WO2012102635A1 - Soupape électromagnétique pour injecteur de carburant à commande hydraulique - Google Patents

Soupape électromagnétique pour injecteur de carburant à commande hydraulique Download PDF

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Publication number
WO2012102635A1
WO2012102635A1 PCT/RU2011/000037 RU2011000037W WO2012102635A1 WO 2012102635 A1 WO2012102635 A1 WO 2012102635A1 RU 2011000037 W RU2011000037 W RU 2011000037W WO 2012102635 A1 WO2012102635 A1 WO 2012102635A1
Authority
WO
WIPO (PCT)
Prior art keywords
armature
pusher
electromagnetic valve
elastic
magnetic circuit
Prior art date
Application number
PCT/RU2011/000037
Other languages
English (en)
Russian (ru)
Inventor
Борис Константинович ЗУЕВ
Original Assignee
Zuev Boris Konstantinovich
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 Zuev Boris Konstantinovich filed Critical Zuev Boris Konstantinovich
Priority to PCT/RU2011/000037 priority Critical patent/WO2012102635A1/fr
Priority to RU2013134929/06A priority patent/RU2541483C1/ru
Publication of WO2012102635A1 publication Critical patent/WO2012102635A1/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
    • F02M63/0014—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
    • 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
    • F02M63/0075—Stop members in valves, e.g. plates or disks limiting the movement of armature, valve or spring
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/088—Electromagnets; Actuators including electromagnets with armatures provided with means for absorbing shocks

