EP2426348A1 - Soupape d'injection de combustible - Google Patents

Soupape d'injection de combustible Download PDF

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Publication number
EP2426348A1
EP2426348A1 EP20110174438 EP11174438A EP2426348A1 EP 2426348 A1 EP2426348 A1 EP 2426348A1 EP 20110174438 EP20110174438 EP 20110174438 EP 11174438 A EP11174438 A EP 11174438A EP 2426348 A1 EP2426348 A1 EP 2426348A1
Authority
EP
European Patent Office
Prior art keywords
nozzle
pressure
needle
sealing seat
fuel
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
EP20110174438
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German (de)
English (en)
Other versions
EP2426348B1 (fr
Inventor
Hans-Christoph Magel
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2426348A1 publication Critical patent/EP2426348A1/fr
Application granted granted Critical
Publication of EP2426348B1 publication Critical patent/EP2426348B1/fr
Active 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • 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
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/002—Arrangement of leakage or drain conduits in or from injectors
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042—The valves being provided with fuel passages
    • 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
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies

Definitions

  • the invention relates to a fuel injection valve for fuel injection systems of internal combustion engines. Specifically, the invention relates to an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • the known injection device comprises an elongated housing with a closed injection end. In the housing extends in the longitudinal direction of a recess. This is connectable to a fuel inlet. At the injection end, at least two axially spaced outlet openings are present. In the recess at least two coaxial and axially movable valve elements are arranged, which work together with valve seats in the region of the outlet openings.
  • the valve elements In order to build the injector as simple and small as possible, the valve elements on a driver connection, wherein a valve element axially comes into contact with a movement after a certain way to the other valve element and this moves with.
  • a common rail system is used in which an injection pressure can be adapted to the instantaneous load and speed in an advantageous manner.
  • a common-rail system may include stroke-controlled common rail injectors in which the respective nozzle needle is controlled directly by a piezoelectric actuator.
  • an inwardly opening nozzle can be provided with spray holes in order to achieve a good mixture preparation in the engine.
  • the piezoelectric actuator of the injector can in this case raise the nozzle needle via a hydraulic coupler chamber in order to achieve the injection of fuel into a combustion chamber of the internal combustion engine. This allows a large opening and closing speed of the nozzle needle can be achieved in a simple Injektor indispensable.
  • Opening forces to open the nozzle needle a relatively large piezoelectric actuator is required. This also has an adverse effect on the cost and durability of the piezoelectric actuator.
  • the fuel injection valve according to the invention with the features of claim 1 has the advantage that a control for injecting fuel through the nozzle opening is improved in a combustion chamber of an internal combustion engine or the like. Specifically, a pressure-balanced design is possible in which only relatively low actuation forces are required.
  • an inner needle is provided, which is guided in the axial bore of the nozzle needle, that the inner needle cooperates with the nozzle body to a second sealing seat, that when the first sealing seat is opened by a fuel pressure, a hydraulic actuation of the inner needle to open the second Sealing seat is made possible that in the nozzle body, a fuel space is provided in the fuel under high pressure is feasible, that the nozzle needle is at least partially disposed in the fuel chamber and that when the first first sealing seat and opened second sealing seat, a fuel flow from the fuel chamber to the Nozzle opening is possible.
  • the nozzle needle can be actuated directly, so that the first sealing seat is opened.
  • the nozzle needle can be uniformly acted upon by the fuel under high pressure, so that a pressure compensation exists, which leads in particular to a force balance along an axis of the nozzle needle.
  • the actuation of the nozzle needle can be achieved with a relatively low actuator force.
  • the nozzle needle can be operated directly, the nozzle needle is pressure balanced and requires only little movement forces.
