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WO2017118562A1 - Vanne de commande pour un système d'injection de carburant, pompe à haute pression de carburant pour un système d'injection de carburant ainsi que procédé de commande pour commander une vanne de commande dans une pompe à haute pression de carburant - Google Patents

Vanne de commande pour un système d'injection de carburant, pompe à haute pression de carburant pour un système d'injection de carburant ainsi que procédé de commande pour commander une vanne de commande dans une pompe à haute pression de carburant Download PDF

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Publication number
WO2017118562A1
WO2017118562A1 PCT/EP2016/081682 EP2016081682W WO2017118562A1 WO 2017118562 A1 WO2017118562 A1 WO 2017118562A1 EP 2016081682 W EP2016081682 W EP 2016081682W WO 2017118562 A1 WO2017118562 A1 WO 2017118562A1
Authority
WO
WIPO (PCT)
Prior art keywords
spring
switching valve
force
spring force
closing element
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.)
Ceased
Application number
PCT/EP2016/081682
Other languages
German (de)
English (en)
Inventor
Andreas Mühlbauer
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.)
Continental Automotive GmbH
Original Assignee
Continental Automotive 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 Continental Automotive GmbH filed Critical Continental Automotive GmbH
Publication of WO2017118562A1 publication Critical patent/WO2017118562A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0075—Stop members in valves, e.g. plates or disks limiting the movement of armature, valve or spring
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F02M59/368—Pump inlet valves being closed when actuated
    • 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
    • F02M2200/50—Arrangements of springs for valves used in fuel injectors or fuel injection pumps
    • F02M2200/505—Adjusting spring tension by sliding spring seats

