EP2659125B1 - Dispositif de regulation de pression d'un système d'injection de carburant ayant une soupape arrange du côté pression de la pompe - Google Patents

Dispositif de regulation de pression d'un système d'injection de carburant ayant une soupape arrange du côté pression de la pompe Download PDF

Info

Publication number
EP2659125B1
EP2659125B1 EP11794505.5A EP11794505A EP2659125B1 EP 2659125 B1 EP2659125 B1 EP 2659125B1 EP 11794505 A EP11794505 A EP 11794505A EP 2659125 B1 EP2659125 B1 EP 2659125B1
Authority
EP
European Patent Office
Prior art keywords
pressure
pump
valve
fuel
pressure regulating
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.)
Not-in-force
Application number
EP11794505.5A
Other languages
German (de)
English (en)
Other versions
EP2659125A1 (fr
Inventor
Siamend Flo
Frank Nitsche
Alexander Schenck Zu Schweinsberg
Thorsten Allgeier
Juergen Arnold
Peter Schenk
Michael Bauer
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 EP2659125A1 publication Critical patent/EP2659125A1/fr
Application granted granted Critical
Publication of EP2659125B1 publication Critical patent/EP2659125B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • 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
    • 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
    • F02M59/34—Varying fuel delivery in quantity or timing by throttling of passages to pumping elements or of overflow passages, e.g. throttling by means of a pressure-controlled sliding valve having liquid stop or abutment
    • 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
    • F02M63/0045—Three-way valves
    • 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
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing
    • F04B49/246—Bypassing by keeping open the outlet valve
    • 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

