EP1509694A1 - Accumulateur haute pression pour systemes d'injection de carburant avec soupape de regulation de pression integree - Google Patents

Accumulateur haute pression pour systemes d'injection de carburant avec soupape de regulation de pression integree

Info

Publication number
EP1509694A1
EP1509694A1 EP03709622A EP03709622A EP1509694A1 EP 1509694 A1 EP1509694 A1 EP 1509694A1 EP 03709622 A EP03709622 A EP 03709622A EP 03709622 A EP03709622 A EP 03709622A EP 1509694 A1 EP1509694 A1 EP 1509694A1
Authority
EP
European Patent Office
Prior art keywords
pressure
control valve
fuel injection
injection system
storage space
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
EP03709622A
Other languages
German (de)
English (en)
Other versions
EP1509694B1 (fr
Inventor
Kurt Frank
Werner Wagner
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 EP1509694A1 publication Critical patent/EP1509694A1/fr
Application granted granted Critical
Publication of EP1509694B1 publication Critical patent/EP1509694B1/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
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/023—Means for varying pressure in common rails
    • F02M63/0235—Means for varying pressure in common rails by bleeding fuel pressure
    • F02M63/025—Means for varying pressure in common rails by bleeding fuel pressure from the common rail
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
    • F02M55/025—Common rails
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/005—Pressure relief valves
    • F02M63/0052—Pressure relief valves with means for adjusting the opening pressure, e.g. electrically controlled
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • accumulator injection systems are used to inject the fuel.
  • These storage injection systems comprise a high-pressure storage space, which is supplied with fuel under high pressure via a high-pressure pump.
  • the high-pressure pump represents the interface between the high-pressure part and the low-pressure part of the injection system.
  • the high-pressure pump can be assigned a pressure control valve which, on the one hand, serves to open the pressure in the high-pressure storage space when the pressure is too high, so that fuel flows from the latter back to the fuel tank via a manifold and on the other hand to seal the high-pressure side against the low-pressure side if the pressure in the high-pressure storage space is too low.
  • the pressure control valve is used on a high pressure pump, see page 267, Figure 7 of the same publication.
  • the pressure regulating valve comprises a ball valve which contains a spherical closing body.
  • An armature is accommodated within the pressure control valve, which is acted upon on the one hand by a compression spring and on the other hand an electromagnet is arranged opposite. The armature of the pressure control valve is flushed for the lubrication and cooling of fuel.
  • the pressure control valve If the pressure control valve is not activated, the high pressure storage space or the high pressure at the outlet of the high pressure pump is applied to the pressure control valve via the high pressure inlet. Since the electroless electromagnet does not exert any force, it predominates High-pressure force versus the force of the compression spring, so that the pressure control valve is opened and this remains more or less open depending on the amount of fuel delivered.
  • the pressure control valve is activated, i.e. If the electromagnet is energized, the pressure in the high pressure circuit is increased. For this purpose, a magnetic force is generated in addition to the force exerted by the compression spring.
  • the pressure control valve is closed until there is an equilibrium of forces between the high-pressure force on the one hand and the spring force and the magnetic force on the other.
  • the magnetic force of the electromagnet is proportional to the drive current I of the solenoid coils within the pressure control valve.
  • the control current I can be clocked by pulse width modulation.
  • the pressure control valve is flange-mounted on the side of the high-pressure pump, for example.
  • both the high-pressure storage space (common rail) and the pressure control valve are each designed as separate components.
  • these separately designed components of the accumulator injection system have high manufacturing costs due to the precise manufacturing processing of their high-pressure sealing points.
  • sealing elements are to be provided at the sealing points on the high-pressure side, which are able to withstand the mechanical stresses occurring on sealing-pressure sockets on the high pressure side. Due to the pressure level prevailing on the high-pressure side, leaks occur inevitably at the sealing points designed on the high-pressure side during the operation of the accumulator injection system.