  • the necessary pressure equalization guide can be separated from a flue gas region at the nozzle opening to prevent coking and excessive heating of the leadership by the flue gases.
  • the inner needle opens here by the injection pressure of the fuel.
  • the actuator is designed as a magnetic actuator, wherein the magnetic actuator has an armature which is connected to the nozzle needle.
  • the magnetic actuator has an armature which is connected to the nozzle needle.
  • a closing spring is provided, which is arranged in the axial bore of the nozzle needle, and that the closing spring acts on the inner needle against the nozzle body.
  • the closing of the inner needle can be achieved by the spring force of the closing spring.
  • the closing spring is arranged in a part of the axial bore of the nozzle needle, that the pressure compensation pin, which is arranged in the axial bore, has a return bore, that the closing spring is at least indirectly supported on the pressure compensation pin and that the part of the axial Bore, in which the closing spring is arranged, is connected via the return bore of the pressure balance pin with a low pressure return.
  • a base body is provided, that the nozzle body is connected to the base body and that the base body has a support surface on which the pressure equalization pin is supported.
  • the pressure compensation pin can be pressed by hydraulic forces to the body in an advantageous manner and thereby seal securely. This ensures a stable position of the pressure balance pin, whereby tolerances between the components can be compensated.
  • a low-pressure space is limited, which is connected to the low-pressure return, and that the return bore of the pressure balance pin opens into the low-pressure chamber.
  • the low pressure chamber facing side of the pressure compensation pin is thereby safely on the low pressure. This ensures a stable position of the pressure compensation pen. Furthermore, this ensures a reliable connection of the part of the axial bore, in which the closing spring is arranged, with the low-pressure return.
  • a sealing sleeve is provided which surrounds the pressure equalization pin sections, that a spring element is provided, which urges the sealing sleeve against the base body, and that the sealing sleeve the Low pressure space limited.
  • the pressure compensation pin can be sealed by the sealing sleeve against the high pressure of the fuel.
  • a tolerance compensation between the components can be further improved.
  • a throttle gap is designed, which leads on the one hand in the part of the axial bore of the nozzle needle and on the other hand leads to the nozzle body between the first sealing seat and the second sealing seat.
  • Fig. 1 shows a first embodiment of a fuel injection valve 1 in a schematic sectional view.
  • the fuel injection valve 1 can in particular as Injector for fuel injection systems of air-compressing, self-igniting internal combustion engines are used.
  • a preferred use of the fuel injection valve 1 is for a fuel injection system with a common rail 2, which serves as an accumulator and leads under high pressure diesel fuel to a plurality of fuel injection valves 1.
  • the fuel injection valve 1 according to the invention is also suitable for other applications.
  • the fuel injection valve 1 has a housing 3 with a main body 4 and a nozzle body 5. In the housing 3, a multi-part fuel chamber 6 is configured. The fuel injection valve 1 is connected via a fuel line 7 to the common rail 2. Fuel is conducted via the fuel line 7 into a fuel channel 8 designed in the base body 4 in order to lead the fuel into a part 9 of the fuel chamber 6.
  • a nozzle needle 10 is arranged, which is guided along an axis 11.
  • At the nozzle needle 10 at least one flow passage 12 is configured, which connects the part 9 of the fuel chamber 6 with a part 13 of the fuel chamber 6. During operation of the fuel injection valve 1 is thus in the parts 9, 13 of the fuel chamber 6 under high pressure fuel.
  • the nozzle needle 10 has an axial bore 15 in which an inner needle 16 and a pressure compensation pin 17 are guided. Further, a closing spring 18 is arranged in the axial bore 15, which acts on the inner needle 16 against a valve seat surface 19 configured on the nozzle body 5.
  • a connected to the pressure compensation pin 17 spacer element 20 is provided which specifies a minimum distance and thus a minimum length of the closing spring 18.
  • a first sealing seat 21 is formed between the nozzle needle 10 and the valve seat surface 19 of the nozzle body 5.
  • a second sealing seat 22 is formed between the inner needle 16 and the valve seat surface 19 of the nozzle body 15.