Definitions

  • the invention relates to a pressure regulating arrangement of a pump-operated fuel injection system for an internal combustion engine, with a valve arranged on the pressure side of the pump for discharging fuel under pressure from the pressure side of the pump to the suction side of the pump. Furthermore, the invention relates to a fuel injection system with such a pressure regulating arrangement.
  • the pressure is generated by means of a pump, a so-called high-pressure pump, which is mechanically driven by the internal combustion engine or engine in known fuel injection systems.
  • An electromechanical, in particular electromagnetic, quantity control valve controls the quantity of fuel delivered by the pump per unit of time into a high-pressure region, a so-called rail. Together with a high pressure signal measured by a high-pressure sensor, an engine control unit thus regulates the pressure in the high-pressure range to the desired level by means of the quantity control valve.
  • the control of injection valves on the internal combustion engine takes place on the basis of the measured pressure signal.
  • Fuel injection systems are in the EP1898084 A1 , of the DE102008043217 A1 .
  • a pressure regulating arrangement of a pump-operated fuel injection system for an internal combustion engine having a valve disposed on the pressure side of the pump for discharging fuel under pressure from the pressure side and the high pressure side of the pump to the suction side and the low pressure side of the pump, respectively.
  • a variable throttle On the suction side of the pump, a variable throttle is provided with a variable throttle effect, which serves to throttle the amount of fuel supplied to the pump.
  • the function of the valve (76) and the variable throttle (78) are realized with a single closure body (84).
  • a purely self-sufficient pressure regulation is created on the pump of a fuel injection system via purely mechanical components.
  • electrical, electrohydraulic or electronic components can be dispensed with.
  • the invention combines two pressure control methods, namely the method of pressure control by means of the valve from the pressure range to the suction region of the pump and the method of suction throttling the pump.
  • the suction throttling is preferably carried out by means of a proportional valve, which opens and closes in proportion to the applied pressure.
  • the advantages of the solution according to the invention are particularly low system costs, in particular due to the elimination of otherwise required electromagnetic components.
  • particularly preferred is no electromechanical quantity control valve, as is the case with known fuel injection systems.
  • the energy requirement for the fuel injection according to the invention and thus the fuel consumption of the entire system due to the lack of electrical components is lower.
  • the valve is advantageously functionally coupled to the variable throttle.
  • the functional coupling of the valve with the variable throttle not only the pressure regulation but also the suction throttling of the pump takes place as a function of the pressure from the high-pressure region.
  • the pressure from the high pressure area thus controls the valve and the variable throttle and their throttle effect.
  • valve and variable throttle are preferably realized mechanically.
  • the pressure or overpressure generated by the pump is advantageously applied to the valve.
  • the valve opens in particular from a certain overpressure.
  • the open-Das Valve is preferably realized as a slide valve. It advantageously captures pressure peaks coming from the high pressure area.
  • the control with the variable throttle is thereby smoothed.
  • a pressure damper function is integrated in the pressure control arrangement and it can be achieved a better control quality.
  • valve and the variable throttle according to the invention in an assembly, in particular in the pump itself, integrated summarized.
  • the conduction paths can be kept very short, which improves the dynamics of the system and at the same time saves costs.
  • the weight is also reduced as compared to conventional systems.
  • the assembly is easier and cheaper.
  • valve and the variable throttle realized with a single closure body.
  • the valve and the variable throttle are preferably combined in one unit.
  • the function of the valve and the variable throttle are then integrated into a single hydraulically controlled valve unit, in particular a proportional valve unit.
  • the valve unit is designed as a spool valve with two control slots or control slot pairs on an associated cylinder, wherein the function of the valve and the variable throttle is formed here in each case with a control slot.
  • the closure body is preferably a piston which is resiliently biased against the pressure coming from the direction of the pump or high-pressure pump.
  • the piston is moved in the cylinder according to the height of the pressure of the high-pressure pump.
  • the control slots can be opened or closed. In this way, the function is provided as a variable throttle and valve in the smallest space with only a few components.
  • the closure body preferably completely covers either a first control slot or a second control slot on the cylinder.
  • the control slots which take over the function of the valve and the variable throttle, are arranged offset on the cylinder of the spool valve in the axial direction.
  • the closure body is thus preferably designed so that it can completely close only one of the two control slots, or - depending on the embodiment - at most partially covers both control slots.
  • the closure body is displaced so that the control slot which forms the valve, opens.
  • the opening movement simultaneously closes the control slot which maps the variable throttle.
  • the piston closes the control slot that forms the valve and at the same time opens the second control slot, which forms the variable throttle.
