EP1403509B1 - Dispositif de limitation de pression et système de combustible avec tel dispositif de limitation de pression - Google Patents

Dispositif de limitation de pression et système de combustible avec tel dispositif de limitation de pression Download PDF

Info

Publication number
EP1403509B1
EP1403509B1 EP20030003826 EP03003826A EP1403509B1 EP 1403509 B1 EP1403509 B1 EP 1403509B1 EP 20030003826 EP20030003826 EP 20030003826 EP 03003826 A EP03003826 A EP 03003826A EP 1403509 B1 EP1403509 B1 EP 1403509B1
Authority
EP
European Patent Office
Prior art keywords
pressure
fuel
limiting device
pressure limiting
collar
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.)
Expired - Lifetime
Application number
EP20030003826
Other languages
German (de)
English (en)
Other versions
EP1403509A2 (fr
EP1403509A3 (fr
Inventor
Helmut Rembold
Wolfgang Bueser
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 EP1403509A2 publication Critical patent/EP1403509A2/fr
Publication of EP1403509A3 publication Critical patent/EP1403509A3/fr
Application granted granted Critical
Publication of EP1403509B1 publication Critical patent/EP1403509B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • 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
    • 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
    • F02M55/04—Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
    • 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
    • F02M63/02—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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
    • 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
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator
    • 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

