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WO2008122521A1 - Soupape et système d'injection pour un moteur à combustion interne comprenant une soupape - Google Patents

Soupape et système d'injection pour un moteur à combustion interne comprenant une soupape Download PDF

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Publication number
WO2008122521A1
WO2008122521A1 PCT/EP2008/053645 EP2008053645W WO2008122521A1 WO 2008122521 A1 WO2008122521 A1 WO 2008122521A1 EP 2008053645 W EP2008053645 W EP 2008053645W WO 2008122521 A1 WO2008122521 A1 WO 2008122521A1
Authority
WO
WIPO (PCT)
Prior art keywords
fluid
fluid pressure
valve
sealing seat
pressure value
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/EP2008/053645
Other languages
German (de)
English (en)
Inventor
Fredrik Borchsenius
Anatoliy Lyubar
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 WO2008122521A1 publication Critical patent/WO2008122521A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • 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
    • 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
    • F02M63/0056—Throttling valves, e.g. having variable opening positions throttling the flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/025—Check valves with guided rigid valve members the valve being loaded by a spring
    • F16K15/026—Check valves with guided rigid valve members the valve being loaded by a spring the valve member being a movable body around which the medium flows when the valve is open
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/06—Check valves with guided rigid valve members with guided stems
    • F16K15/063—Check valves with guided rigid valve members with guided stems the valve being loaded by a spring
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D16/00—Control of fluid pressure
    • G05D16/04—Control of fluid pressure without auxiliary power
    • G05D16/10—Control of fluid pressure without auxiliary power the sensing element being a piston or plunger
    • G05D16/103—Control of fluid pressure without auxiliary power the sensing element being a piston or plunger the sensing element placed between the inlet and outlet
    • 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
    • F02M2200/60—Fuel-injection apparatus having means for facilitating the starting of engines, e.g. with valves or fuel passages for keeping residual pressure in 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
    • F02M59/20—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
    • 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
    • F02M63/0245—Means for varying pressure in common rails by bleeding fuel pressure between the high pressure pump and the common rail