  • An important aspect of the design according to the invention is advantageous in that the throttling effect of the variable throttle is variable by the pressure generated by the pump.
  • the change in the throttling effect is preferably carried out in such a way that, as the pressure increases, the control slot forming the variable throttle is further closed. With the thus reduced passage area at the variable throttle, the fuel quantity supplied to the high-pressure pump of the fuel injection system per unit time is reduced. The pump can draw less fuel, unnecessary pumping of the high-pressure pump is avoided.
  • the pressure regulating arrangement designed in accordance with the invention can advantageously also be developed to have an accumulator function.
  • the closure body and the control slots are designed and arranged such that the volume which releases the closure body in its movement from its rest position to reach a control slot, the amount of fuel can receive at least one cold start injection.
  • the storage of the fuel is particularly advantageous in cold start injection and even lower pump speed and makes the system according to the invention independent of electrical power amplifiers for maintaining the system pressure when stopping the engine, especially in start / stop systems.
  • the closure body moves back in the direction of its stop and replaces this amount of fuel, even if the pump has not yet fed.
  • the fuel pressure drops only insignificantly, depending on the spring design.
  • fuel is stored in the pressure control arrangement, which is elastically stored by the spring force and the specially selected low spring rate.
  • the geometries (diameter and stroke of the closure body, spring rate) of the pressure control arrangement are designed so that the storage volume is sufficient to store at least one cold start injection quantity.
  • the invention is in contrast to known methods for mechanical / hydraulic pressure control. These methods are firstly the so-called (pure) pressure relief via a pressure regulating valve and secondly the so-called (pure) suction throttling.
  • the pressure relief via a pressure control valve takes place when exceeding a predetermined pressure level.
  • the pressure rises in principle with the amount to be eliminated. Due to the coupling of the pump speed and thus the flow rate to the engine speed, therefore, the pressure increases with the speed and falls with increasing load on the engine.
  • this concept is in need of improvement, since the delivery rate of the pump is not reduced as needed and therefore higher drive performance (fuel consumption) and higher heat development is expected, especially at high speeds and low engine load (fuel cut).
  • On the control quality also has a negative effect, especially in pumps with discontinuous Full promotion in a short time large quantities must be diverted and therefore high-pressure pulsations can be stimulated.
  • the supply to the pump is throttled, the higher the pressure level, so as to prevent further increase of the pressure by further pumping the pump.
  • the high-pressure level is used to actuate the Saugdrosselung, relatively large forces occur on the associated variable throttle, which cause high restoring forces in the design of the throttle and therefore also lead to large return means (usually springs).
  • the control quality is due to the existing dead times due to the volumes between the suction throttle and the pump, in principle, less good than the system of a pressure regulator with pressure control valve.
  • the solution according to the invention makes it possible to design such fuel injection systems more cost-effectively with the same or almost the same function and to avoid the disadvantages mentioned.
  • the function of said pressure control valve and the suction throttling can be combined.
  • a fuel injection system 10 is shown with a pump 12.
  • the region on the suction side of the pump 12 is referred to as the low-pressure region and the region on the pressure-side of the pump 12 as the high-pressure region.
  • fuel is pumped from a tank 14 through an electric fuel pump 16 at a pressure of about 5 bar through a fuel filter 18 to a line 20.
  • a pressure relief valve 22 may direct fuel from the fuel pump 16 back into the tank 14. On line 16, a low pressure damper 24 is arranged.
  • the fuel delivery rate of the pump 12 is regulated by a quantity control valve 26.
  • the pump 12 generates a pressure of up to about 200 bar, with which the fuel is conveyed through a Raildrossel 44 in a rail 28. This high pressure defines the already mentioned high-pressure region on the pressure side of the pump 12. From the rail 28, the fuel can be injected via injection valves 30 into an internal combustion engine 32.
  • a possible overpressure of the pump 12 is derived from the high pressure area in the pump 12.
  • a return line 34 which leads back into the delivery chamber of the pump 12.
  • a check valve 36 mounted on the pressure side of the pump 12 forms the outlet valve of the pump 12 and prevents fuel from flowing in the opposite direction to its delivery direction.
  • Another, arranged in the return line 34 check valve 38 ensures that only fuel is returned under pressure in the pump 12.
  • the amount of fuel delivered by the pump 12 can be metered by the quantity control valve 26, so that the pump 12 ideally generates the setpoint control pressure.
  • the pumped amount of fuel is regulated via a comparatively complex electromechanical system.
  • a high pressure sensor 40 measures the pressure applied there.
  • a controller 42 receives the information regarding the rail pressure from the high pressure sensor 40 and processes it. According to the programming of the control unit 42, the quantity control valve 26 is activated. Thus, the quantity control valve 26 regulates the fuel delivery rate of the pump 12 due to the fuel pressure occurring and measured in the rail 24.
  • FIG. 2 an assembly 72 having an embodiment of the invention is shown.
  • the assembly 72 comprises an inner housing 74 on which a control slot 76, a control slot 78 and an inlet bore 80 are formed as a valve.
