EP2813698A1 - Soupape d'injection de combustible - Google Patents

Soupape d'injection de combustible Download PDF

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Publication number
EP2813698A1
EP2813698A1 EP14165002.8A EP14165002A EP2813698A1 EP 2813698 A1 EP2813698 A1 EP 2813698A1 EP 14165002 A EP14165002 A EP 14165002A EP 2813698 A1 EP2813698 A1 EP 2813698A1
Authority
EP
European Patent Office
Prior art keywords
transmission element
valve
force transmission
actuator
closing body
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
EP14165002.8A
Other languages
German (de)
English (en)
Other versions
EP2813698B1 (fr
Inventor
Henning Kreschel
Andreas Rau
Holger Rapp
Thomas Schwarz
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 EP2813698A1 publication Critical patent/EP2813698A1/fr
Application granted granted Critical
Publication of EP2813698B1 publication Critical patent/EP2813698B1/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
    • 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
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2200/00—Input parameters for engine control
    • F02D2200/02—Input parameters for engine control the parameters being related to the engine
    • F02D2200/06—Fuel or fuel supply system parameters
    • F02D2200/0618—Actual fuel injection timing or delay, e.g. determined from fuel pressure drop
    • 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
    • F02M2200/701—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger mechanical
    • 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
    • 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
    • F02M2200/708—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with hydraulic chambers formed by a movable sleeve
    • 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
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0073—Pressure balanced valves

Definitions

  • the invention relates to a fuel injection valve, in particular an injector for fuel injection systems of internal combustion engines. Specifically, the invention relates to the field of injectors for fuel injection systems of air compressing, self-igniting internal combustion engines.
  • a control valve arrangement for a control chamber of a fuel injector is known.
  • the control valve arrangement can be actuated by an electromagnetic actuator.
  • the control valve assembly has a sleeve-shaped closing body, which is tensioned by a closing spring against a concentric seat.
  • a control chamber pressure of the control chamber is removed by means of a guide rod to a transmission, the electromagnetic parameters of the solenoid assembly changed such that the closing times of a nozzle needle can be detected by appropriate evaluation of the electric current-voltage curve of a magnetic coil.
  • the solenoid assembly in addition to its actuator function, the solenoid assembly also assumes sensor functions, and in addition to its guide function for the closing body, the guide rod has the task of modifying parameters of the electromagnet arrangement.
  • control valve assembly As is known from the DE 10 2009 046 332 A1 is known, can be exploited that the control chamber pressure and thus also a valve chamber pressure at the time of injection end experiences a characteristic, rapid increase.
  • the fact can be used that the guide rod is thus acted upon on its lower end face with the valve space pressure and above it is guided such that the guide is simultaneously a seal. Consequently, the guide rod is biased with an axial force that is proportional to the valve chamber pressure.
  • This axial force can be introduced, for example, in a piezoelectric sensor, which then emits a charge or voltage which is proportional to this biasing force and therefore proportional to the valve chamber pressure.
  • the piezo-controlled servo valve to analyze the actuator voltage signal to a typical resonant vibration, which is stimulated among other things by the closing of the nozzle needle.
  • the excitation takes place here on the one hand via the switching chain by the rapid increase of the valve chamber pressure at the moment of valve closing and on the other hand by acoustic transmission through the holding body, which is stimulated by the rapid increase of the nozzle seat force at the moment of the needle closing.
  • a design as they are from the DE 10 2009 046 332 A1 is known, but this is not a targeted detection of the valve space pressure curve, but only the detection of a parasitic excited by the needle closing vibration possible.
  • the detection method for the injection end in a piezoelectrically actuated servo valve is much less robust and much more susceptible to interference than in an electromagnetically actuated control valve assembly, as shown in DE 10 2009 046 332 A1 is known.
  • one in the fuel pressure load level is essential smaller functional area for the detection of an injection end at the piezo injector in comparison to a solenoid valve injector.
  • the fuel injection valve according to the invention with the features of claim 1 has the advantage that an improved design is possible.
  • a portion can be coupled into a biasing force of the piezoelectric actuator, which depends on the pressure in the valve chamber and in particular is proportional to the pressure in the valve chamber.
  • the force transmission element is arranged at least in sections in the valve closing body.
  • the force transmission element may be guided at least in sections in the valve closing body. This is particularly advantageous in a possible embodiment in which the force transmission element is designed as a rigid force transmission element.
  • the force transmission element can then be formed, for example, from a metal or a metallic alloy.
  • the force transmission element may also be formed of a fuel-resistant, elastic plastic or based on a fuel-resistant, elastic plastic.
  • the force transmission element transmits the force which results from the application of pressure to the end face of the force transmission element to the pressure in the valve space, at least indirectly to the actuator.
  • the transmission in practice will regularly be a lossy transmission.
  • the transmission losses will usually arise in embodiments in which the force transmission element is formed of a fuel-resistant, elastic plastic.
  • transmission losses can be accommodated by appropriate adjustments.