Definitions

  • the invention relates to a switching valve for a fuel ⁇ injection system of an internal combustion engine, a high-pressure fuel pump for such a fuel injection system, which in particular has a corresponding switching valve, and a drive method for driving such a switching valve, which is arranged in a high-pressure fuel pump.
  • the fuel is usually compressed to a high pressure, for example to a pressure between 1500 bar and 3000 bar with diesel as fuel or a pressure between 150 bar and 500 bar with gasoline as
  • Fuel in order to be able to meet requirements, for example, for legally prescribed emission values.
  • the pressurized with such a pressure fuel is then injected via injectors in combustion chambers of the internal combustion engine.
  • the fuel injection system can be provided at various Po sitions of the path that takes the fuel from a tank to the injectors, valve arrangements, and in particular switching ⁇ valves, for example as inlet or off ⁇ outlet valves of a pressure chamber in which the fuel with the above high pressure is applied. It is also possible to provide such switching valves as relief valves at different positions of the fuel injection system, for example on a common rail, which is connected upstream of the injectors.
  • switching valves that are used in ⁇ example as intake valves in high-pressure fuel pumps, are often controlled by an actuator, such as a solenoid to the flow through the high-pressure fuel pump.
  • the medium is, that is, the fuel sucked into the pressure chamber of the high-pressure fuel pump through the Abforcebe ⁇ movement of a piston.
  • the switching valve z. B. is designed as an inlet valve, via a spring, such as a compression spring, as long as kept open until the fuel from a high pressure area can be promoted back into a low pressure region of the fuel injection system. This is called zero promotion.
  • the design of the spring takes place as a function of the flow rate at a maximum rotational speed value of the drive region, which drives the piston in the high-pressure fuel pump. However, this maximum speed value is rarely reached in reality. This causes that even at lower retrieved
  • the object of the invention is therefore to provide an improved switching valve for a fuel injection system of an internal combustion engine.
  • a high-pressure fuel pump having such a switching valve, as well as a driving method for driving such a switching valve, are the subject of the independent claims.
  • a switching valve for a fuel injection system of an internal combustion engine has a valve region with a Closing element and with a valve seat, which cooperate in operation for closing the switching valve. Furthermore, a spring is provided with a spring force acting along a spring force acting axis in a spring force acting direction for biasing the closing element into an open or closed position and an actuator area for moving the closing element in an actuating force direction opposite to the spring force acting direction.
  • the switching valve comprises an adjusting device for reversibly changing the spring force of the spring.
  • the adjusting device opens up new, more flexible ways to control the Aktuator Suitees, which regulates the flow of high-pressure fuel pump for example with an inlet valve of a fuel high-pressure pump ⁇ .
  • the load-specific adaptation of the spring force of the spring for example, the energy consumption of the actuator area can be reduced. If, for example, the actuator area is also activated in an optimized manner, there are also positive effects on the impact of components in the actuator area during the switching of the switching valve in the form of a reduced pulse, so that the noise emissions of the switching valve can be reduced.
  • the closing element is formed, for example, as a plate-shaped element, which cooperates with a valve plate as a valve seat and is be ⁇ less the valve plate on an opposite side of the spring.
  • the spring biases the closure member before the ⁇ ff ⁇ planning position, so that the switching valve must only be operated via the actuator area if it is to be closed. This is energetically cheaper than a preferred one Switching valve, which must open actively, since in the example of the above-described zero promotion, the switching valve must be kept open for a longer period than it remains closed.
  • the spring has a spring length extending along the spring force axis, wherein the verse ⁇ dividing device is designed for reversibly changing the spring length.
  • a compression device for compressing the spring along the spring force axis, wherein the compression device is in particular formed by a spring force axis along the movable compression piston, on which the spring is supported with a first spring end.
  • the adjusting device has a drive unit for driving the compression device, wherein the drive unit comprises an electromechanical actuator and / or an electromagnetic actuator and / or a thermal actuator and / or is formed by a hydraulic transmission.
  • the drive unit is advantageously controllable via a control device, so that the adjusting device can be selectively brought into the desired position as a function of external factors.
  • the adjusting device is for changing the Spring force designed such that the spring force during operation of the switching valve at any time greater than the determined counterforce.
  • the counterforce acts from the opposite side to the closing element as the spring force.
  • the counterforce is applied in the example of the high-pressure fuel pump by the hydraulic force on the closing element, which acts on the closing element during the ejection / compression phase of the high-pressure fuel pump.
  • the spring force is preferably at least in the case of the high-pressure fuel pump to keep the closing element in the open position to allow zero delivery. For this reason, during operation the spring force is advantageously greater than the determined counterforce at any time.
  • the force-determining device preferably has a detection device for detecting a rotational speed of a pump drive of a high-pressure fuel pump of the fuel injection system and a calculation device for calculating the counterforce from the determined rotational speed.
  • the calculation device advantageously has a conversion device which can convert the determined rotational speed into a pressure value, for example with the aid of a stored characteristic map, wherein the corresponding counterforce can then be calculated from this pressure value.
  • the adjusting device for reversibly changing an actuator force of the actuator region is designed such that during operation of the actuator region
  • Actuator force is applied, which is greater than the present at the time of operation of the actuator range spring force of the spring.
  • the adjusting device is accordingly not only designed for reversibly changing the spring force of the spring itself, but additionally advantageously also designed to specifically control the actuator region in order to be able to save energy here. Accordingly, the actuator area is controlled at each operating time of the switching valve exactly that the spring force of the spring can be suppressed when the valve is to perform a counter to the spring force acting direction aligned movement. For this purpose, it is advantageously predefined that always the controlled actuator force of the actuator area is adjusted via the adjusting device so that the present spring force can be suppressed at the respective time.
  • the switching valve is designed as an electromagnetic valve, wherein the actuator region a in
  • the actuation portion is thereby advantageous from a Neten electromagnets, that is, via the coil, driven, which is supplied with ent ⁇ speaking voltage and thus can also be easily controlled via the control device.
  • the armature for transmitting the actuator force is connected to the closing element for moving the closing element into the Aktuatorkraftwirkcardi or has at least contact.
  • a pin for connecting or contacting the armature and closing element is provided. If the closing element is formed, for example, as a plate-shaped element, this plate-shaped element is then held by the preferred pin, which in turn is secured to the anchor.
  • a high-pressure fuel pump for a fuel injection system of an internal combustion engine has a pressure chamber and a switching valve described above.
  • the switching valve comprises a closing element cooperating with a valve seat and a spring biasing the closing element in a spring force acting direction.
  • the switching valve is designed in particular as an inlet valve for admitting a fuel in the pressure chamber.
  • the spring is designed to hold the closing element open against a counterforce acting on the closing element from the pressure chamber, in particular a hydraulic force.
  • a high-pressure fuel pump as described above, having a pressure chamber and a switching valve as an inlet valve for introducing fuel into the pressure chamber, wherein the switching valve, a closing element and a spring with a spring force for biasing the
  • a rotational speed of a pump drive of the high-pressure fuel pump is detected and from this rotational speed the opposing force is calculated, in particular with the aid of a conversion factor, which converts the rotational speed into a corresponding pressure value.