  • installation space problems can arise from the fact that lines between the high-pressure storage space and the pressure control valve require lines between them due to the size and orientation of these components of the storage injection system in the installation space. If separate components are joined, their assembly within the engine compartment in the cylinder head area of a self-igniting internal combustion engine is difficult and time-consuming in terms of assembly.
  • temperature problems with regard to the control seat can occur in the components of the high-pressure storage chamber and the pressure control valve which are sealed off from one another on the high pressure side.
  • the regulating seat represents the point at which a closing element, for example in the form of a spherical closing body, is pressed into a seat by an anchor part of the pressure regulating valve.
  • This seat determines the air gap between the armature plate and an end face of the magnetic core which is established in a pressure control valve which is controlled via a solenoid valve.
  • the sealing point between the high-pressure-carrying components of a storage injection system namely the high-pressure storage space and the pressure control valve, can be relocated from the seal-critical high-pressure side to the less critical low-pressure side.
  • the installation of the pressure control valve in the high-pressure storage chamber with a seal on the low-pressure side makes a seal on the high-pressure side, which is exposed to high mechanical loads and which results in leaks, unnecessary.
  • the seat for the closing element for example in the form of a valve ball on the pressure control valve, can be moved into an end face of the high-pressure storage space. This allows good heat dissipation, since the seat is solid, allowing good heat transfer in the material of the high-pressure storage space. Since a homogeneous temperature distribution on the high-pressure storage space can be achieved with the solution according to the invention, there is no decrease in the hardness of the material due to excessive heating, which considerably increases the strength of the high-pressure storage space configured according to the invention.
  • Another advantage is that seat rinsing can be avoided.
  • a seat flush was used to cool the seat area within the low-pressure circuit in order to prevent its inadmissible heating.
  • this made additional connections within the low-pressure circuit necessary, which can now be dispensed with with the solution according to the invention.
  • the seat for the closing element to be controlled via the pressure regulating valve can be incorporated into the end face of the high-pressure storage space.
  • one at the to create a low pressure space between the high pressure storage space and the pressure control valve Front side of the high-pressure storage space can be made in a blind hole that is easy to manufacture.
  • the circumferential surface of the blind hole is advantageously in contact with an end face on the pressure control valve, so that a further material connection is created which forms a possibility of heat dissipation.
  • Another embodiment variant is to design the seat for the closing element of the pressure control valve in an insert part if the cavity of the high-pressure storage space is to be of a uniform design.
  • the insert part containing the valve seat can be pressed into the cavity of the high-pressure storage space or welded into it.
  • a low-pressure chamber is formed in the front side of the insert part opposite the front side of the pressure control valve, in which the low-pressure side seal can be formed.
  • Both the insert part with the valve seat and the end face of the high-pressure storage space in the first-mentioned embodiment variant can comprise a through-hole containing a throttle point, which is closed by the closing element acted upon by the pressure regulating valve.
  • FIG. 1 shows the components of a storage injection system with a high-pressure storage space
  • FIG. 2 shows the high-pressure storage space in a longitudinal section
  • Figure 3 shows an electrically controlled pressure control valve sealed at the high-pressure side of the high-pressure storage space and Figure 4 is a pressure control valve which is sealed on the low pressure side of the high pressure storage space.
  • FIG. 1 shows the components of a fuel injection system with a high-pressure storage space.
  • the fuel injection system 1 shown in FIG. 1 comprises a fuel tank 2 in which there is fuel corresponding to a fuel level 3.
  • a pre-filter 4 is arranged below the fuel level 3 within the fuel tank 2 and is connected upstream of a pre-delivery unit 5.
  • the pre-conveyor unit 5 conveys the fuel drawn in via the pre-filter 4 from the fuel tank 2 via a fuel filter 6 into a low-pressure line section 7, which opens into a high-pressure delivery unit 8.