  • this can be realized structurally by means of a suitable adaptation with regard to the configuration, in particular the size, of the end face, which is acted upon by the pressure in the valve chamber.
  • the power transmission element is configured in a possible embodiment as a rigid power transmission element.
  • the force transmission element can be configured as a pin-shaped force transmission element.
  • the force transmission element it is also possible for the force transmission element to transmit the force which results from the application of pressure to the end face of the force transmission element to the pressure in the valve space, at least substantially unattenuated to the actuator.
  • the actuator actuates the valve closing body by means of a mechanical transmission device and that the force transmission element transmits the force to the actuator by means of the mechanical transmission device.
  • the force can be transmitted indirectly from the power transmission element to the actuator.
  • the transmission device can also achieve a force transmission or displacement transmission between the actuator and the valve closing body. Conversely, then results in a power transmission from the power transmission element to the actuator by means of the mechanical transmission device.
  • a biasing force or an additional biasing force can be exerted on the actuator in an advantageous manner, which depends on the pressure in the valve chamber.
  • the actuator is designed as a piezoelectric actuator.
  • the actuation of the actuator which depends on the pressure in the valve chamber, for piezoelectric actuators, to use the actuator in this case as a sensor with a good resolution is suitable.
  • the actuator actuates the valve closing body by means of a hydraulic transmission device and that the force can be transmitted to the actuator by a mechanical bridging of the hydraulic transmission device from the force transmission element.
  • a transfer of the dynamic Aktorhubs can be achieved on the nozzle needle in an advantageous manner.
  • the actuator can be applied to a certain extent with a DC component, although the hydraulic transmission device can only transfer alternating parts.
  • the hydraulic transmission device can be designed as a hydraulic coupler.
  • the actuator can be designed as a piezoelectric actuator in a corresponding manner.
  • the hydraulic transmission device has a coupler space and a coupler body, that a low-pressure space is provided, that between the low-pressure space and the valve space, a sealing seat formed by the valve closing body is predetermined, that an actuator-side end of the coupler body limits the coupler space a valve-closing body-side end face of the coupler body bears against the valve closing body and that the force transmission element and / or at least one further force transmission element are guided through the coupler body.
  • a mechanical power transmission from the power transmission element can be effected at least indirectly on the actuator, which bridges the hydraulic transmission device.
  • a seal is realized in a suitable manner.
  • the dynamic actuation by the actuator leads to a relatively short pressure increase in the coupler space, which considerably simplifies the sealing.
  • the coupler body has a through hole and that the at least one further force transmission element is guided at least substantially continuously along the through hole of the coupler body.
  • at least one further force transmission element is provided, wherein a certain seal between the at least one further force transmission element and the through hole is realized to allow the pressure increase in the coupler space.
  • a transfer of the DC component of the pressure in the valve chamber to the actuator is possible via the at least one further force transmission element.
  • the coupler body has a through-bore extending through the coupler body, that the at least one further force-transmitting element in an extended Guiding portion of the through hole of the coupler body is guided and that extends the extended guide portion of the through hole to the actuator-side end face of the coupler body.
  • the force transmission element rests against the further force transmission element in the area of the valve closing body-side end face of the coupler body.
  • the force transmission element can be guided on the valve closing body of the control valve.
  • the further power transmission element can be guided independently of the force transmission element in the coupler body. This prevents over-determination.
  • valve closing body has a through hole in which the force transmission element is guided.
  • the bore can be configured in particular as an axial bore with respect to the valve closing body.
  • the valve closing body has a blind hole in which the force transmission element is guided, that an end face of the force transmission element in the blind hole delimits a pressure chamber and that the valve closing body has at least one lateral connection bore, which the pressure chamber with the valve chamber combines.
  • an embodiment of the control valve can be realized with a bypass or the like.
  • a side facing away from the pressure-relieved space end face of the valve closing body can be acted upon at least temporarily or in response to a switching position of the control valve by a pressure which differs from the pressure in the valve chamber, with which the end face of the force transmission element is acted upon.
  • a low-pressure chamber is provided, that between the low-pressure chamber and the valve chamber a sealing seat formed by the valve closing body is provided and that a remote from the low pressure chamber end face of the valve closing body in a valve sleeve, in which the valve closing body is guided, a pressure relieved Subspace separated from the valve chamber.
  • the power transmission element which is preferably guided in the valve closing body, for example, be designed as a rigid pin, which enables the generation of a force and their forwarding to a piezoelectric actuator when pressurized.
  • a purely mechanical coupling or a hydraulic coupling between the valve closing body and the actuator can be provided.
  • the seal between the force transmission element and the valve closing body of the control valve can be realized via a tight guide play.
  • this form of sealing entails that in this guide a permanent leakage occurs, which additionally heats the low-pressure region of the fuel injection valve and requires a correspondingly enlarged dimensioning of the high-pressure pump of the fuel injection system.
