EP1947322A2 - Injecteur destiné à la vaporisation de carburant - Google Patents

Injecteur destiné à la vaporisation de carburant Download PDF

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Publication number
EP1947322A2
EP1947322A2 EP07122721A EP07122721A EP1947322A2 EP 1947322 A2 EP1947322 A2 EP 1947322A2 EP 07122721 A EP07122721 A EP 07122721A EP 07122721 A EP07122721 A EP 07122721A EP 1947322 A2 EP1947322 A2 EP 1947322A2
Authority
EP
European Patent Office
Prior art keywords
piston
valve
actuator
force
coupler
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
EP07122721A
Other languages
German (de)
English (en)
Other versions
EP1947322A3 (fr
EP1947322B1 (fr
Inventor
Holger Rapp
Wolfgang Stoecklein
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 EP1947322A2 publication Critical patent/EP1947322A2/fr
Publication of EP1947322A3 publication Critical patent/EP1947322A3/fr
Application granted granted Critical
Publication of EP1947322B1 publication Critical patent/EP1947322B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic

Definitions

  • the invention relates to an injector for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1.
  • the opening and closing of a fuel injector is controlled by a control valve integrated in the injector.
  • the control valve is usually operated by means of an actuator. Suitable actuators are, for example, piezoactuators.
  • a hydraulic coupler is used for transmitting the force and the stroke of the actuator to the control valve.
  • This is an assembly comprising a housing having two concentric bores, a piston having a first diameter in one of these bores and a valve piston having a second diameter in the second of the concentric bores. The volume bounded by these two pistons is filled with fuel.
  • the actuator moves the first piston. Due to the force exerted by the actuator on this piston pressure is built up in the fuel volume between the two pistons, which in turn causes a force on the second piston. This force results from the force exerted by the actuator according to the ratio of the areas of the two pistons.
  • the deflection of the valve piston also causes a deflection of the piston and thus of the actuator.
  • the deflection of the actuator results from the deflection of the valve piston according to the ratio of the areas of the two pistons.
  • An inventively designed injector for injecting fuel into a combustion chamber of an internal combustion engine comprises a hydraulic coupler, which transmits the stroke and force of an actuator to a control valve.
  • the force acting on the control valve is at least as great as the force delivered by the actuator.
  • the hydraulic coupler comprises a first piston, which is guided in a first guide in a coupler housing and defines a coupler space with an end face.
  • the coupler space is bounded on a second side by a valve piston of the control valve.
  • In a first region of the valve piston is formed in a first diameter and in a second region in a second diameter.
  • the second diameter is smaller than the first diameter.
  • the valve piston in the second region with the smaller diameter is enclosed by a ring element, which is movable relative to the valve piston.
  • the coupler is carried out with a variable transmission ratio.
  • a small stroke initially acts a small gear ratio with a large valve-side force.
  • a medium stroke it automatically switches to a higher gear ratio.
  • the valve-side lifting capacity relative to a coupler thus remains unchanged.
  • the ring element is usually performed with its outer diameter in the guide in the coupler housing.
  • One of a different gear ratio is achieved in that the outer diameter of the ring is different from the diameter of the first region of the valve piston.
  • the outer diameter of the ring element is greater than the diameter of the first region of the valve piston. This ensures that the stroke of the valve piston is greater than the actuator-side stroke.
  • a shoulder is advantageously formed between the first region and the second region, which acts as a stroke limiter for the ring element.
  • This paragraph may be formed, for example, as a flat surface, conical or conical. Furthermore, the paragraph can also have any other geometry known in the art.
  • a spring element acts on the ring element such that the ring element is pressed by the spring force of the spring element against the shoulder.
  • control piston From the ring member, the control piston and the coupler housing a control chamber is enclosed, in which a volume of fuel is enclosed.
  • the outer diameter of the ring member and the outer diameter of the first piston may be the same or different.
  • the advantage with the same diameters is that a guide with a constant diameter is formed in the coupler housing, in which the first piston and the ring element are guided. As a result, the production of the coupler housing is simplified. If the outer diameter of the ring member and the first piston are different, the guide in the coupler housing is also carried out in different diameters. For this purpose, a paragraph is usually provided in the guide. At different diameters of the ring member and the first piston, the gear ratios differ, with which on the one hand the blocking force of the actuator to the valve side and on the other hand, the idle stroke are translated to the valve side.
  • the outer diameter of the first piston is greater than the outer diameter of the annular element.
  • the blocking force of the actuator is reduced to the valve side with a smaller gear ratio and the idle stroke is translated to the valve side with a larger gear ratio.
  • the actuator with which the control valve is actuated is preferably a piezoelectric actuator.
  • the piezoelectric actuator it is also possible to use any other actuator known to the person skilled in the art which has a comparable function.
  • FIG. 1 an inventively designed fuel injector is shown.