Definitions

  • Valve and injection system for an internal combustion engine with valve
  • the invention relates to a valve and an injection system for an internal combustion engine with valve.
  • injection systems For injecting fuel into the combustion chambers of an internal combustion engine, in particular a diesel internal combustion engine, injection systems are used which have increasingly been designed as so-called “common rail” systems in recent years
  • the fuel to be injected is present in the fuel reservoir at a pressure of up to 2000 bar.
  • Injection systems for internal combustion engines usually have various pumps and valves, by means of which combustion chambers of the internal combustion engine fuel can be metered.
  • Such injection systems for internal combustion engines place high demands on the accuracy of the injection pressure required for injecting the fuel into the combustion chambers of the internal combustion engine.
  • soot is highly dependent on the preparation of the air / fuel mixture in the respective cylinder of the internal combustion engine.
  • the injection system can achieve a high accuracy of the injection pressure of the fuel into the combustion chamber of the internal combustion engine with suitable control and regulating units such as corresponding valves.
  • the invention has for its object to provide a valve that is simple. Furthermore, the invention has for its object to provide an injection system with a valve which allows a high accuracy of the injection pressure of the fuel in the combustion chambers of the internal combustion engine and a simple structure of the injection system.
  • the invention is characterized by a valve having a valve housing with a longitudinal axis, which has a Ventilgehauseausinstituung with a wall, a Fluideinbergso réelle and a Fluidaustrittso réelle which are arranged in the valve housing and hydraulically coupled to the Ventilgehauseausinstituung, one at the Wall of VentilgehauseausEnglishung trained sealing seat, a in the VentilgehauseausNFung between the Fluideinbergsoff- and the Fluidaustrittso réelle axially movable valve body having a seating which cooperates with the sealing seat so that in a closed position prevents fluid flow through the Fluidaustrittso réelle and otherwise the fluid flow rate the fluid outlet opening is released, and a spring element, by means of which the valve body can be acted upon with force in the direction of the fluid inlet opening, wherein the valve body and the spring element are designed and arranged in this way et are that in a first Preventing the range of fluid pressure at the Fluideinbergso réelle below
  • the valve body and the sealing seat are designed and arranged such that in a fourth region of the fluid pressure at the Fluideintrittso réelle above the first fluid pressure value and below a third fluid pressure value, a variation of FIu- id jossatzes by the Fluidaustrittso réelle between zero and the maximum second fluid flow rate is allowed, and in a fifth range of the fluid pressure at the fluid inlet above the third fluid pressure value and below the second fluid pressure value, a variation of fluid throughput through the fluid outlet between the maximum second fluid flow rate and the maximum first fluid flow rate is enabled, the fourth range the fluid pressure at the fluid inlet opening is smaller than the fifth area of the fluid pressure at the fluid inlet opening.
  • the valve has a first sealing seat formed on the wall of the VentilgehauseausEnglishung and formed on the wall of VentilgehauseausNFung second sealing seat which is axially spaced from the first sealing seat, wherein the valve body axially between the first sealing seat and the second sealing seat is arranged, and the Ventilkorper having a first seating, which cooperates with the first sealing seat so that in the first region of the fluid pressure at the Fluideintrittso réelle below the first fluid pressure value, a fluid flow rate is prevented by the Fluidaustrittso réelle, and the Ventilkorper a second seating area which cooperates with the second sealing seat so that in the second region of the fluid pressure at the fluid inlet opening above the second fluid pressure value, a fluid flow is prevented by the Fluidaustrittso réelle.
  • This has the advantage that a simple construction of the valve with two sealing seats and a valve body for realizing a fluid throughput in the middle pressure range between the first fluid pressure value and the second fluid pressure value is possible.
  • the first sealing seat is konusformig formed with a first Kegelo réelleswinkel and the second sealing seat kon nusformig formed with a second Kegelo réelleswinkel, and the first cone opening angle of the first sealing seat is greater than the second Kegelo réelleswinkel of the second sealing seat.
  • the first seat portion of the Ventilkorpers is konusformig formed with a first Kegelo réelleswinkel and the second seating area of Ventilkorpers is konusformig formed with a second Kegelo réelleswinkel, and the first Kegeloff- angle of the first seat portion is smaller than the second Kegelo réelleswinkel of the second seating area.