  • the first sealing seat 21 and the second sealing seat 22 are provided, so that only when the first first sealing seat 21 and opened second sealing seat 22, a fuel flow from the fuel chamber 6 to the nozzle opening 24 and thus into a Combustion chamber of an internal combustion engine or the like is possible.
  • the fuel injection valve 1 has a magnetic actuator 30, which comprises a magnet 31 with a magnetic coil 32 and an armature 33.
  • the armature 33 is connected to the nozzle needle 10.
  • the magnet coil 32 of the magnet 31 can be connected via an electrical line 34 to a control unit or the like.
  • the magnet 31 exerts a magnetic force on the armature 33, so that the nozzle needle 10 is actuated in an opening direction 35 along the axis 11.
  • the first sealing seat 21 between the nozzle needle 10 and the valve seat surface 19 is opened.
  • the closing spring 18 is arranged in a part 36 of the axial bore 15, which is connected to a low-pressure return 37.
  • the pressure compensation pin 17 has a return bore 38, which opens on the one hand in the part 36 of the axial bore 15 of the nozzle needle 10 and on the other hand in a low-pressure chamber 39.
  • the low-pressure chamber 39 is connected to the low-pressure return line 37 via a return passage 40 leading through the main body 4.
  • the high pressure of the fuel acts on the inner needle 16 as far as the second sealing seat 22, which is still closed at first.
  • This pressure causes a force on the inner needle 16, which acts in the opening direction 35.
  • the part 36 of the axial bore 15 is under low pressure, the force of the fuel acting in the opening direction 35 counteracts only the closing force of the closing spring 18.
  • the closing spring 18 and the configuration of the inner needle 16 in the region of the second sealing seat 22 are predetermined so that the opening force by the pressure of the fuel exceeds the spring force of the closing spring 18, so that the inner needle 16 is actuated in the opening direction 35.
  • the solenoid coil 32 is de-energized.
  • the nozzle needle 10 is almost balanced in the open state. Therefore, the closing of the nozzle needle 10 via a valve spring 41 can take place.
  • the nozzle needle 10 is adjusted by the valve spring 41 against the opening direction 35, so that the first sealing seat 21 is closed again.
  • the pressure of the fuel acting on the inner needle 16 also collapses. That means that too Inner needle 16 is adjusted by the closing force of the closing spring 18 against the opening direction 35, whereby the second sealing seat 22 is closed again. Therefore, the connection between the fuel chamber 6 and the nozzle opening 24 via the two sealing seats 21, 22 separated again and the injection is completed.
  • the inner diameter of the low-pressure chamber 39 is selected to be greater than the outer diameter of the pressure compensation pin 17. Due to the high pressure of the fuel in the fuel chamber 6 thus the pressure compensation pin 17 is acted upon against a support surface 42 of the base body 4. Thus, the pressure compensation pin 17 is pressed by hydraulic forces to the base body 4, whereby a secure seal is formed.
  • the diameter of the pressure compensation pin 17 is equal to the guide diameter of the nozzle needle 10, over which abuts of the part 36 of the axial bore 15 of low pressure.
  • the diameter of the first sealing seat 21 between the nozzle needle 10 and the valve seat surface 19 preferably has at least substantially the same diameter as the axial bore 15 of the nozzle needle 10.
  • the low-pressure chamber 39 is bounded on the one hand by the main body 4 and on the other hand by the basic compensating body 17. Furthermore, the low pressure space 39 is circumferentially bounded by an annular shoulder 43 of the pressure compensation pin 17. As a result, a certain volume of the low-pressure space 39 is predetermined. Depending on the configuration of the fuel injection valve 1, however, the low-pressure chamber 39 can also be omitted.
  • the magnetic actuator 30 is disposed in the part 9 of the fuel chamber 6, whereby it is surrounded during operation of high-pressure fuel.
  • the fuel injection valve 1 is designed in this embodiment so that the nozzle needle 10 and the inner needle 16 are closed in the de-energized state of the magnetic actuator 30.
  • the necessary pressure equalization guide can be separated from the flue gas region at the nozzle opening 24. As a result, coking and excessive heating of the guide is avoided by the flue gases.
  • the inner needle 16 opens by the injection pressure and closes on the spring force of the closing spring 18th
  • a throttling action between the low pressure and a point between the two sealing seats 21, 22 may be provided.
  • a throttle gap may be predetermined, via which a throttled connection of the point between the two sealing seats 21, 22 formed on the valve seat surface 19 and the part 36 of the axial bore 15.
