  • the armature plate 11 defines an inner bore that is aligned with the inner bore 2a of the armature guide 2 and is also inserted through by the main body 1a of the armature bolt 1.
  • a back end part of the main body 1a of the armature bolt 1 is exposed from a back surface of the flange portion 11b, and a compressive spring 12 is disposed between the flange portion 21 of the armature guide 2 and the flange portion 11b of the armature plate 11 around the tubular portion 22 and the tubular portion 11a.
  • the outer periphery of the back end part of the main body 1a is formed with a circular recess for putting a clamping clip 13 therein for retaining the armature plate 11 around the main body 1a of the armature bolt 1.
  • a returning spring 14 is disposed behind the main body 1a of the armature bolt 1 to apply an axial pushing force on the armature bolt 1 in a direction towards the valve seat 4.
  • An electromagnet core 15 is arranged behind the armature plate 11 and includes therein an electromagnetic coil 16 for generating an electromagnetic attraction force on the armature plate 11.
  • the injection valve injects fuel by means of the reciprocating of the injection needle 8 responsive to the opened and closed states of the control valve.
  • the electromagnetic coil 16 is deenergized so that the control valve is in the closed state shown in Figure 3, fuel (for example, coming from a common rail) supplied into the injection chamber 7 is under a pressure accumulation state, and the valve needle 8 closes the injection valve. Then, the electromagnetic coil 16 is energized so that the control valve comes into the opened state, so a portion of the fuel in the injection chamber 7 flows into the control valve via the valve hole 5. This results in lowering down of the pressure of the fuel behind the valve needle 8, so that a pressure difference is established between front and back sides of the valve needle 8.
  • valve needle 8 moves backwards to open the injection valve, so a fuel injection action (shot) is performed. Then, the electromagnetic coil 16 is deenergized again so that the control valve comes to the closed state again, and thus the injection valve is switched to the pressure accumulation state until the fuel pressures at the front and back sides of the valve needle 8 become the same level. Now the valve needle 8 closes the injection valve under a returning element for the valve needle 8. Then, the next fuel injection action (shot) will be performed in responsive to the energizing of the electromagnetic coil 16 again.
  • the inner peripheral surface (which delimits the inner bore 2a) of the tubular portion 22 of the armature guide 2 comprises cylindrical bolt guiding segments 22a near the front and back ends of the armature guide 2 respectively and a cylindrical non-guiding segment 22b axially between the bolt guiding segments 22a and being coaxial with the bolt guiding segments 22a.
  • the bolt guiding segments 22a each have a nominal diameter equal to the outer diameter of the main body 1a of the armature bolt 1, but with a proper tolerance so that clearance fit is formed between the bolt guiding segments 22a and the main body 1a.
  • the non-guiding segment 22b has a nominal diameter larger than the outer diameter of the main body 1a of the armature bolt 1.
  • the outer periphery of the back end portion of the tubular portion 22 is formed as a thickening portion 22c for increasing stability in supporting the tubular portion 11a of the armature plate 11 in the closed state of the control valve.
  • the non-guiding segment 22b has a diameter larger than the diameter of the bolt guiding segments 22a by 2 ⁇ R. That is to say, the circumferential periphery of the non-guiding segment 22b is offset from the circumferential periphery of the bolt guiding segments 22a radially outwards by a distance ⁇ R.
  • the distance ⁇ R is large enough so that, when the main body 1a slides in the inner bore 2a, the fuel within the distance ⁇ R applies no or little dragging force on the main body 1a and thus the hydraulic sticking is suppressed.
  • the distance ⁇ R depends on the diameter of the bolt guiding segments 22a and may be in general at least 0.02 mm, for example, in a range of 0.02 mm to 0.1 mm, preferably 0.025 mm to 0.075 mm, and in particular, about 0.05 mm.
  • the axial length L of the non-guiding segment 22b may be as large as possible to increase the hydraulic sticking suppressing effect.
  • the axial length L of the non-guiding segment 22b is larger than the total axial length of the bolt guiding segments 22a.
  • transition portions between the non-guiding segment 22b and the bolt guiding segments 22a are in the form of tapered surfaces, each tapered surface forming a taper angle ⁇ 1 or ⁇ 2 between the tapered surface and a corresponding bolt guiding segment 22a.
  • the front and back taper angles may be different with each other.
  • the back taper angle ⁇ 2 (for example, 10 degrees to 40 degrees, such as about 30 degrees) is smaller than the front taper angle ⁇ 1 (for example, 40 degrees to 75 degrees, such as about 45 degrees) so that the fuel is easy to flow into the distance ⁇ R from the back end of the armature guide 2 during the closing stroke of the armature bolt 1.
  • hydraulic sticking also occurs between the front surface 21a of the flange portion 21 of the armature guide 2 and the back surface of the flange portion 1b of the armature bolt 1 during the closing stroke of the armature bolt 1.
  • the radially inner periphery that defines the circular recess 21c shall have a diameter D1 (marked in Figure 6) that is smaller than the outer diameter of the flange portion 1b, and the radially outer periphery that defines the circular recess 21c shall have a diameter D2 (marked in Figure 6) that is larger than the outer diameter of the flange portion 1b.
  • D1 marked in Figure 6
  • D2 marked in Figure 6
  • the circular recess 21c shall has an axial depth T that is large enough for gathering fuel that will flow into the gap between the front surface 21a of the flange portion 21 and the back surface of the flange portion 1b in the closing stroke of the armature bolt 1. Further, the radially outer and inner peripheries of the circular recess 21c each form a rounded corner 21r with the bottom of the circular recess 21c.
  • Figure 8 is a diagram showing the comparison by experiments between fuel injection performance of fuel injector according to prior art shown in Figure 1 and that of the disclosure.
  • the horizontal axis represents fuel injection quantity and the vertical axis represents the total number of shots corresponding to each fuel injection quantity.
  • Curve S1 is the result according to prior art
  • Curve S2 is the result according to the disclosure. It can be seen that the peak point Peak2 (representing peak number of shots) of Curve S2 is higher than the peak point Peak1 of the Curve S1, the fuel injection quantity Q1 at the peak point Peak1 of the Curve S1 is larger than the fuel injection quantity Q2 at the peak point Peak2 of Curve S2, and the distribution band of Curve S2 is narrower than that of the Curve S1. It can be seen from the results that the disclosure may contribute to more stable and accurate fuel injection.
  • the inner peripheral surface that defines the inner bore 2a of the armature guide 2 may comprise three or more bolt guiding segments 22a which are separated in the axial direction by non-guiding segments 22b therebetween.
  • the inner peripheral surface that defines the inner bore 2a of the armature guide 2 may comprise only one bolt guiding segment 22a with one non-guiding segment 22b neighboring it or with two non-guiding segments 22b located axially opposite of it.
  • the armature guide of the disclosure comprises a bolt guiding segment and an axially neighboring non-guiding segment, so the guiding area of the armature guide for guiding the armature bolt is reduced with respect to that of the prior art and thus hydraulic sticking between the armature bolt and the armature guide is suppressed. Desired closing time of the control valve and expected fuel injection quantity of the fuel injector can be achieved. Further, closing behavior of the armature bolt becomes more stable, and deviation of fuel injection quantity from shot to shot can be reduced.

