EP1343965A1 - Systeme d'injection haute pression con u sous la forme d'un papillon de commande sous forme de papillon en cascade - Google Patents

Systeme d'injection haute pression con u sous la forme d'un papillon de commande sous forme de papillon en cascade

Info

Publication number
EP1343965A1
EP1343965A1 EP01989404A EP01989404A EP1343965A1 EP 1343965 A1 EP1343965 A1 EP 1343965A1 EP 01989404 A EP01989404 A EP 01989404A EP 01989404 A EP01989404 A EP 01989404A EP 1343965 A1 EP1343965 A1 EP 1343965A1
Authority
EP
European Patent Office
Prior art keywords
throttle
valve
control chamber
inlet
injection
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
EP01989404A
Other languages
German (de)
English (en)
Other versions
EP1343965B1 (fr
Inventor
Michael Von Dirke
Wendelin KLÜGL
Dirk Baranowski
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.)
Siemens AG
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Publication of EP1343965A1 publication Critical patent/EP1343965A1/fr
Application granted granted Critical
Publication of EP1343965B1 publication Critical patent/EP1343965B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0043—Two-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B2013/008—Throttling member profiles

Definitions

  • the present invention relates to a high-pressure injection system with a control throttle as a cascade throttle, and in particular to a high-pressure injection system in the manner of a common rail injection system of a direct-injection diesel engine.
  • High-pressure accumulator injection systems also known as so-called common rail injection systems, are distinguished from conventional injection systems in that the injection pressure can be generated independently of the engine speed.
  • the decoupling of pressure generation and injection is implemented with the aid of a storage volume in which fuel is made available under high pressure.
  • the high pressure in the storage volume is generated by a high pressure pump.
  • Both the injection nozzle and a control chamber are fed with the fuel from the storage volume, via which a nozzle needle of the injection nozzle is controlled.
  • a control piston is slidably mounted in the control chamber, one end of which is connected to the nozzle needle and the other end of which is pressurized in the control chamber.
  • the pressure in the control chamber is generated via a connecting line by the pressure in the storage volume.
  • the control chamber is connected to a valve to relieve pressure. Furthermore, an inlet throttle is provided between the storage volume and the control chamber, and an outlet throttle is provided between the control chamber and the valve in order to ensure a predetermined pressure build-up or decrease in the control chamber after the valve has been closed or opened.
  • the discharge throttle is designed in such a way that the cavitation transition point, i.e. the back pressure, does not fall below the flow through the throttle due to cavitation can be further increased and is therefore as high as possible regardless of the back pressure prevailing behind the throttle in the flow direction.
  • the outlet throttle cavitates when the valve is open (low back pressure) and the flow through the throttle and thus the movement of the control piston becomes independent of the valve flow cross-section.
  • the predetermined pressure build-up / reduction in the control chamber creates a controlled movement of the control piston and the associated nozzle needle.
  • Controlled is understood to mean that the time of the start of movement when opening and closing as well as the speed of the movement itself are determined by the size of the pressurized cross-sectional areas of the control piston and nozzle needle as well as by the fuel pressure in the storage volume and the flow properties of the throttles, in particular flow resistance and Cavitation point, can be specified.
  • the reproducible injection of defined amounts of fuel with high precision therefore requires high manufacturing accuracy of control pistons and throttles.
  • the relatively large cross-sectional areas of the control pistons can be manufactured very precisely; the production of chokes with low manufacturing tolerance, however, requires a very high level of effort, as will be explained below.
  • the throttles used in the prior art for injection devices are implemented in the form of cylindrical cross-sectional constrictions in the flow path between the control chamber and storage volume or between the control chamber and valve.
  • Such conventional chokes typically have a length of approximately 1 mm and have a throttle passage with a diameter of typically 0.3 mm.
  • the throttle passage is produced, for example, by drilling or by electrochemical etching.
  • the throttle length itself is of secondary importance for the flow properties of the throttle.