  • a fuel injector 1 comprises an injection valve member 3 with which at least one injection opening 5 can be released or closed.
  • fuel is injected into a combustion chamber, not shown here, an internal combustion engine.
  • the injection valve member 3 is received in a lower housing part 7.
  • the injection valve member 3 On its side facing away from the at least one injection opening 5, the injection valve member 3 is surrounded by a spring element 9 and a ring element 11.
  • the ring element 11 has a biting edge with which it is placed against a throttle plate 13.
  • the spring element 9, which is preferably designed as a coil spring compression spring acts with one side against a shoulder 15 on the injection valve member 3 and the other side against an end face 17 on the ring member 11. In this way, the ring member 11 by means of the spring element. 9 pressed against the throttle plate 13.
  • the ring element 11, the throttle plate 13 and an upper end face 19 of the injection valve member 3 enclose a control chamber 21 which is filled with fuel under high pressure.
  • a control valve 23 connects. With the control valve 23 is an outlet throttle 25, which connects the control chamber 21 with a fuel return 27, closed or released. To close the connection, a closing element 29 is placed in its seat 31. For this purpose acts on the closing element 29, a valve piston 33. Die Actuation of the valve piston 33 is effected by means of an actuator 35, which is designed in the embodiment shown here as a piezoelectric actuator. Actuator 35 first acts on a booster piston 37 of a hydraulic coupler 39. Via the hydraulic coupler 39, the stroke and the force of the actuator 35 are translated to the valve piston 33. The stroke of the valve piston 33 is increased relative to the stroke of the booster piston 37th
  • the fuel injector 1 is connected, for example, to a high-pressure accumulator of a high-pressure accumulator injection system.
  • the high pressure fuel provided by the high pressure accumulator flows via the high pressure port 41 and a high pressure passage 43 into a nozzle space 45 enclosing the injection valve member 3.
  • the actuator 35 is connected to a voltage source, which is not shown here.
  • a second spring element 47 acts on the closing element 29 and places the closing element 29 in its seat 31.
  • the fuel under system pressure acts via the high-pressure passage 43, an inlet throttle 49 branching from the high-pressure passage 43 into the control chamber 21, the control chamber 21 and the outlet throttle 25 onto the closing element 29.
  • the system pressure prevailing in the control chamber 21 exerts a pressure force on the injection valve member 3 whereby it is placed in its seat 51 and thus closes the at least one injection opening 5.
  • the actuator 35 is energized. As a result, the actuator 35 expands.
  • the actuator force acts on the booster piston 37.
  • the booster piston 37 is moved in the direction of the valve piston 33.
  • a coupler space 53 is formed, which is filled with fuel.
  • the volume of the coupler space 53 decreases and the pressure increases.
  • the thus increased pressure force acts on the valve piston 33, which is moved in the direction of the closing element 29.
  • the valve piston 33 presses the closing element 29 out of its seat 31.
  • the connection from the control chamber 21 via the outlet throttle 25 into the fuel return 27 is released.
  • the pressure in the control room 21 drops.
  • the injection valve member 3 rises from its seat 51 and releases the at least one injection opening 5.
  • the required Force required to lift the injection valve member 3 out of its seat 51 is provided by the pressurizing force of the fuel in the nozzle space 45.
  • the fuel contained in the nozzle chamber 45 which has system pressure acts on a pressure surface 55 on the injection valve member 3.
  • the pressure surface 55 is oriented so that the force acting on the pressure surface 55 force of the compressive force acting on the upper end face 19 of the injection valve member 3 is opposite ,
  • the energization of the actuator 35 is terminated.
  • the actuator 35 contracts again.
  • the booster piston 37 is moved in the direction of the actuator 35.
  • the volume in the coupler space 53 increases, whereby the pressure in the coupler space 53 decreases.
  • the valve piston 33 also moves in the direction of the actuator 35 and the closing element 29 is returned to its seat 31.
  • the connection from the control chamber 21 via the outlet throttle 25 in the fuel return 27 is closed.
  • fuel that is under system pressure again flows into the control chamber 21, as a result of which system pressure builds up in the control chamber 21. Due to the increasing pressure force on the upper end face 19 of the injection valve member 3, this is again placed in its seat 51 and the at least one injection port 5 is closed.
  • the injection process is finished.
  • FIG. 2 shows an inventively designed hydraulic coupler in an enlarged view.
  • the hydraulic coupler is designed with a variable gear ratio that acts at a small stroke of the actuator 35, first, a small gear ratio and the valve-side force assumes large values. At a medium lift, a higher gear ratio is then automatically switched so that the valve-side lift capacity remains unchanged from a prior art hydraulic coupler.
  • the valve piston 33 is enclosed by a ring element 61.
  • the valve piston 33 comprises a first region 63, which faces the control valve 23 and has a diameter d 1 .
  • the valve piston 33 is designed in a second diameter d 2 .
  • the second diameter d 2 is smaller than the first diameter d 1 .
  • a shoulder 67 is formed at the transition from the first diameter d 1 to the second diameter d 2 .
  • the shoulder 67 serves as a stroke limiter for the ring element 61.
  • the ring element 61 is guided with its inner surface 69 on the second region 65 of the valve piston 33. With its outer surface 71, the ring member 61 is guided in a coupler housing 73. In the coupler housing 73, the booster piston 37 is also guided.