  • the Ventilkorper on a cylinder portion, and the wall of the VentilgehauseausEnglishung has a cylindrical portion, and the Ventilkorper is arranged in the VentilgehauseausEnglishung that between the cylinder portion of the Ventilkorpers and the cylinder portion of the wall of the Ventilgehauseausinstituung Gap is formed with a gap length, such that in the third region of the fluid pressure at the Fluideintrittso réelle above the first Fluid réelle- value and below the second fluid pressure value, the gap length in dependence on the fluid pressure at the Fluideinhoff- so réelle is variable, wherein for the first fluid pressure value a minimum gap length value and for the second fluid pressure value a maximum gap length value is assumed.
  • the invention comprises an injection system for an internal combustion engine, with at least one injector coupled to a fuel reservoir, a demand pump for requesting fuel from a fuel tank, a high-pressure pump downstream of the charge pump, for requesting the fuel into the fuel storage, a downstream of the high-pressure pump valve according to the first aspect of the invention, with which the pressure to be established in the fuel reservoir is adjustable.
  • a volume flow control valve is arranged hydraulically between the pre-demand pump and the high-pressure pump, with which the fuel flow from the pre-demand pump is adjustable in the high-pressure pump.
  • FIG. 1 shows a block diagram of an injection system for an internal combustion engine with a valve
  • FIG. 2 shows a schematic cross section through a valve in a first embodiment
  • 3a shows the course of the effective throttle area of the first embodiment of the valve in dependence on the inlet pressure
  • FIG. 3b shows the profile of the fluid flow rate of the first embodiment of the valve as a function of the inlet pressure
  • FIG. 4 shows a schematic cross section through a valve in a second embodiment
  • Figure 5a shows the course of the gap length of the second embodiment of the valve as a function of the inlet pressure
  • FIG. 5b shows the course of the fluid flow rate of the second embodiment of the valve as a function of the inlet pressure.
  • FIG. 1 shows an injection system for an internal combustion engine, with a fuel tank 10, from which fuel is required by means of a pre-demand pump 12.
  • the Vorforderpumpe 12 can be mechanically driven by a (not shown) drive shaft, the arrival Drive shaft may be fixedly coupled to a motor shaft of the internal combustion engine.
  • the Vorforderpumpe 12 is hydraulically coupled on the output side with a form control valve 28, which returns a part of the demanded by the Vorforderpumpe 12 fuel to the suction side of the Vorforderpumpe 12 when exceeding a predetermined fuel pressure at the output side of the Vorforderpumpe 12 and thus the fuel pressure at the output side of the Vorforderpumpe 12 largely constant.
  • a high-pressure pump 14 Downstream of the pre-demand pump 12, a high-pressure pump 14, which requests fuel into a fuel reservoir 16 via a fuel storage supply line 44.
  • the high-pressure pump 14 the fuel to be injected by means of injectors 18 in combustion chambers of the internal combustion engine, reach a relatively high injection pressure.
  • the high pressure pump 14 may preferably be formed as a radial piston pump or as a series piston pump with a plurality of cylinder units, as are known for use in injection systems of internal combustion engines.
  • the high-pressure pump 14 is connected downstream to the fuel accumulator 16, which in turn is hydraulically coupled via lines to the one injector 18 or a plurality of injectors 18.
  • Each of the injectors 18 is associated with a combustion chamber of the internal combustion engine and each can be controlled so that fuel is injected into the combustion chamber. Excess fuel can be returned from the injectors 18 via an Inj ektorrucklauf für 46 to the fuel tank 10.
  • a valve 22 is arranged in a downstream of the high-pressure pump 14 and upstream of the fuel reservoir 16 branching line 42. When a predetermined fuel pressure is exceeded, the valve 22 opens, and a partial flow of the fuel demanded by the high-pressure pump 14 can be returned to the fuel tank 10 via the line 42 branching off downstream of the high-pressure pump 14 and upstream of the fuel reservoir 16.
  • a volume flow control valve 20 is further arranged, which allows a low-pressure side control of the fuel flow, which is to be supplied to the high-pressure pump 14.
  • the volume flow control valve 20 can be controlled as a function of a fuel pressure measured in the fuel reservoir 16, which is determined by a pressure sensor 24, as well as in dependence on further input variables.
  • the housing of the high-pressure pump 14 can be wound, whereby cooling and lubrication of the high-pressure pump 14 is made possible.
  • a Spul effetsventil 32 and hydraulically in series a Spul effetsdrossel 34 is arranged.
  • the Spul effetsdrossel 34 serves to limit the diverted to Spulungs ultimatelyen in the Spul effet 30 Kraftstoffström.
  • the Spul effetsventil 32 is designed so that it releases the current flowing through the Spul effet 30 Brennstoffström only when exceeding a planned fuel pressure of the output side of the Vorforderpumpe 12.
  • the opening pressure at the Spul effetsventil 32 must be greater than the opening pressure of the intake valves (not shown) of the high-pressure pump 14 and the intervening line. This is the only way to ensure that the winding of the high pressure pump 14 is only used when the operating pressure of the high pressure pump 14 is reached. This ensures that the pressure build-up on the suction side of the high pressure pump 14 is not delayed.