  • at least one groove or the like may be configured on the inner needle 16 and / or on the axial bore 15 in the region of the inner needle 16. The throttle function is then realized within the guidance of the inner needle 16, resulting in favorable production costs.
  • Fig. 2 shows a fuel injection valve 1 in a schematic sectional view according to a second embodiment.
  • a sealing sleeve 50 is arranged in the fuel chamber 6, which encloses the pressure equalization pin 17 in sections.
  • the sealing sleeve 50 is acted upon by the valve spring 41.
  • the valve spring 41 presses the sealing sleeve 50 against the support surface 42 of the base body 4.
  • the sealing sleeve 50 has a sealing edge 51, with which the sealing sleeve 50 bears against the support surface 42.
  • a diameter of the first sealing seat 21 is greater than a diameter of the second sealing seat 22.
  • the opening stroke of Inner needle 16 is limited by the stop, which is determined by the spacer 20, to the extent necessary to achieve an exact closing movement.
  • the stroke stop by the spacer element 20 is supported via the pressure compensation pin 17 on the main body 5 of the housing 3.
  • the magnetic actuator 30 for moving the nozzle needle 10 is arranged in this embodiment in the fuel chamber 6 and engages directly on the nozzle needle 10. To generate the opening force, one or more magnetic actuators 30 may be provided. It is also possible that magnetic actuators are provided which generate closing forces in order to ensure faster needle closing.
  • the nozzle needle 10 is almost force balanced in the open state, so that closing can be done via the spring force of the valve spring 41. To increase the closing speed, the closing force can be supported by an additional actuator.
  • the magnetic coil 32 has a suitable structure for sealing against the surrounding medium, that is to say the fuel, for example a casting with epoxy resin.
  • the contacting of the magnetic coil 32 takes place in a suitable, high-pressure-tight manner, for example via Glaseinschmelzonne.
  • the fuel is guided past the magnet 31 with the magnet coil 32 within the fuel space 6.
  • the end 23 of the nozzle body 5, on which the nozzle opening 24 is configured, has a certain amount of damage between the nozzle needle 10 and the nozzle opening 24, which, however, is not significantly increased by the inner needle 16.
  • a solenoid actuator 30 may be sufficient to ensure actuation of the nozzle needle 10.
  • other types of actuators 30 may be provided for actuating the nozzle needle 10, in particular piezo actuators.
  • Fig. 3 shows a fuel injection valve 1 in a schematic representation according to a third embodiment.
  • another possibility is shown to achieve a throttling action between a location between the two sealing seats 21, 22 and the low pressure return 37.
  • This can cause disturbances that cause leaks at the first sealing seat 21 between the nozzle needle 10 and the valve seat surface 19 of the nozzle body 5 can be compensated.
  • a due to the leak at the first sealing seat 21 between the first sealing seat 21 and the second sealing seat 22 reaching leakage amount of fuel can on the Throttle effect are discharged to the low pressure return flow 37 to prevent actuation of the inner needle 16.
  • a leakage amount entering the combustion chamber can degrade the engine emissions, which is thus avoided.
  • the inner needle 16 has a bore 52 which is aligned with the axis 11. Furthermore, at least one bore 53 is provided which leads from the bore 52 to a location between the sealing seats 21, 22.
  • the bore 53 is designed as a throttle bore 53, so that it forms a throttle 53.
  • the holes 52, 53 can also form a throttle bore in other ways.
  • the throttle bore 53 ensures a throttled connection with the part 36 of the axial bore 15 of the nozzle needle 10.
  • a leakage quantity reaching via the first sealing seat 21 can be reliably isolated.
  • there is the advantage that the residual pressure during closing of the nozzle needle 10 is reduced faster by the throttle 53. This leads to an improved closing behavior of the inner needle 16.
  • the function of the pressure-balanced nozzle needle 10 can be ensured and a directly controlled fuel injection valve 1 can be realized with a cost-effective actuator 30.
  • a small gap 54 can be configured between the sealing seats 21, 22.
  • the bore 53 opens into the intermediate space 54, while the bore 52 opens into the part 36 of the axial bore 15.
  • the throttle bore 52, 53 thereby opens on the one hand in the part 36 and on the other hand, this is open between the first sealing seat and the second sealing seat to the nozzle body 5 out.