  • the flow characteristics of the throttles are not only determined by the diameter of the throttle passage, but also by one possible taper, the shape of inlet and outlet edges and the surface condition of the throttle passage are determined.
  • the flow resistance determining the function of the throttle is set to the setpoint by hydroerosive rounding of the inlet edges of the throttle. Chokes with only small tolerances and constant quality in the flow parameters can therefore only be produced with great effort. In practice, a correspondingly high reject rate must be expected when producing throttles.
  • the invention has for its object to reduce the manufacturing outlay in the manufacture of memory injection systems, in particular with regard to the Dross.
  • the inlet throttle of a storage injection system is designed as a multi-stage throttle.
  • the design of the inlet throttle in the form of a plurality of throttle stages or of throttles connected in series permits greater manufacturing tolerances in the manufacture of the individual throttles or throttle stages without the flow properties of the inlet throttle formed in this way being impaired.
  • the requirements for the manufacturing tolerance of an individual throttle stage or throttle and thus the inlet throttle itself are considerably reduced, as a result of which a lower manufacturing outlay is achieved in the production of the storage injection device according to the invention.
  • N is the number of individual chokes.
  • the individual throttles of an N-stage inlet throttle thus have a flow cross section enlarged by a factor of VN compared to an inlet throttle designed as a single throttle.
  • the spread ⁇ Q of the flow Q is calculated for a multi-stage throttle
  • the design of the inlet throttle as a multi-stage throttle means that individual throttles with a higher flow cross-section on the one hand and a larger manufacturing tolerance on the other hand can be used.
  • a reduction in the manufacturing outlay is achieved.
  • the multi-stage design of the inlet throttle also reduces the pressure drop in an advantageous manner the individual throttle levels. With a total pressure drop ⁇ P total , the pressure drop across the first throttle stage is complete
  • the inlet throttle is designed as a separate cascade throttle.
  • a separate cascade throttle Such a configuration promotes the compact design of the accumulator injection device.
  • the design of the multi-stage choke as a separate, usable component in the form of a cascade choke also facilitates the handling or installation of the choke in the manufacturing process.
  • the multi-stage inlet throttle is constructed from a plurality of identical individual throttles or throttle elements.
  • the use of the same individual chokes or throttle elements enables production to be rationalized.
  • the flow cross section of an individual throttle or a throttle element can be selected such that different total flow cross sections of the inlet throttle are used, for example, in different types of accumulator injection devices can only be realized by varying the number of individual chokes or throttle elements.
  • Such a modular construction of the inlet throttle reduces the number of different components and achieves more variable adjustability with regard to the flow resistance.
  • the individual throttles or throttle elements are aligned with one another in such a way that their throttle bushings are offset from one another. It is thereby achieved that the throttling effect of a throttle or an individual throttle element takes place essentially unaffected by the effect of the other throttles or throttle elements.
  • the flow properties of the multi-stage throttle can thus be predetermined more precisely and undesirable or unforeseeable interactions between the throttle elements can be largely excluded.
  • Figure 1 is a schematic representation of a memory injection device according to the invention and Figure 2 shows a multi-stage inlet throttle of the memory injection device according to the invention corresponding to Figure 1 in an enlarged view.
  • FIG. 1 shows a schematically illustrated accumulator injection device 1 according to the invention, which is designed, for example, in the manner of a common rail injection system with a 2/2-way piezo valve.
  • the accumulator injection device 1 comprises a high-pressure accumulator 2a, a high-pressure line 2, an injection valve 3, and means 8 for the hydraulic control of the injection valve 3.
  • the control means 8 are a control chamber 9, which is connected to the high-pressure accumulator 2a via a high-pressure line 2, and a valve 10 also connected to the control chamber.
  • the valve 10 is actuated via a piezo actuator 11.
  • Reference numeral 12 represents a schematic illustration of the electronic control of the piezo actuator 11.
  • a control piston 14 is slidably mounted in the control chamber 9.