  • the high-pressure delivery unit 8, which can be a high-pressure pump, for example, is controlled via a control line 9 by a central control unit 14, which is only shown schematically here.
  • the high-pressure delivery unit 8 includes, in addition to the connection of the low-pressure line connection 7, a pressure control valve 12 flanged to it with an electrical connection 14, which is also controlled via a control 13 via the central control unit 14.
  • a high-pressure inlet branches off from the high-pressure delivery unit 8, via which a high-pressure storage space 15 (common rail) configured to be tubular is acted upon by fuel under high pressure.
  • a fuel return line 11 branches off from the high-pressure delivery unit 8, which leads into a return line 17, which in turn leads excess, outflowing fuel back into the fuel tank 2.
  • the fuel which is conveyed via the high-pressure inlet 10 by the high-pressure delivery unit 8 and is under very high pressure, enters the high-pressure storage space 15 (common rail), on the outer circumference of which a pressure sensor 16 can be accommodated.
  • the pressure sensor 16 is in turn connected via a pressure signal line 25 to a central signal line 24, which in turn extends from the control unit 14.
  • High-pressure lines 18 branch off from the high-pressure storage space 15, which can be configured, for example, as a tubularly configured component, in a number corresponding to the number of fuel injectors 19.
  • the high-pressure feed lines 18 open at the respective inlet connection 20 of the injector bodies of the fuel injectors 19.
  • the fuel injectors 19 in turn comprise actuators which can be designed, for example, as piezo actuators, mechanical-hydraulic translators or also as solenoid valves and which initiate the injection processes in an appropriate sequence.
  • the actuators of the individual fuel injectors 19 are also connected via actuator control lines 22 to the central signal line 24, which emanates from the schematically represented central control unit 14.
  • the individual fuel injectors 19 have return lines 21, which likewise open into the return 17 to the fuel tank 1 already mentioned, so that, for example, control volumes to be discharged can flow into the fuel tank 2.
  • control line 26 In addition to the control line 13 already mentioned for controlling an electromagnet contained in the pressure control valve 12 and a control line 9 for the high-pressure delivery unit 8 and a pressure sensor line 25 for the pressure sensor 16 of the high-pressure storage space 15, a control line 26 also branches off from the control unit 14, with which the pressure in the fuel tank 2 housed feed unit 5 can be controlled.
  • the central control unit 14 of the Kraftstoffeinspritzsy ste it receives about 'addition, signals from a crankshaft sensor 27, which serves to detect the rotational position of the internal combustion engine, and also signals from a camshaft position sensor 28, the Verbrennungsl ⁇ aftmaschine ge determinable is over the the corresponding Phasenla- as well as input signals of an accelerator pedal sensor 29th
  • the central control unit 14 also receives, via the central signal line 24, signals characterizing the boost pressure 30 via a corresponding sensor housed in the intake tract of the internal combustion engine.
  • the engine temperature 31 for example recorded on the walls of the combustion chambers of the internal combustion engine and the temperature 32 of the cooling fluid of the internal combustion engine, is transmitted via the central signal line 24 to the central control unit 14 shown in FIG.
  • FIG. 2 shows the high-pressure storage space of the fuel injection system in longitudinal section.
  • the high-pressure storage space 15 essentially encloses a cavity 33.
  • the high-pressure storage space 15 shown in FIG. 2 is designed as a separate component and comprises on its first end face 37 an insert element 39 designed as a closure, to which the return line 17 shown in FIG. 1 to the fuel tank can be connected ,
  • the high-pressure storage space 15 comprises, as shown in FIG. 2, a high-pressure connection 40 to which the high-pressure inlet 10 shown in FIG. 1 can be connected.
  • the pressure sensor 16 shown in FIG. 1 is accommodated on its outer circumferential surface and is connected to the control unit 14 via the pressure sensor line 25 shown in FIG. 1 (see illustration according to FIG. 1).
  • connecting pieces 34 are formed on the circumferential surface of the high-pressure storage space 15, to which the high-pressure feed lines 18 to the fuel injectors 19 can be connected (see illustration according to FIG. 1).
  • the connecting pieces 34 each enclose transverse bores 35, which are connected to the cavity 33 of the high-pressure storage space 15 and via which the fuel under high pressure from the high-pressure storage space 15 is fed to the individual fuel injectors 19.