  • the sealing between the force transmission element and the valve closing body of the control valve via sealing elements as they come in a corresponding manner in other components of a motor vehicle, for example in anti-lock braking systems (ABS) or ESP systems used. Then, a leakage in the leadership of the power transmission element can be avoided.
  • ABS anti-lock braking systems
  • ESP ESP systems
  • the power transmission element in the practical implementation may be very small and consequently the bore (guide bore) in the valve closing body in which the power transmission element is guided, a small diameter, for example of at most 1 mm. With these small dimensions, the realization of a defined guide clearance or the installation of separate sealing elements may be difficult.
  • An advantageous solution of the problems just mentioned is not to carry out the force transmission element of a rigid material, such as a metal, but from a fuel-resistant, elastic plastic. Particularly suitable for this purpose is a silicone material. If such a force transmission element is subjected to an axial force, then it shortens and at the same time expands in the radial direction. As a result, the force transmission element engages positively against an inner wall of the guide bore and thus seals this guide completely.
  • the force transmission element is at least partially formed from a material which is based on a fuel-resistant, elastic plastic.
  • the material has reinforcing elements and that the plastic is reinforced by the reinforcing elements.
  • the Permanent leakage can be avoided on the leadership of the power transmission element.
  • a sufficient durability with respect to the size of the force occurring during operation, which results from the application of the pressure to the end face of the force transmission element in the valve chamber, can be achieved by optionally provided reinforcing elements in the plastic.
  • the reinforcing elements may in this case be configured advantageously as glass fibers and / or carbon fibers and / or metal particles.
  • the number of reinforcing elements per unit volume and the selection of suitable reinforcing elements in this case an adaptation to the particular application is possible.
  • the force transmission element is at least partially inserted into a bore of the valve closing body and that the force transmission element when loading the end face of the force transmission element with the pressure in the valve chamber form fit to an inner wall of the bore of the valve closing body, in which the force transmission element is arranged invests.
  • the power transmission element during assembly can first be introduced into the bore of the valve closing body.
  • pressure is then achieved by the generated axial force and the resulting transverse strain, the positive application of the force transmission element to the inner wall of the bore.
  • the force transmission element may be configured cylindrical before the first pressurization.
  • elastic plastic which is optionally reinforced, are also injected into the bore of the valve closing body to design in this way a connected to the valve closing body power transmission element.
  • a dimensionally stable sealing element is at least partially disposed in the bore of the valve closing body, that the sealing element on the further end face of the force transmission element, which faces away from the end face of the force transmission element, and that the force transmission element, the force on the sealing element at least indirectly transfers to the actor.
  • the dimensionally stable sealing element can in particular be designed as a metallic sealing element be.
  • Fig. 1 shows a first embodiment of a fuel injection valve 1 in a partial, schematic sectional view.
  • the fuel injection valve 1 can serve in particular as an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • a preferred use of the fuel injection valve 1 is for a fuel injection system with a common rail, the diesel fuel under high pressure leads 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 partially illustrated housing 2, a throttle plate 3 and a valve piece 4. Furthermore, a nozzle body 5 is provided, which is connected in a suitable manner, in particular via a nozzle retaining nut, with the housing 2. The throttle plate 3 and the valve piece 4 are disposed within the housing 2 and the nozzle body 5.
  • a piezoelectric actuator 6 is arranged with a protective sleeve 7.
  • An actuator head attached to the piezoelectric actuator 6 is connected to the protective sleeve 7 via a deformable membrane 9.
  • the piezoelectric actuator 6 is sealed off from a pressure-relieved space (low-pressure space) 10, via which a reflux of fuel takes place during operation.
  • a control unit 11 is provided, which is connected to the piezoelectric actuator 6.
  • a fuel chamber 12 is formed, which is filled via a fuel line 13, which is partially guided by the throttle plate 3, in operation with fuel.
  • a nozzle needle 14 is arranged, which cooperates with a valve seat surface 15 to a sealing seat.
  • An end face 16 of the nozzle needle 14, which faces the throttle plate 3, defines a control chamber 17, which is formed within a sleeve 18.
  • the nozzle needle 14 is in this case guided in the sleeve 18.
  • the sleeve 18 is acted upon by a spring 19 against the throttle plate 3, so that the control chamber 17 is separated from the fuel chamber 12.
  • control chamber 17 is filled with fuel via an inlet throttle 20 configured in the throttle plate 3.
  • the pressure in the control chamber 17 is controlled by a control valve 30.
  • the actuation of the control valve 30 takes place here by the piezoelectric actuator 6.
  • the control valve 30 has a valve closing body 31 which is at least partially disposed in a valve chamber 32.
  • a valve seat surface 33 is formed on the valve piece 4.
  • the valve closing body 31 cooperates with the valve seat surface 33 to form a sealing seat.
  • the valve closing body 31 is acted upon by a valve spring 34 against the valve seat surface 33.
  • the valve closing body 31 of the control valve 30 is indirectly actuated by the actuator 6 in this embodiment.
  • the actuator 6 actuates the valve closing body 31 by means of a transmission device 36.