  • the control slots 76, 78 and the inlet bore 80 are openings in the inner housing 74 which allow fuel flow into or out of the inner housing 74.
  • the shape of the openings of the control slots 76, 78 preferably deviates from a rectangular or circular shape.
  • the shape is preferably substantially triangular with not curved inside legs, whereby the characteristic for the pressure regulating arrangement is favorably influenced.
  • the closure body 84 is based on a plunger 82 Fig. 2 pushed to the left.
  • the plunger 82 is formed with an intermediate portion 86 and a main portion 88.
  • the diameter of the intermediate region 86 acting as a tappet tip or push rod is smaller than that of the closure body 84.
  • the inner housing 74 is designed stepped and adapted in particular with its inner diameter to the diameter of the closure body 84. In this way, the closure body 84 can completely or partially close the control slot 76 and / or the control slot 78 in a fluid-tight sealing manner.
  • the closure body 84 can close both control slots 76, 78 at the same time.
  • any overlapping or purely serial triggering of the suction throttling with the pressure relief can be achieved.
  • the control quality can be optimally adjusted.
  • the closure body 84 and the intermediate region 86 are made in two parts.
  • the closure body 84 is biased in the inner housing 74 via the plunger 82 with a spring 90 frontally against an opposite return opening 92.
  • the spring geometry of the spring 90 is dimensioned so that the transverse force minimized to the spring and thus buckling of the spring 90 is prevented.
  • a seal 94 is formed in the form of a seat seal.
  • a flow chamber 96 is formed in the inner housing, which is initially connected to the two control slots 76, 78, and the inlet bore 80. Depending on the respective displacement of the closure body 84 in the inner housing 74, this flow space 96 can be increased or reduced voluminously.
  • the control slot 76 is connected by a parallel line 98 with the flow space 96 or the parallel line 98 can be considered as part of the flow space 96.
  • Fig. 2 is a coupling of a pump 100 shown in simplified form, this may be electrically or as preferred preferably mechanically driven.
  • fuel is passed under high pressure through a pressure line 102 to a rail 104.
  • the fuel Via a branch 106 in the pressure line 102, the fuel also reaches the return opening 92. Since the closure body 84 is biased against the return opening 92, initially no fuel flows into the inner housing 74. However, if the pressure which the pump 100 generates becomes too high , So this generates overpressure whose pressure force is higher than the counter-pressure force of the spring 90, the closure body 84 is based on Fig. 2 pushed to the right (back). The closure body 84 thus releases the return opening 92 and fuel can flow into the inner housing 74. The inflowing fuel is stored in the inner housing 74 (accumulator function of the arrangement).
  • closure body 84 releases the control slot 78 during this time.
  • fuel conveyed by a fuel pump 108, flows via the inlet bore 80, a flow chamber 96 and the control slot 78 into a suction line 110 leading to the pump 100.
  • the closure body 84 If the pressure rises above a defined desired pressure, the closure body 84 successively closes the control slot 78 and opens the control slot 76. Through the control slot 76 the fuel flows through a parallel line 98 into the flow chamber 96, where it mixes with the fuel from the low pressure region and is led to the pump 100.
  • control slot 76 performs the function of a valve or a pressure control valve for pressure control and the control slot 78, the function of a variable throttle or a suction throttle.
  • the closure body 84 and the control slots 76,78 are further preferably designed and arranged such that the volume which the closure body 84 releases in its movement from its rest position at the return opening 92 until reaching a control slot 76, 78, the amount of fuel at least one cold start injection can record.
  • Such a design realizes an axial free travel of the closure body 84 in the inner housing 74 between a closure body stop in its rest position and the beginning of a control slot 76, 78 for pressure relief or suction throttling.
  • the pressure control valve according to the invention prevents a possible, too large pressure drop by the fuel storage function, especially for large injection quantities in the cold start.
  • the geometries (diameter and stroke of the closure body 84, spring rate of the spring 90) of the pressure regulating arrangement are designed so that the storage volume is sufficient to store at least one cold start injection quantity.
  • Fig. 3 is the assembly 72 made Fig. 2 shown in an integrative construction with the pump 100.
  • the pump 100 is positioned below the assembly 72 in a common housing.
  • the Fig. 4 shows an enlarged section of the Fig. 3 , In particular, the course of the fuel flow is shown here.
  • a dashed arrow line the fuel flow from the fuel pump 108, through the inlet bore 80 into the flow chamber 96, and from there again through the control slot 78 in the direction of the pump 100 shown (suction pressure, low pressure region).
  • the fuel flow is shown with a solid arrow line, which is first performed by the pump 100 to the rail 104 (high-pressure area).
  • a positive pressure is passed through the branch 106 to the return opening 92 and displaces the closure body 84.
  • the return opening 92 is opened and the fuel continues to the control slot 76, and from there through the parallel line 98 to the flow space 96.
  • the recirculated fuel unites with the from the inlet of the fuel pump 108. If the pressure drops below the setpoint control pressure again, then the closure body 84 shifts to the left with respect to the figure and opens the control slot 78 for suction throttling and closes the control slot 76 for pressure control. Or, in other words, as soon as the force of the spring 90 is sufficient to push the closure body 84 back against the decreasing force of the overpressure.