Definitions

  • the invention relates to engine building, in particular to fuel-spraying equipment for internal combustion engines.
  • High pressure hydraulically controlled fuel nozzles typically comprise a control chamber with an outlet channel closed by a shut-off element by means of a pre-loaded main spring and opened by exciting an electromagnet to move the armature to overcome the force exerted by the spring.
  • the armature is rigidly connected to a rod sliding inside a fixed guide.
  • the impact of the locking element on the valve seat creates a significant force proportional to the mass and speed of movement of the armature and the rod and inversely proportional to the duration of the impact, which is very small, and, given the hardness of the rod, ball and valve seat, leads to a significant impact when closing the channel, so moving the armature does not ensure stable operation of the nozzle.
  • a damping device is introduced into the design of the electromagnetic valve.
  • the electromagnetic valve according to the patent RU 2209337 there is a damping device interacting with the anchor and the fixed element, which works with the displacement of the fuel, which damps the transient vibrations of the armature during its dynamic movement.
  • the disadvantage of this design is the difficulty of ensuring a calibrated gap between the armature and the fixed element.
  • the control device of the high-pressure nozzle according to the patent US 6305355 is also known, in which the function of the damping device is performed by a massive body located coaxially with the armature and in contact with it from the side opposite to the electromagnet.
  • the anchor after pressing the locking element against the saddle, collides with the massive body, transmitting its momentum to it and, accordingly, preventing its possible oscillations.
  • the disadvantages of this design include the need to introduce additional elements into the design, which leads to its cost increase.
  • a common feature of all the mentioned structures with a movable armature is the presence of two guide surfaces on the rod. The first is the direction of the rod itself in a fixed sleeve fixed in the housing, the second is the direction of the movable armature along the rod. The presence of these two surfaces limits the minimum axial dimensions of the control valve.
  • the objective of the present invention is to eliminate the above disadvantages and create a simple, reliable solenoid valve for a hydraulic nozzle with reduced axial dimensions. Disclosure of invention
  • the elastic element is made in the form of an elastic disk combined with a pusher and rigidly connected with its peripheral part to the anchor with the formation of a damping cavity between the end of the elastic disk and the anchor, and the emphasis is an elastically deformable ring fixed along the periphery in the anchor on the other side of the damping cavity relative to the elastic disk.
  • the damping cavity may be in the form of a ring, an annular gap on the inner diameter of which forms the outlet section of the damping cavity.
  • the axial dimension of the slit of the exit section of the damping cavity is 0.5 to 1.5 times the stroke of the pusher.
  • a decrease in the axial size of the output section leads to an increase in the outflow velocity and, accordingly, to an increase in damping, however, the magnitude of the force transmitted from the armature to the rod increases.
  • the specified range is a compromise between the amount of damping and the pressing force of the locking element to the seat.
  • the ratio of the outer diameter of the damping cavity to the inner diameter is 1.8 - 3. Since the diameter of the outlet cross section is determined constructively, this ratio determines the area of the damping cavity. At a ratio of 1.8, it is minimal and fluid displacement requires less effort. When this ratio is increased to 3, the area of the damping cavity increases, and more force is required to displace the liquid from it, which increases the damping of the kinetic energy of the armature. Also, an increase in the diameter of the damping cavity leads to an increase in the deformation of the elastic disk of the pusher, which makes it possible to perform an elastic disk of greater thickness at the same strain value, increasing the manufacturability of its manufacture.
  • the stiffness of the thrust ring is 2 to 5 times greater than the stiffness of the elastic disk.
  • the specified range is selected from the conditions of collateral the necessary rigidity of fixing the anchor, moving under the action of the return spring, while the minimum value of the range determines the maximum lag of the armature from the pusher, and the maximum value of stiffness - the minimum lag.
  • the outer diameter of the thrust ring is equal to the diameter of the elastic disk, and the inner diameter is 1, 3 - 2 of the diameter of the pusher.
  • the specified range is selected from the condition for ensuring the necessary rigidity of the anchor moving under the action of the return spring, as well as from the condition for ensuring the necessary size of the additional damping cavity between the elastic disk and the thrust ring, and the minimum diameter determines the minimum lag of the armature from the pusher and the maximum cavity size, and maximum diameter — maximum lag and minimum cavity size.
  • FIG. 1 is a sectional view of a fuel injector comprising an electromagnetic valve according to the invention
  • FIG. 5 is a section along D-D in FIG. 1 on an enlarged scale
  • FIG. 6 is a section along EE in FIG. 1 on an enlarged scale.
  • the electromagnetic valve is located in the nozzle housing 1 and contains a magnetic circuit 2 with a winding 3 and an armature 4 mounted on the pusher 5.
  • the magnetic circuit 2 is pressed through the insulator 17 in the sleeve 18, pressed by the nut 19 through the adjusting washer 15 to the housing 1.
  • a cap 16 of non-magnetic material is mounted on its axis, protruding from this magnetic circuit 2 to a distance N (Fig. 2).
  • the voltage on the winding 3 is supplied through the contacts 20 passing through the holes in the insulator 17 (not shown) and filled with plastic in the manufacture of the pads 21.
  • the pusher 5 is installed in the hole 7 of the housing 1 with the possibility of axial movement and under the action of the spring 8 with the adjusting washer 9 presses the locking element 10 through the spacer 11 to its seat, blocking the hole 12.
  • the anchor 4 is mounted on the pusher 5 by means of an elastic disk 13, made integral with the pusher 5, and a deformable ring 6.
  • the outer diameter of the thrust ring 6 is equal to the diameter of the elastic disk 13, and the inner diameter is 1, 3 - 2 diameters of the pusher 5.
  • the stiffness of the thrust ring 6 is 2 to 5 times higher than the stiffness of the elastic disk 13. The elastic disk 13 and the deformable ring 6 are pressed against each other and fastened to the armature 4 on the periphery, in particular, crimped.