  • One end 15 of the control piston 14 is acted upon by the pressure of the control chamber 9 and its other end 16 acts on a nozzle needle 5 of the injection valve 3.
  • the nozzle needle 5 is movably mounted in the injection valve 3 in order to open or remove nozzle openings 6 of the injection valve 3 - check.
  • the nozzle needle 6 is biased by a spring 7 against the valve seat of the injection valve 3.
  • the injection valve 3 is fed with fuel from the high-pressure accumulator 2a via a feed line 7.
  • Throttles 19, 20 are provided between the control chamber 9 and the high-pressure accumulator 2a and the control chamber 9 and the valve 10, via which fuel from the high-pressure accumulator 2a can flow into the control chamber 9 and can flow out of the control chamber 9.
  • the throttles 19, 20 enable the setting of predetermined flow parameters of the fuel when the fuel flows in or out from the control chamber 9.
  • the inlet throttle 19 is designed according to the invention in the form of a multi-stage throttle.
  • valve 10 When the valve 10 is closed, fuel flows from the high-pressure accumulator 2a and the high-pressure line 2 via the inlet throttle 19 into the control chamber 9. As a result, a corresponding fuel pressure of the high-pressure accumulator 2a is built up in the control chamber 9, and thus the control piston 14 at its piston side end 16 with the pressure of Control chamber 9 acted upon. This causes a movement of the control piston 14 in the direction of the nozzle openings 6 of the injection valve 3, which is transferred to the nozzle needle 5 via the end 15 of the control piston 14 on the nozzle needle side. The nozzle needle 5 closes the nozzle openings 6 of the injection valve 3 against the pressure of the fuel to be injected.
  • FIG. 2 shows an enlarged illustration of the multi-stage inlet throttle 19 of the storage injection device 1 according to the invention from FIG. 1.
  • the multi-stage inlet throttle 19 is constructed from a plurality of throttle elements 22, which are arranged, for example, in a cylindrical housing 21. The two open ends of the housing 21 are the inlet or outlet opening of the throttle 19.
  • the exemplary throttle elements 21 are disk-shaped and have throttle passages 23.
  • the throttle passage 23 is designed in the form of a depression or a groove in the lateral surface of the disk-shaped throttle element 22, a defined flow cross section of the throttle element 22 being inserted in the housing by the interaction of the groove with the inner lateral surface of the cylindrical housing 21 Condition is given.
  • the bushings or passages can also be designed as through bores or other constricting constructions of the throttle elements.
  • Distance means 24 are provided between the individual throttle elements 22, which ensure a minimum distance between the throttle elements 22.
  • the spacing means 24 can be formed integrally with the throttle elements 22 or can also be provided on the housing 21.
  • the throttle elements 22 are preferably aligned in the cylindrical housing 21 such that the respective bushings 23 are offset from one another. This creates a largely independent throttle effect of a throttle element 22 compared to the other throttle elements 22.
  • the multi-stage throttle 19 shown in the exemplary embodiment is designed as a separate component and can be built into the storage injection device 1 according to the invention with little effort.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Manufacturing & Machinery (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne un système d'injection haute pression (1) comprenant au moins un accumulateur haute pression (2a) destiné au carburant, une chambre de commande (9), une soupape (10) et une soupape d'injection (3) dotée d'une aiguille d'injecteur (5) et d'un piston pilote (14). La chambre de commande (9) est reliée à l'accumulateur haute pression (2a) par un papillon d'arrivée (19) et à la soupape (10) par un papillon de sortie (20). La chambre de commande (9) permet de commander le mouvement du piston pilote (14) et l'aiguille d'injecteur (5) qui y est reliée. A cet effet, le papillon d'arrivée (19) et le papillon de sortie (20) permettent de commander les rapports d'écoulement du carburant qui entre dans et qui sort de la chambre de commande (14). Le papillon d'arrivée (19) est conçu sous forme de multi-étage.
EP01989404A 2000-12-20 2001-12-13 Systeme d'injection haute pression con u sous la forme d'un papillon de commande sous forme de papillon en cascade Expired - Lifetime EP1343965B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10063698A DE10063698A1 (de) 2000-12-20 2000-12-20 Hochdruckeinspritzsystem mit Ausführung einer Steuerdrossel als Kaskadendrossel
DE10063698 2000-12-20
PCT/DE2001/004703 WO2002050423A1 (fr) 2000-12-20 2001-12-13 Systeme d'injection haute pression conçu sous la forme d'un papillon de commande sous forme de papillon en cascade