  • the transmission device 36 is designed as a mechanical transmission device 36, which converts the stroke of the piezoelectric actuator 6 in a corresponding stroke of the valve closing body 31.
  • this can also be a path translation or force transmission.
  • a power transmission element 37 is provided.
  • the valve closing body 31 has a through bore 38, in which the force transmission element 37 is guided.
  • the force transmission element 37 has an end face 39 with an effective area A.
  • the force transmission element 37 is guided along an axis 40 of the valve-closing body 31, which in this embodiment is also the axis 40 of the through-bore 38.
  • the end face 39 is in this embodiment in a plane which is oriented perpendicular to the axis 40. Thereby, the area of the end face 39 is equal to the effective area 39A.
  • the effective area A results as a projection of the end face 39 in such a plane which is oriented perpendicular to the axis 40.
  • a pressure p V acts on the end face 39 a.
  • Due to the through bore 38 of the valve closing body 31 is configured so that the end face 39 of the force transmission element 37 is acted upon by the pressure p V in the valve chamber 32, so that the force transmission element 37, a force F acts.
  • the force F results from the application of the end face 39 with the pressure p V in the valve chamber 32.
  • the force F results here as a product of the effective area A and the pressure p V. In particular, the force F is thus proportional to the pressure p V in the valve chamber 32.
  • the valve closing body 31 has a sleeve-shaped extension 41, which extends through the pressure-relieved space 10 to the transmission device 36.
  • a small distance between the sleeve-shaped extension 41 and a contact surface 42 of the transmission device 36 may be provided in order to allow a reliable closing of the valve closing body 31 with respect to possible tolerances, temperature-related expansions and the like. From a preferably small stroke of the actuator 6, it then comes to operate the Valve-closing body 31, in which the sleeve-shaped extension 41 is then in contact with the contact surface 42 of the transmission device 36.
  • the force transmission element 37 is axially movable in the through bore 38 and is always on the contact surface 42 of the transmission device 36 at. In this case, the force transmission element 37 transmits the force F dependent on the pressure p V in the valve space 32 to the piezoelectric actuator 6 by means of the mechanical transmission device 36.
  • the mechanical transmission device 36 may be designed as a rigid transmission device 36. However, the transmission device 36 may also be designed as a mechanical switching chain for force and displacement transmission between the actuator 6 and the valve closing body 31.
  • the mechanical transmission device 36 transmits the DC component of a force, so that the force transmission element 37 can be supported directly on the transmission device 36 in order to transmit the axial force F.
  • the through hole 38 extends axially and centrally in the valve closing body 31. In this case, the through hole 38 preferably has a small diameter. In a modified embodiment, an embodiment of the through bore 38 with a center offset is possible. Furthermore, an only approximately axial guidance of the force transmission element 37 may be sufficient.
  • the seal between the force transmission element 37 and the through bore 38 can be done by a small guide clearance and / or by suitable sealing elements, as they come for high pressure systems, especially high pressure pumps or the like used.
  • a force P proportional to the pressure p V in the valve chamber 32 can be permanently introduced into the transmission device 36 and thus transmitted to the actuator 6.
  • the control unit 11 can use the piezoelectric actuator 6 as a sensor to detect vibrations emanating from the nozzle needle 14. This results in the advantage that a broad frequency band of the pressure p V in the valve chamber 32, including its DC component, is transmitted to the biasing force of the piezoelectric actuator 6. This is made possible by the force transmission element 37.
  • the increase in the pressure in the control chamber 17 and thus also the increase in the pressure p V in the valve chamber 32 at the end of injection leads to a correspondingly constant increase in the actuator voltage and a nearly exact mapping of the pressure p V in the actuator voltage. This allows a much more accurate detection of an end of an injection process, which in addition is allowed to a much larger area of a fuel pressure load range.
  • the Aktorvorschreib is significantly increased by the transmission of the pressure p V in the valve chamber 32 proportional force F on the actuator 6, especially at high pressures, and serving as a spring sleeve 7 protective sleeve 7 can be biased lower.
  • a weaker and cheaper design of the protective sleeve (spring sleeve) 7 is made possible. Since caused by the pressure p V force F is constantly applied to the actuator, so even in its not controlled state, and 13 greatly decreases when opening the control valve 13 for actuating the nozzle needle 14, this solution also contributes to the power relief of the control valve 13 and a reduction the voltage requirement of the actuator 6 at.
  • Fig. 2 shows the in Fig. 1 labeled II section of the fuel injection valve 1 in an excerpt, schematic sectional view according to a second embodiment.
  • the valve closing body 31 has a blind hole 43 in which the force transmission element 37 is axially guided.
  • the end face 39 of the force transmission element 37 limits this in the blind hole 43 a pressure chamber 44.
  • the valve closing body 31 has lateral connection bores 45, 46, which connect the pressure chamber 44 with the valve chamber 32.
  • the application of the end face 39 of the force transmission element 37 thus does not take place with its effective area A from a bottom 47 of the valve closing body 31, as in the case of the Fig. 1 described embodiment of the case, but of a lateral surrounding area of the valve closing body 31 in the valve chamber 32.