Claims (8)

  1. Ensemble de régulation de pression d'un système d'injection de carburant fonctionnant à l'aide d'une pompe (12, 100) pour un moteur à combustion interne (32), comprenant une soupape (76) agencée côté pression de la pompe (12, 100) pour évacuer du carburant sous pression à partir du côté pression de la pompe (12, 100) jusqu'au côté aspiration de la pompe (12, 100), un étranglement variable (78) présentant un effet d'étranglement modifiable étant prévu du côté aspiration de la pompe (12, 100), pour limiter la quantité de carburant acheminée jusqu'à la pompe (12, 100), caractérisé en ce que la fonction de la soupape (76) et celle de l'étranglement variable (78) sont réalisées à l'aide d'un corps de fermeture (84) unique.
  2. Ensemble de régulation de pression selon la revendication 1,
    caractérisé en ce que la soupape (76) est accouplée fonctionnellement, en particulier accouplée mécaniquement, à l'étranglement variable (78).
  3. Ensemble de régulation de pression selon la revendication 1 ou 2,
    caractérisé en ce que la soupape (76) et l'étranglement variable (78) sont groupés de manière intégrée dans une unité de construction, en particulier dans la pompe (12, 100).
  4. Ensemble de régulation de pression selon l'une quelconque des revendications 1 à 3,
    caractérisé en ce qu'une première et une deuxième fente de commande (76, 78) sont prévues, parmi lesquelles, dans différentes positions du corps de fermeture (84), soit la première fente de commande (76) soit la deuxième fente de commande (78) est entièrement fermée.
  5. Ensemble de régulation de pression selon l'une quelconque des revendications 1 à 4,
    caractérisé en ce que l'effet d'étranglement de l'étranglement variable (78) peut être modifié par la pression produite par la pompe (12, 100).
  6. Ensemble de régulation de pression selon l'une quelconque des revendications 1 à 5,
    caractérisé en ce qu'une fonction d'accumulateur de pression est intégrée dans celui-ci.
  7. Ensemble de régulation de pression selon l'une quelconque des revendications 1 à 6,
    caractérisé en ce qu'une fonction d'amortisseur de pression est intégrée dans celui-ci.
  8. Système d'injection de carburant (10) fonctionnant à l'aide d'une pompe, comprenant un ensemble de régulation de pression selon l'une quelconque des revendications 1 à 6.
EP11794505.5A 2010-12-27 2011-12-14 Dispositif de regulation de pression d'un système d'injection de carburant ayant une soupape arrange du côté pression de la pompe Not-in-force EP2659125B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010064219 DE102010064219A1 (de) 2010-12-27 2010-12-27 Druckregelanordnung eines Kraftstoffeinspritzsystems mit einem druckseitig von einer Pumpe angeordneten Ventil
PCT/EP2011/072829 WO2012089511A1 (fr) 2010-12-27 2011-12-14 Ensemble de régulation de la pression d'un système d'injection de carburant comportant une soupape agencée côté pression d'une pompe

Publications (2)

Publication Number Publication Date
EP2659125A1 EP2659125A1 (fr) 2013-11-06
EP2659125B1 true EP2659125B1 (fr) 2014-09-17

Family

ID=45319125

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11794505.5A Not-in-force EP2659125B1 (fr) 2010-12-27 2011-12-14 Dispositif de regulation de pression d'un système d'injection de carburant ayant une soupape arrange du côté pression de la pompe

Country Status (4)

Country Link
EP (1) EP2659125B1 (fr)
CN (1) CN103270289B (fr)
DE (1) DE102010064219A1 (fr)
WO (1) WO2012089511A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2550144A (en) * 2016-05-10 2017-11-15 Delphi Automotive Systems Lux Fuel pump
CN106321309A (zh) * 2016-08-26 2017-01-11 重庆凯龙科技有限公司 压力侧设有节流部的燃油调节泵
CN106321311B (zh) * 2016-08-30 2018-10-12 重庆凯龙科技有限公司 带有弹簧振动装置的燃油调节泵

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH672168A5 (fr) * 1987-01-30 1989-10-31 Nova Werke Ag
DE4323683A1 (de) * 1993-07-15 1995-01-19 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
JP3304755B2 (ja) * 1996-04-17 2002-07-22 三菱電機株式会社 燃料噴射装置
JP4453028B2 (ja) * 2005-03-30 2010-04-21 株式会社デンソー 高圧燃料ポンプ
JP2008057451A (ja) * 2006-08-31 2008-03-13 Hitachi Ltd 高圧燃料供給ポンプ
DE102008043217A1 (de) * 2008-10-28 2010-04-29 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine
DE102008058288A1 (de) * 2008-11-20 2010-05-27 Continental Mechanical Components Germany Gmbh Druckbegrenzungsventil und Hochdruckpumpe mit einem Druckbegrenzungsventil