  • a spring element 75 acts, which is supported with one side against the ring member 61 and with the other side against the booster piston 37.
  • the spring element 75 is preferably designed as a compression spring coil spring. But it is also any other, known in the art compression spring used.
  • the ring element 61, the valve piston 33 and the coupler housing 73 enclose a control chamber 77.
  • the control chamber 77 is filled with fuel.
  • the booster piston 37 is moved in the direction of the coupler space 53.
  • the volume in the coupler space 53 decreases and the pressure thereby increases.
  • a compressive force on the valve piston 33 acts on the annular element 61.
  • the annular element 61 and the valve piston 33 are moved in the direction of the control valve 23. Due to the same outer diameter of the booster piston 37 and the ring member 61 in the in FIG. 2
  • the transmission ratio is thus initially at 1: 1.
  • the movement of the ring element 61 in the direction of the control valve 23 reduces the volume in the control chamber 77.
  • a pressure builds up in the control chamber 77.
  • the pressure in the coupler space 53 decreases due to the actuator force due to the longitudinal extent of the actuator 35.
  • x 0 is the stroke of the actuator 35.
  • ü is the ratio of the booster piston 37 to valve piston 33rd
  • Advantage of the present invention designed hydraulic coupler 39 is that initially the full force of the actuator 35 is transmitted, but at the same time the increased idle stroke of a coupler with a transmission ratio> 1 can be used without for this purpose increases the actuator voltage or a larger actuator must be used ,
  • the booster piston 37 is moved out of the coupler space 53. Also, the valve piston 33 and the ring member 61 move back to their original position.
  • the stroke of the valve piston is plotted on the x-axis, and the force exerted by the valve piston 33 on the closing element 29 is plotted on the y-axis.
  • the force of the valve piston 33 decreases to the closing element 29 corresponding to the line 81.
  • the full force of the actuator 35 acts on the valve piston 33.
  • F 0 denotes the blocking force of the actuator, that is to say the force which the actuator 35 would exert on its surroundings in the event of double-sided firm tension.
  • the force decreases with increasing deflection x due to the non-zero actuator stiffness.
  • the force zero is reached when the deflection of the valve piston 33 reaches the multiplied by the gear ratio idle stroke of the actuator. With a transmission ratio of 1: 1, the deflection of the valve piston 33 is equal to the idling stroke of the actuator.
  • Reference numeral 83 designates the force / stroke curve resulting in a gear ratio of 1: 1.4. How out FIG. 3 it can be seen acts in such a ratio with one-piece booster piston 37 and one-piece valve piston 33 is not the full blocking force of the actuator on the valve piston 33. The maximum force that can act on the valve piston 33, compared to the force at a gear ratio of 1 : 1 can act on the valve piston 33, reduced.
  • the ring element 61 which on the second portion 65 of Valve piston 33 is guided, depending on the volume of the control chamber 77, the designated by the reference numerals 85, 87 and 89 force / stroke curves.
  • the volume of the control chamber 77 is the smallest in the force / stroke curve 89 and the largest in the force / stroke curve 85.
  • the force initially decreases with increasing stroke on the basis of the blocking force of the actuator F 0 .
  • the valve piston 33 continues to move without the ring member 61 in the direction of the control valve 23.
  • the force / stroke curve takes a flatter course and ends at a maximum stroke corresponding to the stroke, with a corresponding Gear ratio, here at a transmission ratio of 1: 1.4, is achieved.
  • the switching point 91 is reached in each case when the force which the valve piston 33 exerts on the closing element 29 is the gear ratio below the force / stroke curve of a single-stage hydraulic coupler with the ratio 1. This is shown with the dashed auxiliary line 93.
  • the outer diameter of the ring member 61 and the booster piston 37 it is also possible to make the outer diameter of the ring member 61 and the booster piston 37 different.
  • a shoulder is formed in the coupler housing 73, so that both the booster piston 37 and the ring element 61 can be guided with its outer diameter in the coupler housing 73.
  • the ring element then has an outer diameter d ' 0 , while the diameter of the booster piston 37 is still d 0 .
  • the spring element 75 which holds down the ring member 61 in the resting state on the shoulder 67 of the valve piston, also ensures that the small amount of fuel that penetrates via guide gaps of the ring member 61 with active coupler in the control chamber 77 in the operating pauses again pressed out of the control chamber 77 becomes.
  • the spring element 75 can continue to take over the task of the known from the prior art valve piston spring and ensure the refilling of the coupler chamber 53. The known from the prior art valve piston spring can then be omitted.
  • the shoulder 67 is designed as a flat surface
  • the piston 33 and the ring member 61 touch on arbitrarily shaped surfaces.
  • the paragraph 67 may be designed cone-shaped and the corresponding surface on the ring member 61 level, conical or as a double cone.
  • the contact line or the contact surface between the ring element 61 and the second region 65 of the valve piston 33 is continuous or interrupted.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
EP07122721A 2007-01-16 2007-12-10 Injecteur destiné à la vaporisation de carburant Not-in-force EP1947322B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007002278A DE102007002278A1 (de) 2007-01-16 2007-01-16 Injektor zum Einspritzen von Kraftstoff