  • the lateral surrounding area 48 encloses the valve closing body 31 in this case circumferentially.
  • the bottom 47 is designed as a closed end 47.
  • Fig. 3 shows the in Fig. 1 With II designated section of the fuel injector 1 in a partial, schematic sectional view corresponding to a third Embodiment.
  • the control valve 30 is designed as a pressure-relieved control valve 30.
  • the power transmission element 37 is guided in the blind hole 43.
  • the configured in the blind hole 43 pressure chamber 44 is connected via the lateral connection holes 45, 46 with the valve chamber 32, so that in the pressure chamber 44, the pressure p V acts as in the valve chamber 32.
  • valve closing body 31 in this embodiment, a guide portion 49 which extends from the bottom (front side) 47 in the axial direction.
  • control valve 30 has a valve sleeve 50, in which the valve closing body 31 is axially guided with its guide portion 49.
  • Adjoining the underside 47 of the valve closing body 31 is a partial space 51, which is separated from the valve space 32, in which the pressure p V prevails, by the valve sleeve 50.
  • the subspace 51 is connected via a connection 52 with the pressure-relieved space 10.
  • the pressure-relieved space 10 is a low-pressure space 10, in which a much lower pressure than in the valve chamber 32 prevails when the sealing seat between the valve closing body 31 and the valve seat surface 33 is closed.
  • This embodiment has the advantage that the actuation force for opening the sealing seat formed between the valve closing body 31 and the valve seat surface 33 is reduced.
  • control valve 30 may also be provided a Guidedrossel 53, which serves as a bypass, for example, to allow faster closing of the nozzle needle 14.
  • a Basal throttle 53 which serves as a bypass, for example, to allow faster closing of the nozzle needle 14.
  • the pressure from the valve chamber 32 can be increased faster via the filling throttle 43.
  • it can also lead to an opposite flow through the outlet throttle 35, wherein the control chamber 17 is at least temporarily filled not only via the inlet throttle 20, but also on the outlet throttle 35, which is made possible by the filling of the control chamber 32 via the Basdrossel 53.
  • Fig. 4 shows a fuel injection valve 1 in an excerpt, schematic sectional view according to a fourth embodiment.
  • the valve closing body 31 the through hole 38, in which the power transmission element 37 is axially guided.
  • the transmission device 36 is configured in this embodiment as a hydraulic transmission device 36.
  • the actuator 6 actuates the valve closing body 31 for opening the nozzle needle 14 in this embodiment by means of the hydraulic Transmission device 36. This can be done Hubbergersville or force transmission.
  • the hydraulic transmission device 36 has a coupler space 60, a coupler body 61 and a further coupler body 62, the coupler bodies 61, 62 being guided in a coupler housing 59.
  • the piezoelectric actuator 6 mechanically actuates the further coupler body 62.
  • the stroke of the actuator 6 thus directly effects a stroke of the further coupler body 62.
  • the displacement of the fuel in the coupler space 60 which takes place through the stroke of the further coupler body 62, then leads to a hydraulically transmitted movement of the Coupler body 61.
  • an actuator-side end face 77 of the coupler body 61 limits the coupler space 60.
  • the coupler body 61 in turn acts on the valve closure body 31.
  • the coupler body 61 can not simply be acted upon in this case because an act of subjecting the coupler body 61 to the DC component of the force F leads to an empty-pressing due to a functionally required throttled leakage of the coupler space 60 until the coupler body 61 rests against the further coupler body 62.
  • the operation of the hydraulic transmission device 36 would no longer be guaranteed, since in this movement of the coupler body 61 and the contact between the contact surface 42 on the coupler body 61 and the sleeve-shaped extension 41 of the valve closing body 31 is released.
  • another power transmission member 63 is provided which extends through a through hole of the coupler body 61.
  • the through-hole 64 is designed as an axial through-hole 64. Further, the through hole 64 is centered through the coupler body 61.
  • the other power transmission member 63 is continuously guided along the through hole 64 of the coupler body 61.
  • the coupler body 61 is between the coupler space 60 and the low pressure space 10 is arranged.
  • the further force transmission element 63 extends on the one hand through the coupler space 60 and on the other hand it is led to the low-pressure space 10.
  • the further coupler body 62 has a side 65 adjacent to the coupler space 60.
  • the further force transmission element 63 has an end face 66. With the end face 66, the further force transmission element 63 abuts on the side 65 of the further coupler body 62.
  • the contact surface 42 is designed as a valve closing body-side end face 42 of the coupler body 61.
  • the force transmission element 37 rests with its end face 67 against an end face 68 of the further force transmission element 63.
  • the end face 68 of the further force transmission element 63 is in this case facing away from the end face 66.
  • the force F which acts on the force transmission element 37 against the further force transmission element 63 is formed.
  • the force F is thus forwarded by the further force transmission element 63 to the further coupler body 62.