  • fastening tabs 36 are also welded or welded, via which the high-pressure storage space 15 in the cylinder head area of a self-igniting internal combustion engine can be connected to it.
  • the high-pressure storage space 15 shown in FIG. 2 comprises five connecting pieces 34, so that five high-pressure feed lines 18 to the fuel injectors 19 of a self-igniting internal combustion engine can be supplied with fuel under high pressure.
  • the high-pressure storage space 15 shown as a separate component in FIG. 2 can of course be designed both to supply a four-cylinder self-igniting internal combustion engine and to supply a six- or eight-cylinder internal combustion engine with fuel.
  • FIG. 3 shows an electrically controlled pressure control valve sealed on the high pressure side in the high pressure storage space.
  • the pressure control valve shown in section in FIG. 3 contains an electrical connection 41, which can be clipped onto ring grooves of a housing body or is molded onto it.
  • An electromagnet 46 is arranged within the housing body.
  • An armature plate 42 which is acted upon by a compression spring 44, is arranged opposite the electromagnet 46.
  • the anchor plate 42 and the compression spring 44 are enclosed by an approximately 43-shaped insert 43.
  • the anchor plate 42 is connected to an anchor part 45, which has a taper in the form of a truncated cone at the end opposite the anchor plate 42.
  • the tapered end of the armature part 45 acts on a closing element 47 designed here as a valve ball, which is received in a valve seat 49.
  • a high-pressure-side seal 48 designated by reference numeral 48, is formed, with which the pressure control valve shown in section according to FIG. 3 can be arranged both on a high-pressure supply unit for a high-pressure pump or on a high-pressure storage space.
  • the seal on the high-pressure side identified by reference numeral 48, requires high machining quality, the smallest tolerances and is exposed to extremely high mechanical stresses during operation and therefore represents a weak point of a fuel injection system for self-igniting internal combustion engines with increasing service life.
  • Figure 4 shows a pressure control valve which can be sealed on the low-pressure side of a high-pressure storage space.
  • Both the high-pressure storage chamber 15 and the pressure control valve 57 are shown in longitudinal section from the illustration in FIG. 4.
  • the high-pressure storage space 15 is designed with a wall thickness that is adapted to the prevailing pressure level.
  • 15 connecting pieces 34 are formed on the outer circumferential surface of the high-pressure storage space, each of which is penetrated by a transverse bore 35. The fuel under high pressure flows from the cavity 33 of the high-pressure storage space 15 via the cross bores 35 via the connecting pieces 34 into the respective high-pressure feed lines 18 to the injectors 19, which inject the fuel into the combustion chambers of the internal combustion engine to be supplied.
  • a bore 52 for example a blind hole, is formed at one end of the high-pressure storage space 15.
  • the blind hole 52 at one end of the high-pressure storage space 15 forms a low-pressure region when the pressure control valve 57 is mounted in it.
  • a low-pressure area 51 is assigned to the low-pressure area, via which fuel entering the low-pressure area 52, 51 and exiting from the cavity 33 of the high-pressure storage area 15 flows back in the low-pressure area of the fuel injection system, for example into a return 17 to the fuel tank (see illustration in FIG. 1) can.
  • the pressure regulating valve 57 shown in FIG. 4 is seatless and comprises an end face 53 which is embodied in a smaller diameter than the outside diameter of the pressure regulating valve 57.
  • An annular groove 55 can run within the area of the pressure control valve 57, which is of smaller diameter, in which a Sealing element 56 can be embedded.
  • the sealing element 56 embedded in the annular groove 55 forms a low-pressure side seal 54 within the low-pressure region 51, 52, which is exposed to significantly lower pressure loads than a high-pressure side seal (see illustration according to FIG. 3, position 48).
  • a recess could also be arranged in the region of the front-side contact surface of the pressure regulating valve body with the annular surface closing the blind hole 52 on the high-pressure storage space 15.
  • Both of the low-pressure side seals 54 shown by way of example have in common that they are designed for lower mechanical stresses compared to a high-pressure side sealing point 48 between the pressure control valve 57 and the high-pressure storage space 15. Furthermore, the arrangement of a pressure control valve 57 shown in FIG. 4 directly to a high-pressure storage space 15 on a first end face 37 and also on a second end face 38 makes it possible to dispense with a line connection between the high-pressure storage space and the pressure control valve.