Publications (3)

Publication Number Publication Date
EP1947322A2 true EP1947322A2 (fr) 2008-07-23
EP1947322A3 EP1947322A3 (fr) 2009-08-05
EP1947322B1 EP1947322B1 (fr) 2011-02-23

Family

ID=39232743

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07122721A Not-in-force EP1947322B1 (fr) 2007-01-16 2007-12-10 Injecteur destiné à la vaporisation de carburant

Country Status (3)

Country Link
EP (1) EP1947322B1 (fr)
AT (1) ATE499522T1 (fr)
DE (2) DE102007002278A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013225379A1 (de) 2013-12-10 2015-06-11 Robert Bosch Gmbh Hydraulischer Koppler

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10322672A1 (de) * 2003-05-20 2004-12-09 Robert Bosch Gmbh Ventil zum Steuern von Flüssigkeiten
DE102004035280A1 (de) * 2004-07-21 2006-03-16 Robert Bosch Gmbh Kraftstoffinjektor mit direkter mehrstufiger Einspritzventilgliedansteuerung
DE102005007543A1 (de) * 2005-02-18 2006-08-24 Robert Bosch Gmbh Kraftstoffinjektor mit direkter Nadelsteuerung für eine Brennkraftmaschine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10322672A1 (de) * 2003-05-20 2004-12-09 Robert Bosch Gmbh Ventil zum Steuern von Flüssigkeiten
DE102004035280A1 (de) * 2004-07-21 2006-03-16 Robert Bosch Gmbh Kraftstoffinjektor mit direkter mehrstufiger Einspritzventilgliedansteuerung
DE102005007543A1 (de) * 2005-02-18 2006-08-24 Robert Bosch Gmbh Kraftstoffinjektor mit direkter Nadelsteuerung für eine Brennkraftmaschine

Also Published As

Publication number Publication date
DE502007006537D1 (de) 2011-04-07
EP1947322A3 (fr) 2009-08-05
ATE499522T1 (de) 2011-03-15
EP1947322B1 (fr) 2011-02-23
DE102007002278A1 (de) 2008-07-17

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