  • the force is introduced into the piezoelectric actuator 6 via the further coupler body 62.
  • a bias of the actuator 6 with the force F.
  • the force F which depends on the pressure p V in the valve chamber 32, by a mechanical bridging of the hydraulic transmission device 36 of the power transmission element 37 and the other Power transmission element 63 to the actuator 6 transferable.
  • the through-bore 64 can also be designed in other ways.
  • the through-bore 64 may also extend eccentrically through the coupler body 61.
  • the through-bore 64 may also be designed as a guide bore only on a part of its length. In this case, a seal or a sufficiently large throttling effect is ensured in a suitable manner in order to allow the pressure build-up in the coupler space 60 required for the functioning of the hydraulic transmission device 36.
  • the seal along the guide of the further force transmission element 63 in the through hole 64 can be done by a small guide clearance or by sealing elements.
  • the end faces 67, 68 of the power transmission element 37 and the further force transmission element 63 are designed so that an advantageous power transmission is possible and at the same time a certain distance to the contact surface 42 of the coupler body 61 or to the sleeve-shaped extension 41 is guaranteed to snag on the Coupler body 61 or the sleeve-shaped extension 41 to prevent.
  • the force F is advantageously forwarded by a contact with the coupler body 61 or the sleeve-shaped extension 41 in the region of the end faces 67, 68 is avoided.
  • Fig. 5 shows the fuel injection valve 1 in an excerpt, schematic sectional view according to a fifth embodiment.
  • the further power transmission element 63 has a larger diameter portion 69 and a smaller diameter portion 70.
  • the through-bore 64 is designed as a stepped bore 64.
  • the through-hole 64 has an extended guide portion 71 extending to the actuator-side end face 77 of the coupler body 61, and a portion 72 having a diameter smaller than a diameter of the extended guide portion 71.
  • the further force transmission element 63 is sealingly guided at its portion 69.
  • an annular gap 73 is formed between the section 70 of the further force-transmitting element 63 and the section 72 of the through-hole 64.
  • the sealing of the coupler space 60 with respect to the low-pressure chamber 10 thus takes place in the region of the extended guide section 71 of the through-bore 64.
  • the through-bore 64 thus functions only in the guide section 71 as a guide in this exemplary embodiment.
  • the further force transmission element 63 is guided on one or more sections of the through bore 38 of the valve closing body 31.
  • Fig. 6 shows a diagram for explaining the operation of the fuel injection valve 1 according to a possible embodiment of the invention.
  • a signal in particular a voltage signal U
  • the abscissa shows the time.
  • the Control unit 11 can detect the actuator voltage 6.
  • a suitable voltage can be applied to the piezoelectric actuator 6.
  • the actuator 6 is acted upon by an actuating voltage.
  • the signal here is very large, which is illustrated by arrows 74, 75. The voltage swing between the times t 1 and t 2 is therefore only shown in a hint.
  • the closing of the nozzle needle 14 occurs.
  • a characteristic pattern 76 occurs in the signal curve U (t). Because when closing the nozzle needle 14, there is a typical, excited by the nozzle needle closing vibration 76. This vibration 76 follows the closing of the nozzle needle 14, so that the end of the injection can be determined at the time t 3 .
  • the oscillation occurs in the form of the characteristic pattern 76. Between the times t 2 and t 3 , the oscillation initially decreases, as it corresponds, for example, to a typical attenuation, while after the time t 3 an oscillation with now greater amplitude occurs again.
  • the vibration characterized by the pattern 76 is an additional excited vibration due to needle closure.
  • an injection end detection can be realized in an advantageous manner.
  • the fuel injection valve 1 can thus be designed in particular when using a piezoelectric actuator 6 so that a specific suitability for detecting an end of an injection process, as shown in the Fig. 6 is illustrated by the time t 3 exists.
  • Fig. 7 shows the in Fig. 1 Section II of the fuel injection valve 1 in a partial, schematic sectional view corresponding to a sixth Embodiment when new before a first pressurization.
  • the control valve 30 has a valve closing body 31 with an axial, continuous bore 38.
  • the power transmission element 37 is introduced in the through hole 38.
  • the power transmission element 37 is formed in this embodiment of a material based on a fuel-resistant, elastic plastic.
  • the power transmission element 37 is in this case designed cylindrical in the new state.
  • the through bore 38 in this exemplary embodiment is not exactly cylindrical.
  • an annular gap 81 is formed between an inner wall 80 of the through bore 43 and the cylindrical force transmission element 37.
  • a further end face 67 of the power transmission element 37 which is remote from the pressurized in operation end face 39 of the power transmission element 37, in the new state, a slight distance of the power transmission element 37 to the contact surface 42 of the transmission device 36 and / or the other end face 82 is not accurate be designed plan.
  • Fig. 8 shows the in Fig. 7 shown section of the fuel injection valve 1 according to the sixth embodiment in the state with pressurization.
  • the axial force F is generated. Due to the resulting axial force F on the force transmission element 37, this deforms elastically, wherein it is shortened in the longitudinal direction and expands in the radial direction.