  • a map is advantageously stored, which brings the determined speed with a pressure value or the opposing force in connection.
  • the spring force is adjusted so that the spring force is reversibly adjusted. That means the
  • Spring force can be increased or decreased again after setting.
  • the spring force is adjusted such that a spring length of the spring is changed, for example by upsetting and relieving the spring.
  • a compression device can be driven with a corresponding drive unit.
  • an actuator force of an actuator region which actuates the switching valve to the determined counterforce, in such a way that the Aktuatorkraft, when exercised, at any time greater than the spring force.
  • Fig. 1 is a schematic sectional view of a sectionbe ⁇ riches a fuel injection system with a high-pressure fuel pump, as the inlet valve
  • Switching valve comprising a spring
  • Fig. 2 is a diagram illustrating a spring characteristic of a compression spring.
  • Fig. 1 shows a schematic representation of a portion of a fuel injection system 10, which provides a Brennkraftma ⁇ machine with highly pressurized fuel is available, namely the portion of the fuel injection system 10 in which a high-pressure fuel pump 12 is located.
  • the high-pressure fuel pump 12 has a pressure chamber 14, in which the fuel is subjected to a high pressure during operation, and a switching valve 16, which is formed in the present embodiment as an inlet valve 18 to fuel from a low pressure region 20 of the fuel ⁇ injection system 10 in the Pressure chamber 14 of the high fuel ⁇ pressure pump 12 engage.
  • the switching valve 16 has in a valve region 21 a closing element 22, which as
  • platelet-shaped element is formed and cooperates with a valve seat 24 formed by a valve seat 26 to hold the switching valve 16 in a closed position.
  • Closing element 22 is arranged on the side of the valve plate 24 which faces the pressure chamber 14.
  • a spring 28 which is in particular formed as a compression spring, and, indirectly, the closing member 22 holds on its spring force F F in an open position
  • the switching valve 16 In Fig. 1, only one particular embodiment of the switching valve 16 is shown, in which the spring 28 is arranged so that it holds the closing element 22 in the open position about its spring force F F , but it is also possible to provide a switching valve 16 which is held by the spring 28 in the closed position, for example by a tension spring is provided instead of a compression spring. In the present case, however, the closing element 22 along a Federkraftwirkachse 30 of the spring 28 in a Federkraftwirk ⁇ direction 32, shown by the arrow, biased in the open position.
  • a piston 34 moves up and down in the pressure chamber 14 and compresses an existing in the pressure chamber 14 medium, such as the
  • an actuator region 36 is provided which engages with an actuator force F A acting opposite to the spring force F F
  • Actuator force acting direction 37 the spring force F F can overpressure, and thus allows the closure member 22 can move to the closed position.
  • the switching valve 16 is formed in the present embodiment as an electromagnetic valve 38, and has a movable armature 40, a fixed pole piece 42 and a coil 44.
  • the coil 44 When the coil 44 is energized, the armature 40 moves in the direction of the pole piece 42. Since the armature 40 is in contact with the closing element 22 via a pin 46, tightening the armature 40 allows closing of the closing element 22.
  • the armature 40 that is, with respect to the pole piece 42 on the side facing the valve plate 24 is directed towards, or is arranged away from the switching valve 16 is normally closed or de-energized opened valve formed because the armature 40 in the one position the closing element 22 during its movement
  • the coil 44 is driven from outside the fuel high ⁇ pressure pump 12 via a voltage contact 48, the controlled by a control device 50 applies a predetermined voltage to the coil 44 so as to move the armature 40 in the desired manner.
  • the voltage is variable and dependent on the force from the armature 40 on the
  • Closing element 22 is to be exercised.
  • the switching valve 16 further comprises an adjusting device 54, with which the spring force F F of the spring 28 can be adjusted.
  • This adjusting device 54 comprises a compression device 56, in the present embodiment, for example, as
  • Upset piston 58 is formed, which is movable along the spring force axis 30, and on which the spring 28 is supported with a first spring end 60.
  • the spring 28 is in the present
  • Embodiment arranged in corresponding recesses in the pole piece 42 and the armature 40 and is supported by a second spring end 61 on an anchor surface 52 from.
  • the spring can be changed in their extending along the spring force acting axis 30 spring length L F 28, for example compressed or relaxed.
  • FIG. 2 shows a diagram illustrating the spring force F F of a spring 28 as a function of a spring travel S for different spring lengths L F.
  • This known as a spring characteristic diagram is particularly applicable to linear compression springs, but also applies to progressive or degressive springs.
  • a compression spring in the untensioned state has an initial length L0. If the spring force F F Installed on an installation length L F i, it receives a force Fi at L F i via its spring rate. If the spring 28 is further compressed on the spring length L F 2, it has been ascended force F 2 at this length L f 2. If the working range is shifted in the direction of LO, that is, in the direction L F i * , the spring force F F is reduced further and, as a result, also the required actuator force F A to overpress the spring force F F and the switching valve 16 to move. On this basis, the upset piston 58 is adjusted so that the spring force F F of the spring 28 is just sufficient, the
  • the adjusting device 54 has, in addition to the compression device 56, a drive unit 62 with which the compression device 56 can be actively driven.
  • the drive unit 62 can be realized by various systems and is shown here only schematically, it may be an elekt ⁇ romagnetician actuator, an electromechanical
  • the spring force F F of the spring 28 is ideally biased so as to be greater in each specific load case than the associated hydraulic force F H , that is, the opposing force F G.
  • the drive unit 62 is thereby, also controlled by the control ⁇ device 50 targeted.
  • To control the correlation between a speed of a pump drive, not shown, of the high-pressure fuel pump 12, which drives the piston 34, and the associated flow is used to form the basis for the load-specific hydraulic force F H , that is, the counterforce F G in the return ⁇ promote from the pressure chamber 14 in the low pressure region 20 to determine.
  • This counterforce F G engages the closing element 22 of the switching valve 16 and wants to press the closing element 22 in the closed position.
  • the force-determining device 64 In order to determine the reaction force F G acting from the pressure chamber 14 forth on the closure member 22, has the verse section ⁇ means 54 to a force detecting means 64th
  • the force-determining device 64 in turn comprises a detection device 66, which detects a rotational speed of the mentioned pump drive of the high-pressure fuel pump 12.
  • the force-determining device 64 comprises a calculation device 68, by means of which, based on the determined rotational speed, the counterforce F G can be calculated.
  • a map may be stored in the control device 50, which brings the determined speed directly in connection with the counterforce F G , but it is also possible to detour over a
  • Conversion device to go which first converts the determined speed into a general pressure value.
  • the spring length L F of the spring 28 and thus its spring force F F are then changed via the drive unit 62 or the upsetting device 56.
  • the switching valve 16 is adapted load-specific, on the one hand with respect to the spring force F F of the spring 28 and on the other hand with respect to the Aktuatorkraft F A , which is determined by the energization of the coil 44.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne une vanne de commande (16) pour un système d'injection de carburant (10), laquelle possède un élément de fermeture (22) précontraint par un ressort (28). La force de ressort (FF) du ressort (28) peut être modifiée de manière réversible par le biais d'un dispositif de réglage (54). L'invention concerne en outre une pompe à haute pression de carburant (12) qui est équipée d'une telle vanne de commande (16), ainsi qu'un procédé de commande avec lequel cette vanne de commande (16) peut être commandée.
PCT/EP2016/081682 2016-01-05 2016-12-19 Vanne de commande pour un système d'injection de carburant, pompe à haute pression de carburant pour un système d'injection de carburant ainsi que procédé de commande pour commander une vanne de commande dans une pompe à haute pression de carburant Ceased WO2017118562A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016200016.0A DE102016200016B4 (de) 2016-01-05 2016-01-05 Schaltventil für ein Kraftstoffeinspritzsystem, Kraftstoffhochdruckpumpe für ein Kraftstoffeinspritzsystem sowie Ansteuerverfahren zum Ansteuern eines Schaltventils in einer Kraftstoffhochdruckpumpe
DE102016200016.0 2016-01-05