  • the fuel used for Spulungs- purposes can leave the high-pressure pump 14 via a Spulrucklauftechnisch 35 and be returned via this in the fuel tank 10.
  • filters 36, 38 are arranged in front of the front-end pump 12 and the volume flow control valve 20 for protection against particles entrained in the fuel flow or for separating water.
  • a first filter 36 is provided to protect the Vorforderpumpe 12 hydraulically between the fuel tank 10 and the Vorforderpumpe 12.
  • a second filter 38 is arranged in front of the volume flow control valve 20 to protect the volume flow control valve 20 and the high-pressure pump 14.
  • the valve 22 is branched off in the downstream of the high-pressure pump 14 and upstream of the fuel reservoir 16
  • Line 42 is arranged, the output side of which is coupled to an injector return line 46 of the at least one injector 18.
  • the Spulrucklauftechnisch 35, the branching line 42 and the Injektorrucklauf effet 46 of the injectors 18 are preferably returned to the fuel tank 10.
  • FIG. 2 shows in detail a first embodiment of the valve 22 which is arranged between the fuel storage supply line 44 and the branching line 42 downstream of the high-pressure pump 14.
  • the valve 22 has a valve housing 50 with a longitudinal axis X.
  • a Ventilgehauseausnaturalung 52 is formed in the valve housing 50 .
  • Upstream of the valve housing recess 52 is a fluid inlet opening 54 and downstream of the valve housing.
  • Tilgehauseausnaturalung 52 a Fluidaustrittso réelle 56 is arranged.
  • the fluid inlet opening 54 and the fluid outlet opening 56 can be hydraulically coupled to the valve housing recess 52.
  • a Ventilkorper 58 is arranged, which is axially movable in the VentilgehauseausEnglishung 52.
  • valve body 58 By means of a spring element 60, the valve body 58 can be acted upon by force in the direction of the fluid inlet opening 54.
  • the valve housing recess 52 has a wall 66 on which a first sealing seat 62 and a second sealing seat 64 are formed.
  • the valve body 58 has a first seat area 68 in a lower section with reference to FIG. 2 and a second seat area 70 with an upper section with respect to FIG. 2.
  • Both the first sealing seat 62 and the second sealing seat 64 of the wall 66 of the valve housing recess 52 as well as the first seating area 68 and the second seating area 70 of the valve body 58 are conically formed in the embodiment shown here.
  • the first sealing seat 62 of the wall 66 of the valve housing recess 52 and the first seat portion 68 of the Ventilkorpers 58 may cooperate such that a fluid flow between the Fluideintrittso réelle 54 and the Fluidaustrittso réelle 56 is interrupted.
  • the second sealing seat 64 on the wall 66 of the VentilgehauseausEnglishung 52 so cooperate with the second seat portion 70 of the Ventilkorpers 58 that a flow of fluid from the Fluideintrittso réelle 54 is prevented to the Fluidaustrittso réelle 56.
  • valve body 58 In a starting position in which the fluid pressure at the fluid inlet opening 54 assumes only a small value, the valve body 58 is pressed by the spring force of the spring element 60 against the wall 66 of the valve housing recess 52 such that the first Sealing seat 62 of the wall 66 of the VentilgehauseausEnglishung 52 and the first seat portion 68 of Ventilkorpers 58 sealingly prevent fluid throughput through the Fluidaustrittso réelle 56.
  • the first sealing seat 62 of the wall 66 of the valve housing recess 52 has a first cone opening angle ALPHA 1.
  • the second sealing seat 64 of the wall 66 of the valve housing recess 52 has a second cone opening angle ALPHA_2, and the second cone opening angle ALPHA_2 of the second sealing seat 64 of the wall 66 is smaller than the first Cone opening angle ALPHA_1 of the first sealing seat 62 of the wall 66.
  • the cone-shaped first seating area 68 of the valve body 58 has a first cone opening angle BETA_1, and the second seating area 70 of the valve body 58 has a second cone opening angle BETA 2.
  • the first cone opening angle BETA 1 of the first seating area 68 of the valve body 58 is smaller than the second cone opening angle BETA 2 the second seating area of the valve body 58.
  • FIG. 3 a shows the course of an effective throttle area A of the valve 22 as a function of a fluid pressure P at the fluid inlet opening 54.
  • the effective throttle area A In a third region of the fluid pressure P at the fluid inlet opening 54 above the first fluid pressure value P 1 and below the second fluid pressure value P 2, the effective throttle area A first increases from zero to a maximum effective throttle area A_MAX. In a further increase of the fluid pressure P at the fluid inlet opening 54 to a third fluid pressure value P_3, the effective throttle area A is initially equal to the maximum effective throttle area A_MAX. Finally, the second seating area 70 of the valve body 58 approximates the second sealing seat 64 of the wall 66 of the valve housing recess 52 such that the effective throttle area A continuously decreases until it finally becomes zero for the second fluid pressure value P 2.
  • first cone opening angle ALPHA 1 of the first sealing bit 62 of the wall 66 of the valve housing recess 52 is greater than the second cone opening angle ALPHA 2 of the second sealing seat 64 of the wall 66 of the valve housing recess 52 or the first cone opening angle BETA_1 of the first seating area 68 of the valve body 58 is smaller