  • a partial plastic deformation of the force transmission element 37 is possible and permissible.
  • existing cavities between the power transmission element 37 and the inner wall 80 of the bore 38 and between the power transmission element 37 and the contact surface 42 of the transmission device 36 are completely filled.
  • the annular gap 81 is filled up by the deformation of the force transmission element 37, so that it disappears, at least for the duration of the pressurization.
  • the force transmission element 37 evenly against the inner wall 80 of the through bore 38 at.
  • the power transmission element 37 is wholly or partly formed from the material, which is based on the fuel-resistant, elastic plastic.
  • the contact surface or contact line between the other end face 67 of the force transmission element 37 and the contact surface 42 is preferably not closed circumferentially, but executed interrupted. This can be realized, for example, by means of small grooves or notches in at least one of the two surfaces, that is to say on the end face 39 and / or on the contact surface 42. However, in the concrete case of application, this may involve the risk that the force transmission element 37 may be extruded at high loads through such grooves or notches and thus ultimately damaged or destroyed.
  • a dimensionally stable sealing element 83 can be introduced above the force transmission element 37 in the bore 38, as it is based on the Figures 9 and 10 is described in more detail.
  • a reinforcement of the material which is based on the elastic plastic, be provided by reinforcing elements of higher-strength materials.
  • Glass fibers, carbon fibers or metal particles and suitable mixtures of such fibers and / or particles can be used.
  • Fig. 9 shows the in Fig. 1 labeled II section of the fuel injector 1 in a partial, schematic sectional view according to a seventh embodiment of the invention.
  • the dimensionally stable sealing element 83 is arranged between the further end face 67 of the force transmission element 37 and the contact surface 42 of the transmission device 36.
  • the further end face 67 has a configuration adapted to the surface 84 of the sealing element 83.
  • the further end face 67 is designed partially spherical and concave. In this way, the sealing element 83 can be partially inserted into the force transmission element 37, wherein it bears against the further end face 67.
  • the dimensionally stable sealing element 83 is preferably made of metal and has a guide clearance to the inner wall 80 of the bore 38, in which it is at least partially inserted.
  • the guide play is large enough to ensure easy production of the through bore 38 of the valve closing body 31 and of the dimensionally stable sealing element 83, and on the other hand is small enough to reliably prevent extrusion of the force transmission element 37 through the guide gap.
  • the guide clearance of the sealing element 83 in the bore 38 may be on the order of 10 ⁇ m.
  • the material for the power transmission element 37 which is based on the elastic plastic, can be stabilized by said reinforcing elements.
  • glass fibers, carbon fibers or metal particles in question for example, glass fibers, carbon fibers or metal particles in question.
  • the dimensionally stable sealing element 83 is designed in this embodiment as a spherical sealing element. In a modified embodiment, the dimensionally stable sealing element 83 may also be designed as a cylindrical sealing element 83. Furthermore, other modifications with respect to the configuration of the sealing element 83 are possible.
  • the further end face 67 of the force transmission element 37 may in this case be adapted to the surface 84 of the sealing element 83 in its respective configuration.
  • Fig. 10 shows a fuel injection valve 1 in a partial, schematic sectional view according to an eighth embodiment of the invention.
  • the control valve 30 is connected to the piezoelectric actuator 6 via a transmission device 36 designed as a hydraulic coupler 36.
  • the hydraulic coupler 36 acts as a high pass and thus can not transmit stationary forces. Therefore, the force F is transmitted in this embodiment via the further power transmission element 63 to the other coupler body 62.
  • the basic principle corresponds to the fourth embodiment, which is based on the Fig. 4 is described, or the fifth embodiment, based on the Fig. 5 is described. Since the power transmission element 37 in the now using the Fig.
  • the 10 described eighth embodiment is at least partially formed of the material, which is based on the fuel-resistant, elastic plastic, it may in a possible embodiment in which the force transmission element 37 acts directly on the further force transmission element 63, at the contact point between the force transmission element 37 and further force transmission element 63 in the respective application to an extrusion of the force transmission element 37 come.
  • the dimensionally stable sealing element 83 is additionally provided, as shown in the Fig. 10 is shown.
  • the dimensionally stable sealing element 83 is in this case arranged between the force transmission element 37 and the further force transmission element 63.
  • the power transmission member 37 is prevented from extruding at the contact point to the other power transmission member 63.
  • the potential scope can be increased.
  • the power transmission element 37 may advantageously be at least partially formed of a material based on a fuel-resistant, elastic plastic. In a modified embodiment, it may also be particularly advantageous not to manufacture the power transmission element 37 separately and to insert it into the bore 38 of the valve closing body 31, but to inject it directly into the through bore 38 of the valve closing body 31. In one embodiment, in which a dimensionally stable sealing element 83 is provided, the dimensionally stable sealing element 83 can already be inserted into the bore 38 before the material for the force transmission element 37 is injected into the bore 38. In this way, the finished valve closing body 31 can be easily made with the power transmission element 37 and the dimensionally stable sealing element 83.