  • a bore is made in the armature 4, so that a damping cavity 14 is formed between the elastic disk 13 and the armature 4, and the deformable ring 6, which acts as a stop, is located on the other side of the damping cavity 14 with respect to the elastic disk 13 and limits the deformation of the elastic disk 13 towards the closed side magnetic circuit.
  • the damping cavity 14 has the shape of a ring, the annular gap S on the inner diameter d of which forms the output section of the damping cavity.
  • the ratio of the outer diameter D of the cavity 14 to the specified inner diameter d lies in the range from 1, 8 to 3, and the axial size of the slit S of the output section of the damping cavity 14 is 0.5 to 1.5 of the working stroke M of the pusher 5.
  • the stroke M of the pusher 5 is defined as the distance from the surface of the armature 4 facing the magnetic core 2 to the cap 16 in the pressed position of the locking element 10 to its seat.
  • This stroke M can be controlled by selecting the thickness of the adjusting washer 15 (Fig. 2), which determines the position of the magnetic circuit 2 relative to the housing 1.
  • the minimum clearance between the armature 4 and the magnetic circuit 2 is determined by the protrusion N of the specified cap 16.
  • the pusher 5 has an axial hole 22 and grooves 23 for the passage of fuel consumed for controlling the nozzle to the magnetic circuit 2 for cooling it, and then into the cavity 24 of the electromagnet.
  • the hole 25 and the grooves 26 (Fig. 1) connect the specified cavity 24 with the drain fitting 27.
  • the sealing ring 28 prevents the passage of fuel flowing from the hole 12 immediately to the drain fitting 27, if the pressure drop does not exceed the permissible. Sealing of the cavity 24 is carried out by a rubber sealing ring 29.
  • the solenoid valve described above controls the operation of an electro-hydraulic nozzle, for example, a diesel internal combustion engine, comprising a spray gun 30 connected to a hollow body 1, in which three needles 31 are installed, covering the spray holes 32.
  • the upper ends of the needles 31 in the closed state coincide with the end of the spray gun 30.
  • the needles 31 are kept from turning either by those needles 31 that are pressed against the saddle, or due to friction between the needle 31 and the pusher 33 interacting with it.
  • a bore 34 is made in the housing 1 (Fig. 4), which determines the maximum value h of raising the needles 31.
  • thickeners 35 are made on the needles 31, each of which has flat platforms 36 (Fig.
  • Each pusher 33 (Fig. 1) is affected by a locking multiplier 39, the upper part of which is under the influence of the fuel pressure in the hydraulic control chamber 40 (Fig. 2).
  • the multiplier 39 in the lower part has a thrust shoulder 41, which provides preliminary compression of the pusher 33, because the distance between the upper end of the needle 31 in its closed position and the lower end of the multiplier 39, pressed by the shoulder 41 to the end of the multiplier sleeve 42 (i.e. in the upper position), is less than the length of the pusher 33 in the free state, which ensures that the needle 31 is pressed against the saddle when lack of pressure in the system.
  • the magnitude of this compression is about 0.2 mm, which eliminates the influence of the difference in the coefficients of thermal expansion of the parts and reduces the requirements for the accuracy of their manufacture.
  • the holes 38 (Fig. 1) for supporting the pusher along the axis of action of the forces of the needle 31 and the multiplier 39 are made inclined with great accuracy on a wire EDM machine.
  • Fuel into the hydraulic control chamber 40 enters through the inlet fitting 43 (Fig. 1), the holes in the housing 1, the tubular pin 44 and the throttle hole 45 (Fig. 2) and can be ejected from it through the hole 12, by opening which is controlled by a solenoid valve.
  • the solenoid valve in the hydraulic fuel injector operates as follows.
  • the armature 4 (Fig. 2) is attracted to the magnetic circuit 2, compressing the spring 8 through the thrust ring 6 and releasing the locking element 10.
  • the force of impact of the armature 4 on the end face of the cap 16 is damped by displacing the liquid from the gap between the armature 4 and the magnetic circuit 2, reducing the magnitude of the rebound during the collision of the armature 4 with the end face of the cap 16, and a significant area of the colliding surfaces provides the necessary life of the nozzle.
  • the release of the locking element 10 leads to a drop in pressure in the hydraulic control chamber 40, and the multiplier 39 under the action of the elastic forces of the pusher 33 (Fig. 1) and the pressure of the fuel acting on the differential platform of the needle 31 rises to the contact of the shoulder 41 with the multiplier sleeve 42.
  • the anchor 4 (Fig. 2), under the action of the spring 8, breaks away from the magnetic circuit 2 through the thrust ring 6 and, moving together with the pusher 5 and the spacer 11, puts the locking element 10 into the valve seat.
  • the impact force of the locking element 10 on the saddle decreases approximately by a factor of many times, how many times the mass of the pusher 5 is less than the total mass moving from the mass of the pusher 5, the armature 4 and the thrust ring 6.
  • the stress decreases by the collision of the locking element 10 and its seat, reducing their wear, and the energy of the rebound of the locking element 10 is reduced by the same amount.
  • the armature 4 together with the thrust ring 6 continues to move by inertia towards the opening of the magnetic circuit, deforming the elastic disk 13.
  • fuel is displaced from the cavity 14 (Fig. 3), damping most of the kinetic energy of the armature 4 and the thrust ring 6 and reducing the amount of deformation of the elastic disk 13 and, as a consequence, the value of the stored strain energy.
  • the deformation of the elastic disk 13 also leads to the formation of a cavity between the elastic disk 13 and the thrust ring 6, which under the influence of the resulting vacuum is filled with fuel, and when the elastic disk 13 is straightened to its original position, the fuel is displaced from this cavity, providing a smooth fit of the thrust ring 6. the force of their impact is less than the force of the spring 8, which eliminates the undesirable separation of the locking element 10 (Fig. 2) from the saddle.
  • a decrease in the collision force of the locking element 10 against the saddle will allow, without increasing the stresses arising at the same time, on the saddle and the locking element 10 to reduce the diameter of the locking element 10 and, as a result, using the same electromagnet, control a significantly higher fuel pressure.