  • second cone opening angle BETA_2 of the second seat portion 70 of the valve body 58 it can be easily achieved that an increase in the effective throttle area A occurs when passing through a small fluid pressure area and a reduction in the effective throttle area A is possible when passing through a large fluid pressure area.
  • FIG. 3b shows a profile of a fluid flow rate FR as a function of the fluid pressure value P.
  • a fluid throughput through the fluid outlet opening 56 is provided in the third region of the fluid pressure at the fluid inlet opening 54 above the first fluid pressure value P_l and below the second fluid pressure value P_2.
  • the fluid throughput increases in a fourth range of the fluid pressure at the fluid inlet opening 54 above the first fluid pressure value P 1 and below a third fluid pressure value P 3 initially from zero to a second fluid flow rate FR 2.
  • the fluid flow rate FR through the fluid outlet opening 56 finally decreases again from the maximum second fluid flow value FR_ 2 to zero.
  • first cone opening angle ALPHA_1 of the first sealing seat 62 is greater than the second cone opening angle ALPHA_2 of the second sealing seat 64 and the first cone opening angle BETA 1 of the first seating area 68 is smaller than the second cone opening angle BETA 2 of the second seating area 70 of the valve body 58, it is achieved that the fluid flow rate in a small fluid pressure range increases from zero to the second fluid flow rate value FR 2, while Fluid flow rate FR falls in a large fluid pressure range from the second fluid flow rate FR 2 to the first fluid flow rate FR_1 (equal to zero).
  • valve 22 is shown in a second embodiment.
  • the valve 22 of the second embodiment differs from the valve 22 of the first embodiment in that the Ventilkorper 58 in its Fluidaustritts- opening 56 facing region has a cylinder portion 72 having a cylindrical portion 74 of the wall 66 of the Ventilgehauseaus Principleung 52 to form a gap 76 corresponds, wherein a gap length L of the gap 76 is variable.
  • the gap length L increases continuously as the fluid pressure P between the first fluid pressure value P 1 and the second fluid pressure value P 2 increases, from a minimum gap length L MIN to a maximum gap length L MAX. Above the second fluid pressure value P 2, the gap length L remains constant at the maximum gap length L_MAX.
  • the fluid flow rate FR is equal to zero (FIG. 5b).
  • the fluid flow rate from zero to the second fluid flow rate value FR 2 increases.
  • the fluid flow rate FR drops continuously from the second fluid flow rate value FR 2 to the first fluid flow rate value FR 1. This is possible by controlling the fluid flow rate FR over the gap length L between the minimum gap length L MIN up to the maximum gap length L MAX.
  • the fluid pressure P is greater than the second fluid pressure value P_2, it is achieved that, by leaving the gap length L at the maximum gap length L MAX and the absence of the second sealing seat 64 of the wall 66, the fluid flow rate substantially assumes the constant first fluid flow rate value FR_1.
  • the pre-demand pump 12 requires fuel from the fuel tank 10. By means of the admission pressure control valve 28, the pressure of the fuel to be supplied to the high-pressure pump 14 is limited.
  • the precharge pump 12 supplies the fuel via the second filter 38 to the volume flow control valve 20. At this, the fuel flow rate for the suction side of the high-pressure pump 14 can be adjusted.
  • the high-pressure pump 14 supplies the fuel reservoir 16 via the fuel storage line 44 with the amount of fuel required for the injectors 18.
  • the pressure required for the fuel reservoir 16 can first be adjusted by means of the pressure sensor 24 via a volume flow control on the volume flow control valve 20.
  • a fluid leakage flow can occur at the volume flow control valve 20.
  • the valve 22 each open so far that this leakage fluid flow via the downstream of the high-pressure pump 14 and upstream of the fuel reservoir 16 branching line 42 can flow into the fuel tank 10, together with the fluid from the Spulrucklauf- line 35 and the effluent via the Injektorrucklauftechnisch 46 from the injectors 18 fluid.
  • the fluid flow rate FR continuously decreases in the largest possible portion of the third area of the fluid pressure at the fluid inlet opening 54 above the first fluid pressure value P 1 and below the second fluid pressure value P_2, since in this case the valve 22 is particularly good Control characteristic with respect to a occurring in the third region of the fluid pressure at the Fluideintrittso réelle 54 above the first fluid pressure value P_l and below the second fluid pressure value P_2 fluid leakage flow through the flow control valve 20 of the injection system has. It is thus possible with the aid of the valve 22 to dissipate the fluid leakage flow occurring at the volume flow control valve 20 in a particularly simple manner via the branching line 42 to the fuel tank 10.
  • the fluid flow rate FR through the valve 22 and thus via the branching line 42 is prevented in order to allow an undisturbed starting of the injection system.
  • the fluid flow rate FR through the valve 22 is likewise prevented or restricted to the small fluid flow rate value FR 1 in order to keep the fluid leakage flow rate via the branching line 42 small , as this is always associated with a loss of energy at the injection system.
  • the volume flow control valve 20 is thus over the entire control range, the active actuator to be set.