Also Published As

Publication number Publication date
CN103270289A (zh) 2013-08-28
DE102010064219A1 (de) 2012-06-28
WO2012089511A1 (fr) 2012-07-05
CN103270289B (zh) 2016-05-04
EP2659125A1 (fr) 2013-11-06

Similar Documents

Publication Publication Date Title
DE102004013307B4 (de) Kraftstoffhochdruckpumpe mit einem Druckbegrenzungsventil
DE10327411B4 (de) Druckbegrenzungsventil sowie Kraftstoffsystem mit einem solchen Druckbegrenzungsventil
EP1411238A1 (fr) Soupape de limitation de pression pour un system d'injection de carburant
EP2798191B1 (fr) Soupape de décharge de carburant pour un injecteur de carburant et injecteur de carburant équipé d'une soupape de décharge de carburant
DE102005022661A1 (de) Fluidpumpe, insbesondere Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine mit Kraftstoff-Direkteinspritzung
DE102005033638A1 (de) Kraftstoff-Fördereinrichtung, insbesondere für eine Brennkraftmaschine
WO2012104236A2 (fr) Unité pompe pour une pompe haute pression
EP2735725B1 (fr) Soupape d'injection de carburant pour moteurs à combustion interne
DE102010031628A1 (de) Kraftstofffördereinrichtung für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
EP1357283B1 (fr) Dispositif d'injection de carburant pour un moteur à combustion interne
EP2659125B1 (fr) Dispositif de regulation de pression d'un système d'injection de carburant ayant une soupape arrange du côté pression de la pompe
EP2694796B1 (fr) Soupape de vidange pour systèmes d'injection d'huile lourde à rampe commune
DE10139055A1 (de) Verfahren, Computerprogramm, Steuer- und/oder Regelgerät sowie Kraftstoffsystem für eine Brennkraftmaschine
EP2156050B1 (fr) Système d'amplification de pression pour au moins un injecteur de carburant
EP1970556A1 (fr) Injecteur
WO2012089378A1 (fr) Pompe d'un système d'injection de carburant
DE102012203724A1 (de) Kraftstofffördereinrichtung für ein Kraftstoffeinspritzsystem mit einem Überströmventil sowie Überströmventil
DE102010042582A1 (de) Überströmventil für ein Kraftstoffeinspritzsystem einer Brennkraftmaschine
DE102007016625A1 (de) Ventil und Einspritzanlage für eine Brennkraftmaschine mit Ventil
DE102010064179A1 (de) Druckregelanordnung eines Kraftstoffeinspritzsystems
DE102011089964A1 (de) Drucksteuerventil für ein Kraftstoffeinspritzsystem sowie Kraftstoffeinspritzsystem
DE102007001365A1 (de) Injektor mit Steuer- und Schaltkammer
DE102017222204A1 (de) Kraftstofffördereinrichtung für kryogene Kraftstoffe
DE102004007317A1 (de) Kraftstoffhochdruckpumpe für eine Brennkraftmaschine
DE102013211196A1 (de) Ventilanordnung zur Steuerung der Fördermenge einer Hochdruckpumpe sowie Hochdruckpumpe

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20130729

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20140613

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 687831

Country of ref document: AT

Kind code of ref document: T

Effective date: 20141015

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502011004427

Country of ref document: DE

Effective date: 20141030

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141217

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141218

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20140917

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150119

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150117

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502011004427

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20141231

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

Ref country code: LU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141214

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

26N No opposition filed

Effective date: 20150618

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20141214

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20141231

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20141231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 5

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20111214

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 7

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 687831

Country of ref document: AT

Kind code of ref document: T

Effective date: 20161214

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161214

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140917

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20211220

Year of fee payment: 11

Ref country code: GB

Payment date: 20211222

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20220224

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20211230

Year of fee payment: 11

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502011004427

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20221214

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20221214

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230701

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20221231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20221214