  • the pressure control valve 57 comprises an armature part 45 which, with its end facing away from the pressure spring 44, acts on the closing element 47 configured here in a spherical shape.
  • the closing element 47 which is spherical in FIG. 4, works together with a valve seat 59 or 61.
  • the seat 59 can be incorporated directly into an end wall 58 of the high-pressure storage space 15.
  • the cavity 33 of the high-pressure storage space 15 is delimited by the end face 58, which is penetrated by a bore containing a throttle point immediately before the closing element 47.
  • a pressure relief of the cavity 33 of the high-pressure storage space 15 can take place via the closing body 47 pressed into the valve seat 59 by means of the armature part 45 of the pressure control valve 57.
  • the opening or opening of the cavity 33 which can be released or closed by the spherical closing element 47, is at a distance 62 with respect to its end face facing the cavity 33 with respect to the line of symmetry of the transverse bore 35 of a first high-pressure connection 34.
  • the distance 62 between the transverse bore 35 of the first High-pressure connection 34 and the end face of the high-pressure storage space 15 is dimensioned such that Relieve mechanical stresses within the high-pressure storage space 15 between the transverse bore 35 and the end face of the high-pressure storage space 15.
  • the valve seat 59 for the closing element 47 which is formed in the end face 58 of the high-pressure storage space 15, has the particular advantage that the valve seat 59 is formed in a solidly designed area.
  • an insert part 60 in the case of high-pressure storage spaces 15 formed in two or more parts, an insert part 60 can be pressed or welded into the space 33 to limit the cavity 33.
  • a valve seat 61 can be incorporated into the insert part 60.
  • the end face of the insert part 60 facing the high-pressure storage space 33 is preferably also arranged at a distance 62 with respect to the line of symmetry of the transverse bore 35 of the first high-pressure connection 34
  • a thermal bridge such that the material of the high-pressure storage space 15 surrounding the blind bore 52 rests and rests on the body of the pressure control valve 57 with one end face this way can serve as a pressure control valve 57 or its outer peripheral surface for heat dissipation.
  • the body of the pressure regulator Valves 57 on the end of which opposite the end face 53 electrical connections 63 and 41 can be formed, preferably has in the area of the end face 53 an area with a tapered diameter in which an annular groove 55, which receives the sealing element 56 of the low-pressure side seal 54, is introduced can be.
  • the low-pressure area 52, 51, in which the seal 54 is located is essentially delimited by the blind hole 52 on one of the end faces of the high-pressure storage space 15 and the bottom of the blind hole 52, in which the valve seat 59 for the closing element 47 in one-piece high-pressure storage spaces 15 and the valve seat 61 lies in multi-part high-pressure storage spaces 15 with a pressed-in or welded-in insert part 60.
  • a seal on the high-pressure side can be dispensed with, as a result of which an easily achievable seal between the high-pressure storage space 15 and the pressure control valve 57 can be achieved.
  • Good seat cooling can also be achieved by the arrangement of the seat 59 or 61 for the spherical closure element 47 given in both design variants, since heat can be dissipated via the solid material surrounding the seat 59 or 61. Furthermore, in the solution proposed according to the invention, seat flushing can be dispensed with in both design variants.
  • the seal 54 on the low-pressure side proposed according to the invention can be used with a seatless pressure control valve integrated on the front side 37 or 38 of the high-pressure storage chamber 15 Produce 57 much cheaper, since a much lower pressure level has to be sealed.
  • Fuel injection system Fuel tank Fuel level Pre-feeder Pre-delivery unit Fuel filter Low pressure line section High-pressure delivery unit Control line High-pressure inlet Fuel return Pressure control valve Control chamber Electromagnet Control unit High-pressure storage chamber Pressure sensor Return to fuel tank High-pressure supply line to injector Fuel injector Intake side sensor Sensor sensor supply line Pressure sensor supply line Nine sensor control line Fuel pressure sensor First front side of high-pressure storage chamber Second front side of high-pressure storage chamber Closure connecting piece High-pressure connection Electrical connection Anchor plate Bell-shaped insert Discharge spring Anchor part Electromagnet Closing element High-pressure sealing valve seat Low-pressure chamber low-pressure connection Blind hole Front side Pressure control valve Low-pressure seal Ring groove sealing element Pressure control valve (seatless) Pressure control valve connections