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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)
EP11174438.9A 2010-09-07 2011-07-19 Soupape d'injection de combustible Active EP2426348B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201010040309 DE102010040309A1 (de) 2010-09-07 2010-09-07 Brennstoffeinspritzventil

Publications (2)

Publication Number Publication Date
EP2426348A1 true EP2426348A1 (fr) 2012-03-07
EP2426348B1 EP2426348B1 (fr) 2015-06-17

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP11174438.9A Active EP2426348B1 (fr) 2010-09-07 2011-07-19 Soupape d'injection de combustible

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EP (1) EP2426348B1 (fr)
DE (1) DE102010040309A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015150183A1 (fr) * 2014-04-01 2015-10-08 Robert Bosch Gmbh Injecteur de carburant
CN114151242A (zh) * 2021-11-19 2022-03-08 哈尔滨工程大学 双阀协同控制氨燃料喷射器

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5979803A (en) * 1997-05-09 1999-11-09 Cummins Engine Company Fuel injector with pressure balanced needle valve
DE10118699A1 (de) 2001-04-17 2002-10-31 Bosch Gmbh Robert Kraftstoff-Einspritzvorrichtung und Kraftstoffsystem für Brennkraftmaschinen, sowie Brennkraftmaschine
EP1719903A1 (fr) * 2005-05-03 2006-11-08 Delphi Technologies, Inc. Arrangement et procédé pour une soupape d'injection de carburant à mode de commutations
EP2011993A1 (fr) * 2007-07-06 2009-01-07 Delphi Technologies, Inc. Buse à injection de pulvérisation double
WO2009150512A1 (fr) * 2008-06-12 2009-12-17 Toyota Jidosha Kabushiki Kaisha Buse d’injection de carburant et clapet d’injection de carburant, et système de commande d’injection de carburant les utilisant
WO2010108747A1 (fr) * 2009-03-25 2010-09-30 Robert Bosch Gmbh Dispositif d'injection de carburant

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5979803A (en) * 1997-05-09 1999-11-09 Cummins Engine Company Fuel injector with pressure balanced needle valve
DE10118699A1 (de) 2001-04-17 2002-10-31 Bosch Gmbh Robert Kraftstoff-Einspritzvorrichtung und Kraftstoffsystem für Brennkraftmaschinen, sowie Brennkraftmaschine
EP1719903A1 (fr) * 2005-05-03 2006-11-08 Delphi Technologies, Inc. Arrangement et procédé pour une soupape d'injection de carburant à mode de commutations
EP2011993A1 (fr) * 2007-07-06 2009-01-07 Delphi Technologies, Inc. Buse à injection de pulvérisation double
WO2009150512A1 (fr) * 2008-06-12 2009-12-17 Toyota Jidosha Kabushiki Kaisha Buse d’injection de carburant et clapet d’injection de carburant, et système de commande d’injection de carburant les utilisant
WO2010108747A1 (fr) * 2009-03-25 2010-09-30 Robert Bosch Gmbh Dispositif d'injection de carburant

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015150183A1 (fr) * 2014-04-01 2015-10-08 Robert Bosch Gmbh Injecteur de carburant
CN114151242A (zh) * 2021-11-19 2022-03-08 哈尔滨工程大学 双阀协同控制氨燃料喷射器
CN114151242B (zh) * 2021-11-19 2023-07-21 哈尔滨工程大学 双阀协同控制氨燃料喷射器

Also Published As

Publication number Publication date
DE102010040309A1 (de) 2012-03-08
EP2426348B1 (fr) 2015-06-17

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