Definitions

  • the present invention relates to a pressure limiting device for a fuel system of an internal combustion engine
  • Pressure limiting devices are known from the market. They are preferably used in such fuel systems, which are used in internal combustion engines with gasoline direct injection. Such fuel systems usually have a low pressure range and a high pressure range. An electric fuel pump delivers the fuel into the low pressure range, from which the fuel via a high pressure pump in a fuel rail ("common rail called) is promoted. The pressure in the fuel rail is usually controlled by a pressure control or a quantity control valve.
  • a pressure limiting device is provided in the high pressure region of the fuel system.
  • This is generally a conventional pressure relief valve with a acted upon by a spring against a valve seat valve element.
  • the valve member lifts off the valve seat so that fuel can flow from the inlet of the pressure relief valve to the outlet and thence back to the low pressure region of the fuel system.
  • the pressure limiting device In general, the pressure limiting device must be arranged in the region of the fuel collecting line, that is to say at a certain distance from the high-pressure pump. The reason for this is that during operation, the high-pressure pump generates pressure pulsations whose peaks can exceed the opening pressure of the pressure-limiting valve. If the pressure limiting valve were to be arranged directly at the high-pressure pump, there would be the danger that the pressure-limiting valve would open due to the pressure pulsations, although the maximum system pressure has not yet been reached. Only at a certain distance from the high pressure pump, it comes to a smoothing of Pressure pulsations due to throttle effects in the fuel line and due to the compressibility of the fuel.
  • the pressure relief valve so that its opening pressure is above the pressure peaks due to the pressure pulsations.
  • This pressure limiting valve can then be arranged in the immediate vicinity of the high pressure pump or even integrated into it. In emergency mode, so if the pressure control of the fuel rail is no longer working properly and then there is a higher pressure in the fuel rail than the normal system pressure, safe operation of the internal combustion engine must still be ensured. This in turn would require the design of the components of the high pressure region of the fuel system to the high opening pressure of the pressure relief valve. However, such components are relatively expensive.
  • a pressure limiting device in which the pressure pulsations are reduced by a compensation chamber, so that the pressure limiting device does not open during normal operation of the fuel pump despite the pressure pulsations caused by the high pressure pump. This allows the arrangement of the pressure relief device also in the vicinity of the high-pressure pump.
  • a pressure limiting device in which a first collar of a piston defines a compensation chamber. As soon as the volume of the compensation chamber increases due to pressure pulsations, the piston lifts off from a valve seat and releases a hydraulic connection between the high pressure region and the low pressure region of the fuel system. As a result, the efficiency of the fuel system deteriorates and the fuel is strongly heated by the dissipated energy.
  • the piston has a second collar, and on the second collar a control edge is formed, that the control edge so cooperates with a recess of the bore, that in the closed state of the pressure limiting device, the hydraulic connection between the high pressure fuel line and Low-pressure fuel line is interrupted, that the pressure limiting device opens only when the compensation chamber has reached a predetermined minimum volume, and that the minimum volume of the overlap of the control edge in the bore in the closed position of the pressure relief device depends.
  • This pressure limiting device according to the invention unlike the pressure limiting device known from the prior art, can be used without adaptation measures in virtually all fuel pumps or fuel systems. As a result, the required variety of variants is greatly reduced, which brings considerable economic advantages in the production, storage and repair of equipped with the pressure limiting device according to the invention fuel systems with it.
  • a spring is clamped between the piston and the housing, which acts on the piston in the direction of the closed position of the pressure limiting device.
  • the piston When the piston has a sealing cone at its end remote from the first collar and the sealing cone rests in the closed position of the pressure limiting device on a sealing seat of the housing, the pressure in the high-pressure region of the fuel system is maintained when the internal combustion engine is shut off, which prevents the formation of vapor bubbles.
  • a shoulder is formed in the housing, and that the piston bears against the shoulder in the closed position of the pressure-limiting device.
  • a further, particularly advantageous embodiment of the invention provides that the piston has a third collar, and that the compensation chamber is additionally limited by the third collar, wherein the diameter of the third collar is smaller than the diameter of the first collar.
  • the resulting hydraulic force is reduced to the first collar, which - with otherwise the same hydraulic boundary conditions - allows a smaller spring between the piston and housing.
  • the spring can be made smaller, which helps reduce the overall volume of the entire pressure limiting device. Due to the fact that a partial compensation of the hydraulic forces takes place between the first collar and the third collar, the forces exerted by the piston on the spring are very small, without the piston diameters becoming very small. In the series production of turned parts with diameters smaller than 4 mm and high precision, the production costs increase compared to slightly larger sized parts. As a result, the cost of the pressure limiting device according to the invention can be minimized.