Publications (2)

Publication Number Publication Date
EP1343965A1 true EP1343965A1 (fr) 2003-09-17
EP1343965B1 EP1343965B1 (fr) 2005-11-23

Family

ID=7668067

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01989404A Expired - Lifetime EP1343965B1 (fr) 2000-12-20 2001-12-13 Systeme d'injection haute pression con u sous la forme d'un papillon de commande sous forme de papillon en cascade

Country Status (4)

Country Link
US (1) US7216629B2 (fr)
EP (1) EP1343965B1 (fr)
DE (2) DE10063698A1 (fr)
WO (1) WO2002050423A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10063698A1 (de) 2000-12-20 2002-07-04 Siemens Ag Hochdruckeinspritzsystem mit Ausführung einer Steuerdrossel als Kaskadendrossel
DE102007042466B3 (de) * 2007-09-06 2009-04-09 Continental Automotive Gmbh Einspritzsystem mit reduzierter Schaltleckage und Verfahren zum Herstellen eines Einspritzsystems
JP2019148193A (ja) * 2018-02-26 2019-09-05 株式会社Ｓｏｋｅｎ 燃料噴射装置

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4118156A (en) * 1976-12-01 1978-10-03 Sulzer Brothers Limited Fuel injection pump having choke means in overflow line
US4526151A (en) * 1982-03-12 1985-07-02 Mitsubishi Jukogyo Kabushiki Kaisha Fuel injection device
DE29508395U1 (de) * 1995-05-19 1995-08-10 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Hydraulisches Dämpfungsventil
DE29508392U1 (de) * 1995-05-19 1995-08-10 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Elektrohydraulisches Hubmodul
DE29518547U1 (de) * 1995-11-22 1996-01-11 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Kaskadendrossel
JP3653882B2 (ja) * 1996-08-31 2005-06-02 いすゞ自動車株式会社 エンジンの燃料噴射装置
EP0976924B1 (fr) * 1998-07-31 2003-09-17 Siemens Aktiengesellschaft Injecteur avec une servovalve
JP3763698B2 (ja) * 1998-10-22 2006-04-05 株式会社日本自動車部品総合研究所 圧力脈動を緩和し得る燃料供給システムの設計方法
GB9905896D0 (en) * 1999-03-16 1999-05-05 Lucas Ind Plc Fuel injector arrangement
DE19939419A1 (de) * 1999-08-20 2001-03-01 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung
DE19939418A1 (de) * 1999-08-20 2001-03-01 Bosch Gmbh Robert Kraftstoffeinspritzsystem für eine Brennkraftmaschine
FI112527B (fi) * 1999-12-16 2003-12-15 Waertsilae Finland Oy Ruiskutusventtiilijärjestely
DE10063698A1 (de) 2000-12-20 2002-07-04 Siemens Ag Hochdruckeinspritzsystem mit Ausführung einer Steuerdrossel als Kaskadendrossel

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0250423A1 *

Also Published As

Publication number Publication date
US20040035950A1 (en) 2004-02-26
EP1343965B1 (fr) 2005-11-23
DE10063698A1 (de) 2002-07-04
US7216629B2 (en) 2007-05-15
DE50108204D1 (de) 2005-12-29
WO2002050423A1 (fr) 2002-06-27

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