  • control valve 30 advantageous embodiments of the control valve 30 are possible in which the dimensionally stable sealing element 83 bears against the further end face 67 of the force transmission element 37, wherein the force transmission element 37 transmits the force F via the sealing element 83 at least indirectly to the actuator 6.
EP14165002.8A 2013-06-10 2014-04-16 Soupape d'injection de combustible Active EP2813698B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013210745 2013-06-10
DE201310222650 DE102013222650A1 (de) 2013-06-10 2013-11-07 Brennstoffeinspritzventil

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EP2813698A1 true EP2813698A1 (fr) 2014-12-17
EP2813698B1 EP2813698B1 (fr) 2016-06-08

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DE (1) DE102013222650A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016059069A1 (fr) * 2014-10-15 2016-04-21 Continental Automotive Gmbh Injecteur piezo à rampe commune à compensation de jeu hydraulique intégré dans la servosoupape
WO2018068926A1 (fr) * 2016-10-14 2018-04-19 Continental Automotive Gmbh Injecteur asservi comportant une chambre d'injection à volume minimal

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1640604A1 (fr) * 2004-09-23 2006-03-29 Siemens Aktiengesellschaft Servovalve et soupape d'injection
EP1703119A1 (fr) * 2005-02-28 2006-09-20 Robert Bosch Gmbh Buse d'injection de carburant
DE102005030132A1 (de) * 2005-06-28 2007-01-04 Siemens Ag Injektor, insbesondere Kraftstoffinjektor
DE102005040533A1 (de) * 2005-08-26 2007-03-15 Siemens Ag Verfahren und Vorrichtung zum Erkennen eines Erreichens eines maximalen Öffnungszustands oder Schließzustands eines Ventils
EP1939441A2 (fr) * 2006-12-21 2008-07-02 Robert Bosch Gmbh Injecteur de carburant
DE102009000170A1 (de) * 2009-01-13 2010-07-15 Robert Bosch Gmbh Kraftstoffinjektor
DE102009046332A1 (de) 2009-11-03 2011-05-05 Robert Bosch Gmbh Steuerventilanordnung
EP2354526A2 (fr) * 2010-01-28 2011-08-10 Robert Bosch GmbH Injecteur de carburant
DE102011078159A1 (de) * 2011-06-28 2013-01-03 Robert Bosch Gmbh Kraftstoffeinspritzventil
WO2013098307A1 (fr) * 2011-12-28 2013-07-04 Robert Bosch Gmbh Injecteur de carburant pour moteurs à combustion interne

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1640604A1 (fr) * 2004-09-23 2006-03-29 Siemens Aktiengesellschaft Servovalve et soupape d'injection
EP1703119A1 (fr) * 2005-02-28 2006-09-20 Robert Bosch Gmbh Buse d'injection de carburant
DE102005030132A1 (de) * 2005-06-28 2007-01-04 Siemens Ag Injektor, insbesondere Kraftstoffinjektor
DE102005040533A1 (de) * 2005-08-26 2007-03-15 Siemens Ag Verfahren und Vorrichtung zum Erkennen eines Erreichens eines maximalen Öffnungszustands oder Schließzustands eines Ventils
EP1939441A2 (fr) * 2006-12-21 2008-07-02 Robert Bosch Gmbh Injecteur de carburant
DE102009000170A1 (de) * 2009-01-13 2010-07-15 Robert Bosch Gmbh Kraftstoffinjektor
DE102009046332A1 (de) 2009-11-03 2011-05-05 Robert Bosch Gmbh Steuerventilanordnung
EP2354526A2 (fr) * 2010-01-28 2011-08-10 Robert Bosch GmbH Injecteur de carburant
DE102011078159A1 (de) * 2011-06-28 2013-01-03 Robert Bosch Gmbh Kraftstoffeinspritzventil
WO2013098307A1 (fr) * 2011-12-28 2013-07-04 Robert Bosch Gmbh Injecteur de carburant pour moteurs à combustion interne

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016059069A1 (fr) * 2014-10-15 2016-04-21 Continental Automotive Gmbh Injecteur piezo à rampe commune à compensation de jeu hydraulique intégré dans la servosoupape
CN106795851A (zh) * 2014-10-15 2017-05-31 大陆汽车有限公司 具有集成到伺服阀中的液压的间隙补偿件的压电共轨喷射器
US10233885B2 (en) 2014-10-15 2019-03-19 Continental Automotive Gmbh Piezo common rail injector with hydraulic clearance compensation integrated into the servo valve
CN106795851B (zh) * 2014-10-15 2019-06-18 大陆汽车有限公司 具有集成到伺服阀中的液压的间隙补偿件的压电共轨喷射器
WO2018068926A1 (fr) * 2016-10-14 2018-04-19 Continental Automotive Gmbh Injecteur asservi comportant une chambre d'injection à volume minimal

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EP2813698B1 (fr) 2016-06-08

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