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

Abstract

L'invention concerne un système d'injection de carburant pour moteurs à combustion interne qui comprend une chambre d'accumulateur haute pression (15). Cette chambre d'accumulateur haute pression (15) reçoit du carburant sous haute pression par l'intermédiaire d'un groupe d'alimentation haute pression (8) et alimente à son tour des injecteurs de carburant (19, 23) en carburant. Le système d'injection de carburant comprend une soupape de régulation de pression (57) qui est disposée entre un côté haute pression (33) et un côté basse pression (50, 51, 52) et par l'intermédiaire de laquelle peut être actionné un obturateur (47). La soupape de régulation de pression (57) est actionnée par l'intermédiaire d'un actionneur électrique (46). La soupape de régulation de pression (57) délimite, avec une face (53), la zone basse pression (50, 51, 52), au niveau de la chambre d'accumulateur haute pression (15) et elle est fermée de façon étanche par un joint d'étanchéité (54) placé côté basse pression.
EP03709622A 2002-05-23 2003-02-18 Accumulateur haute pression pour systemes d'injection de carburant avec soupape de regulation de pression integree Expired - Lifetime EP1509694B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10222895A DE10222895A1 (de) 2002-05-23 2002-05-23 Hochdruckspeicher für Kraftstoffeinspritzsysteme mit integriertem Druckregelventil
DE10222895 2002-05-23
PCT/DE2003/000486 WO2003100247A1 (fr) 2002-05-23 2003-02-18 Accumulateur haute pression pour systemes d'injection de carburant avec soupape de regulation de pression integree

Publications (2)

Publication Number Publication Date
EP1509694A1 true EP1509694A1 (fr) 2005-03-02
EP1509694B1 EP1509694B1 (fr) 2006-08-23

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP03709622A Expired - Lifetime EP1509694B1 (fr) 2002-05-23 2003-02-18 Accumulateur haute pression pour systemes d'injection de carburant avec soupape de regulation de pression integree

Country Status (5)

Country Link
US (1) US7185635B2 (fr)
EP (1) EP1509694B1 (fr)
JP (1) JP2005526930A (fr)
DE (2) DE10222895A1 (fr)
WO (1) WO2003100247A1 (fr)

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DE10342484A1 (de) * 2003-09-15 2005-04-07 Robert Bosch Gmbh Druckregelventil für Speicherkraftstoffeinspritzsystem
DE102004037538A1 (de) * 2004-08-03 2006-02-23 Robert Bosch Gmbh Verfahren und Vorrichtung für den Raildruckabbau bei einem Common Rail Einspritzsystem
EP1741923B1 (fr) * 2005-07-08 2009-09-02 C.R.F. Societa Consortile per Azioni Système de connexion d'une rampe tubulaire pour carburant à haute pression
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US20060102150A1 (en) 2006-05-18
DE50304760D1 (de) 2006-10-05
US7185635B2 (en) 2007-03-06
JP2005526930A (ja) 2005-09-08
DE10222895A1 (de) 2003-12-11
EP1509694B1 (fr) 2006-08-23

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