Publications (1)

Publication Number Publication Date
WO2017118562A1 true WO2017118562A1 (fr) 2017-07-13

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Application Number Title Priority Date Filing Date
PCT/EP2016/081682 Ceased WO2017118562A1 (fr) 2016-01-05 2016-12-19 Vanne de commande pour un système d'injection de carburant, pompe à haute pression de carburant pour un système d'injection de carburant ainsi que procédé de commande pour commander une vanne de commande dans une pompe à haute pression de carburant

Country Status (2)

Country Link
DE (1) DE102016200016B4 (fr)
WO (1) WO2017118562A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000009883A1 (fr) * 1998-08-13 2000-02-24 Diesel Technology Company Vanne de commande
DE19963926A1 (de) * 1999-12-31 2001-07-12 Bosch Gmbh Robert Steuerventil für eine Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen mit verstellbarem Hubanschlag
DE102012205346A1 (de) * 2012-04-02 2013-10-02 Robert Bosch Gmbh Hochdruckpumpe
WO2016015912A1 (fr) * 2014-07-29 2016-02-04 Robert Bosch Gmbh Pompe à haute pression

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3711744A1 (de) * 1987-04-07 1988-10-27 Bosch Gmbh Robert Verfahren und vorrichtung zur steuerung der kraftstoffeinspritzmenge

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000009883A1 (fr) * 1998-08-13 2000-02-24 Diesel Technology Company Vanne de commande
DE19963926A1 (de) * 1999-12-31 2001-07-12 Bosch Gmbh Robert Steuerventil für eine Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen mit verstellbarem Hubanschlag
DE102012205346A1 (de) * 2012-04-02 2013-10-02 Robert Bosch Gmbh Hochdruckpumpe
WO2016015912A1 (fr) * 2014-07-29 2016-02-04 Robert Bosch Gmbh Pompe à haute pression

Also Published As

Publication number Publication date
DE102016200016B4 (de) 2017-12-21
DE102016200016A1 (de) 2017-07-06

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