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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)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne une soupape de commande utilisée dans un injecteur de carburant comprenant : un élément de soupape (3) et un siège de soupape (4) coopérant l'un avec l'autre ; un guide d'armature (2) comprenant un trou interne (2a) à travers celui-ci qui est défini par une surface périphérique interne ; et un boulon d'armature (1) inséré à travers le trou interne (2a), le boulon d'armature (1) étant mobile vers l'avant par rapport au guide d'armature (2) pour appliquer une force de poussée sur l'élément de soupape (3) pour fermer la soupape de commande et étant mobile vers l'arrière par rapport au guide d'armature (2) pour libérer la force de poussée appliquée sur l'élément de soupape (3) de sorte que la soupape de commande est ouverte ; la surface périphérique interne du guide d'armature (2) comprenant un segment de guidage de boulon (22a) qui guide les mouvements vers l'avant et vers l'arrière du boulon d'armature (1) et un segment de non-guidage (22b) qui présente un diamètre supérieur à celui du segment de guidage de boulon (22a).
PCT/CN2017/101867 2017-09-15 2017-09-15 Injecteur de carburant et soupape de commande associée WO2019051767A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/CN2017/101867 WO2019051767A1 (fr) 2017-09-15 2017-09-15 Injecteur de carburant et soupape de commande associée
CN201780093474.7A CN110945231B (zh) 2017-09-15 2017-09-15 燃油喷射器及其控制阀

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/CN2017/101867 WO2019051767A1 (fr) 2017-09-15 2017-09-15 Injecteur de carburant et soupape de commande associée

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WO2019051767A1 true WO2019051767A1 (fr) 2019-03-21

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101545431A (zh) * 2008-03-27 2009-09-30 株式会社电装 喷射器
EP2365205A1 (fr) * 2010-03-03 2011-09-14 Continental Automotive GmbH Soupape d'injection
CN203892092U (zh) * 2014-05-29 2014-10-22 哈尔滨工程大学 蓄压限流式电磁控制喷油器
CN104265530A (zh) * 2014-07-31 2015-01-07 中国第一汽车股份有限公司无锡油泵油嘴研究所 电控内燃机喷射器控制阀
EP3009663A1 (fr) * 2014-10-15 2016-04-20 Continental Automotive GmbH Ensemble de soupape et injecteur de fluide
CN105756820A (zh) * 2016-04-21 2016-07-13 哈尔滨工程大学 组合式增压电磁喷油-非增压压电喷气混合燃料喷射装置
CN106050501A (zh) * 2016-08-02 2016-10-26 成都威特电喷有限责任公司 高可靠性电控高压燃油喷射装置

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009055356A1 (de) * 2009-12-29 2011-06-30 Robert Bosch GmbH, 70469 Elektromagnetisch betätigtes Mengensteuerventil, insbesondere zur Steuerung der Fördermenge einer Kraftstoff-Hochdruckpumpe
JP6087210B2 (ja) * 2013-05-24 2017-03-01 日立オートモティブシステムズ株式会社 燃料噴射弁

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101545431A (zh) * 2008-03-27 2009-09-30 株式会社电装 喷射器
EP2365205A1 (fr) * 2010-03-03 2011-09-14 Continental Automotive GmbH Soupape d'injection
CN203892092U (zh) * 2014-05-29 2014-10-22 哈尔滨工程大学 蓄压限流式电磁控制喷油器
CN104265530A (zh) * 2014-07-31 2015-01-07 中国第一汽车股份有限公司无锡油泵油嘴研究所 电控内燃机喷射器控制阀
EP3009663A1 (fr) * 2014-10-15 2016-04-20 Continental Automotive GmbH Ensemble de soupape et injecteur de fluide
CN105756820A (zh) * 2016-04-21 2016-07-13 哈尔滨工程大学 组合式增压电磁喷油-非增压压电喷气混合燃料喷射装置
CN106050501A (zh) * 2016-08-02 2016-10-26 成都威特电喷有限责任公司 高可靠性电控高压燃油喷射装置

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CN110945231B (zh) 2021-09-14
CN110945231A (zh) 2020-03-31

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