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

Abstract

L'invention se rapporte à une soupape (22) comprenant : une boîte de soupape (50) comportant un évidement de boîte de soupape (52) présentant une paroi (66); une ouverture d'entrée de fluide (54) et une ouverture de sortie de fluide (56) situées dans la boîte de soupape (50) et pouvant être hydrauliquement couplées à l'évidement de corps de soupape (52); un siège d'étanchéité (62, 64) situé sur la paroi (66) de l'évidement de boîte de soupape (52); un corps de soupape (58) axialement mobile entre l'ouverture d'entrée de fluide (54) et l'ouverture de sortie de fluide (56) dans l'évidement de boîte de soupape (52), lequel le corps comprenant une zone de siège (68, 70) coopérant avec le siège d'étanchéité (62, 64) de manière à empêcher le fluide de s'écouler par l'ouverture de sortie de fluide (56) dans une position fermée et à permettre au fluide de s'écouler par l'ouverture de sortie de fluide (56) dans une position ouverte; et un élément de ressort (60) dont la force permet d'actionner le corps de soupape (58). Dans une première plage de pressions fluidiques inférieure à une première valeur de pression fluidique (P_1) au niveau de l'ouverture d'entrée de fluide (54), on empêche le fluide de s'écouler par l'ouverture de sortie de fluide (56). Dans une deuxième plage de pressions fluidiques supérieure à une deuxième valeur de pression fluidique (P_2), on permet au fluide de s'écouler par l'ouverture de sortie de fluide (56) avec une première valeur de débit maximale (FR_1). Dans une troisième plage de pressions fluidiques supérieure à la première valeur de pression fluidique (P_1) et inférieure à la deuxième valeur de pression fluidique (P_2), on permet au fluide de s'écouler par l'ouverture de sortie de fluide (56) avec une deuxième valeur de débit maximale (FR_2) qui est supérieure à la première valeur de débit maximale (FR_1).
PCT/EP2008/053645 2007-04-05 2008-03-27 Soupape et système d'injection pour un moteur à combustion interne comprenant une soupape Ceased WO2008122521A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007016625.9 2007-04-05
DE102007016625A DE102007016625A1 (de) 2007-04-05 2007-04-05 Ventil und Einspritzanlage für eine Brennkraftmaschine mit Ventil

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WO2008122521A1 true WO2008122521A1 (fr) 2008-10-16

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WO (1) WO2008122521A1 (fr)

Families Citing this family (3)

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Publication number Priority date Publication date Assignee Title
DE102008058288A1 (de) * 2008-11-20 2010-05-27 Continental Mechanical Components Germany Gmbh Druckbegrenzungsventil und Hochdruckpumpe mit einem Druckbegrenzungsventil
DE102016110279A1 (de) * 2015-11-25 2017-06-01 Hilite Germany Gmbh Rückschlagventil für ein Pleuel für eine variable Verdichtung einer Brennkraftmaschine sowie Pleuel mit einem derartigen Rückschlagventil
EP3173601B1 (fr) * 2015-11-25 2018-03-14 Hilite Germany GmbH Clapet de non-retour pour une bielle pour une compression variable d'un moteur à combustion interne et bielle comprenant un tel clapet de non-retour

Citations (7)

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US2033839A (en) * 1934-04-20 1936-03-10 Bryce Ltd Pressure equalizing valve
US2608208A (en) * 1947-09-18 1952-08-26 Atlas Diesel Ab Pressure reduction valve
EP0487944A1 (fr) * 1990-11-28 1992-06-03 Herion-Werke KG Soupape de sécurité
DE19822671A1 (de) * 1998-05-20 1999-11-25 Bosch Gmbh Robert Druckbegrenzungsventil
WO2002077446A1 (fr) * 2001-03-27 2002-10-03 L'orange Gmbh Soupape de limitation de pression pour systemes d'injection de carburant
EP1251266A1 (fr) * 2001-04-18 2002-10-23 Robert Bosch Gmbh Dispositif de limitation de pression et système de combustible avec tel dispositif de limitation de pression
WO2004027250A1 (fr) * 2002-09-13 2004-04-01 Robert Bosch Gmbh Dispositif d'injection de carburant pour moteur à combustion interne

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2033839A (en) * 1934-04-20 1936-03-10 Bryce Ltd Pressure equalizing valve
US2608208A (en) * 1947-09-18 1952-08-26 Atlas Diesel Ab Pressure reduction valve
EP0487944A1 (fr) * 1990-11-28 1992-06-03 Herion-Werke KG Soupape de sécurité
DE19822671A1 (de) * 1998-05-20 1999-11-25 Bosch Gmbh Robert Druckbegrenzungsventil
WO2002077446A1 (fr) * 2001-03-27 2002-10-03 L'orange Gmbh Soupape de limitation de pression pour systemes d'injection de carburant
EP1251266A1 (fr) * 2001-04-18 2002-10-23 Robert Bosch Gmbh Dispositif de limitation de pression et système de combustible avec tel dispositif de limitation de pression
WO2004027250A1 (fr) * 2002-09-13 2004-04-01 Robert Bosch Gmbh Dispositif d'injection de carburant pour moteur à combustion interne

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