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

Abstract

L'invention concerne une soupape électromagnétique pour injecteur de carburant à commande hydraulique, laquelle est destinée à être utilisée dans le système de pulvérisation de carburant d'un moteur à combustion interne. La soupape électromagnétique comprend un électro-aimant, un poussoir (5) poussé par un ressort dans le sens de l'ouverture du circuit magnétique et connecté à un élément de fermeture (10), un induit d'électro-aimant (4) disposé sur le poussoir (5) de manière à pouvoir effectuer un déplacement axial par rapport au poussoir (5) dans le sens de l'ouverture du circuit magnétique et comportant une butée dans le sens de la fermeture, le déplacement de l'induit (4) dans le sens de l'ouverture du circuit magnétique étant limité par un élément élastique. Selon la présente invention, l'élément élastique se présente sous forme d'un disque élastique (13) qui est relié au poussoir (5) et qui est fixé rigidement par sa partie périphérique à l'induit (4) de manière à former une cavité d'amortissement (14) entre la face du disque élastique (13) et l'induit (4). La butée consiste en un anneau élastique déformable (6) qui est fixé sur la périphérie de l'induit (4) de l'autre côté de la cavité d'amortissement par rapport au disque élastique (13). La soupape électromagnétique de la présente invention possède une structure simple et fiable ayant des dimensions axiales réduites, et permet de gérer une pression de carburant accrue sans augmenter la puissance de l'électro-aimant.
PCT/RU2011/000037 2011-01-26 2011-01-26 Soupape électromagnétique pour injecteur de carburant à commande hydraulique WO2012102635A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/RU2011/000037 WO2012102635A1 (fr) 2011-01-26 2011-01-26 Soupape électromagnétique pour injecteur de carburant à commande hydraulique
RU2013134929/06A RU2541483C1 (ru) 2011-01-26 2011-01-26 Электромагнитный клапан для гидроуправляемой топливной форсунки

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/RU2011/000037 WO2012102635A1 (fr) 2011-01-26 2011-01-26 Soupape électromagnétique pour injecteur de carburant à commande hydraulique

Publications (1)

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WO2012102635A1 true WO2012102635A1 (fr) 2012-08-02

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RU (1) RU2541483C1 (fr)
WO (1) WO2012102635A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10167831B2 (en) 2017-01-13 2019-01-01 Caterpillar Inc. Accumulator centering mechanism
CN110513225A (zh) * 2019-09-29 2019-11-29 中船动力研究院有限公司 一种电控喷油器

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6305355B1 (en) * 1998-05-07 2001-10-23 Daimlerchrysler Ag Control device for a high-pressure injection nozzle for liquid injection media
DE10336816A1 (de) * 2003-08-11 2005-03-10 Bosch Gmbh Robert Verfahren und Anordnung zur Messung des Druckes im Steuerraum eines der Kraftstoffeinspritzung in Zylinderbrennräume von Brennkraftmaschinen dienenden Injektors, insbesondere Common-Rail-Injektors
RU2280781C1 (ru) * 2005-03-05 2006-07-27 Федеральное государственное образовательное учреждение высшего профессионального образования Воронежский государственный аграрный университет им. К.Д. Глинки Электрогидравлическая форсунка для дизеля

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU1738097A3 (ru) * 1990-11-27 1992-05-30 В.М.Коросташевский, А.Н.Савушкин и Б.А.Шахт Электромагнитна форсунка дл впрыска топлива в двигатель внутреннего сгорани
RU2059868C1 (ru) * 1992-08-31 1996-05-10 Фирма "Авангард" Электромагнитная форсунка
US5893516A (en) * 1996-08-06 1999-04-13 Lucas Industries Plc Injector
JP4078320B2 (ja) * 2004-02-27 2008-04-23 三菱重工業株式会社 ポペット弁装置及びそれを備えた電子制御燃料噴射装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6305355B1 (en) * 1998-05-07 2001-10-23 Daimlerchrysler Ag Control device for a high-pressure injection nozzle for liquid injection media
DE10336816A1 (de) * 2003-08-11 2005-03-10 Bosch Gmbh Robert Verfahren und Anordnung zur Messung des Druckes im Steuerraum eines der Kraftstoffeinspritzung in Zylinderbrennräume von Brennkraftmaschinen dienenden Injektors, insbesondere Common-Rail-Injektors
RU2280781C1 (ru) * 2005-03-05 2006-07-27 Федеральное государственное образовательное учреждение высшего профессионального образования Воронежский государственный аграрный университет им. К.Д. Глинки Электрогидравлическая форсунка для дизеля

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10167831B2 (en) 2017-01-13 2019-01-01 Caterpillar Inc. Accumulator centering mechanism
CN110513225A (zh) * 2019-09-29 2019-11-29 中船动力研究院有限公司 一种电控喷油器

Also Published As

Publication number Publication date
RU2013134929A (ru) 2015-03-10
RU2541483C1 (ru) 2015-02-20

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