  • the third collar with the bore defines a space and this space is at least indirectly hydraulically connected to a low-pressure region of the fuel system, so that any accumulating leaks can be dissipated.
  • the present invention also relates to a fuel system for supplying fuel for an internal combustion engine, with a reservoir, with a first fuel pump, which is connected on the input side to the reservoir, with a second fuel pump, which is the input side connected via a fuel connection to the first fuel pump, and with a pressure limiting device, which limits the pressure in a fuel connection on the output side of the second fuel pump.
  • Pressure limiting device is formed in the manner described above.
  • the second fuel pump comprises a 1-cylinder piston pump.
  • the pressure pulsations are particularly pronounced, so that here the pressure limiting device according to the invention works very effectively.
  • the pressure limiting device is attached to the second fuel pump, preferably integrated in this.
  • Such an arrangement of the pressure limiting device within the fuel system has the advantage that it is possible to dispense with a return line from the pressure limiting device, for example, to the low pressure region of the fuel system. As a result, the cost of the fuel system according to the invention are significantly reduced.
  • a fuel system as a whole bears the reference numeral 10. It comprises a low-pressure region 12 and a high-pressure region 14.
  • the low-pressure region 12 comprises a reservoir 16 in which fuel 18 is stored.
  • the fuel 18 is conveyed from the reservoir 16 by a first fuel pump 20.
  • This is an electric fuel pump.
  • the electric fuel pump 20 conveys into a low-pressure fuel line 22.
  • a filter 24 is initially provided after the electric fuel pump 20 as seen in the flow direction. Seen in the flow direction before the filter 24 branches off from the low-pressure fuel line 22 from a branch line 26, which leads back to the reservoir 16.
  • a pressure limiting valve 28 is arranged in the branch line 26 in the branch line 26, which leads back to the reservoir 16.
  • the low-pressure fuel line 22 leads to a second fuel pump 30. This is driven in a manner not shown here by the camshaft of an internal combustion engine (not shown).
  • the second fuel pump 30 is a 1-piston high-pressure pump. Upstream of the high pressure pump 30 are still in the low pressure fuel line 22 a Pressure damper 32 and a check valve 34 is arranged. Between the filter 24 and the pressure damper 32 branches from the low-pressure fuel line 22 from a branch line 36, in which a low-pressure regulator 38 is arranged.
  • the branch line 36 also leads back to the reservoir 16 for the fuel 18. From the high-pressure pump 30, a leakage line 40 leads to the branch line 36.
  • the high-pressure pump 30 conveys into a high-pressure fuel line 42, which leads via a check valve 44 to a fuel manifold 46.
  • Fuel injection valves 48 which in turn inject the fuel into a combustion chamber, not shown, of the internal combustion engine are in turn connected to the fuel manifold 46.
  • the pressure in the fuel rail 46 is detected by a pressure sensor 50.
  • the pressure in the high-pressure fuel line 42 and the fuel manifold 46, ie in the high-pressure region 14 of the fuel system 10, is controlled and / or regulated via a quantity control valve 52.
  • the connection takes place via a branch line 54.
  • the quantity control valve 52 is actuated by a 1, not shown, which in turn receives signals from the pressure sensor 50. In this way, a closed loop for the control of the pressure in the high pressure region 14 of the fuel system 10 is provided.
  • a pressure relief device 56 is combined with the high-pressure pump 30.
  • the exact structure of a first embodiment of a pressure limiting device 56 according to the invention can be seen from FIG. 2:
  • the high-pressure pump 30 and the pressure-limiting device 56 are accommodated in a common housing 58. Only one region of a delivery chamber 60 and the outlet valve 44 arranged on the outlet side of the delivery chamber 60 are visible from the high-pressure pump 30 in FIG.
  • the outlet valve 44 comprises a spherical valve element 64, which is acted upon by a spring 66 against a valve seat 68. Downstream of the exhaust valve 44, the high pressure fuel line 42 is visible.
  • the delivery chamber 60 is sealed off from the high-pressure fuel line 42 by the outlet valve 44.
  • a bore 70 is provided, in which a piston 72 is guided.
  • the piston 72 has a first collar 74 and a second collar 76.
  • the piston 72 is guided over the first collar 74 and the second collar 76 in the bore 70.
  • the fit of bore 70 and first collar 74 is sized so that the annular gap between bore 70 and first collar 74 serves as a throttle.
  • the fit of bore 70 and second collar 76 is sized so that a good sealing effect between the bore 70 and second collar 76 is achieved and the piston 72 is still displaced in the bore 70 still.
  • first collar 74 and second collar 76 has the Piston 72 has an annular groove 78 which communicates hydraulically with the high-pressure fuel line 42.
  • a bottom 80 of the bore 70 and the first collar 74 of the piston 72 define a compensation chamber 82, which is hydraulically connected to the high-pressure fuel line 42 via the annular gap between the bore 70 and the first collar 74.
  • annular recess 84 is concentric with the bore 70 is provided.
  • the annular groove 78 and the second collar 76 of the piston 72 form a control edge 86, which cooperates with the recess 84.
  • the control edge 86 to the recess 84 has an overlap, which is indicated in Figure 2 by the reference numeral 88.
  • the hydraulic connection between the high-pressure fuel line 42 and recess 84 is interrupted in this position of the piston 72.
  • the second collar 76 is wider than the recess 84, so that the piston 72 is always performed regardless of its position in the bore 70 through the first collar 74 and the second collar 76 in the bore 70.
  • a sealing cone 90 is integrally formed on the piston 72.
  • the sealing cone 90 together with a sealing seat 92 formed in the housing 58, separates the recess 84 from a spring chamber 94, which in turn hydraulically communicates with the low pressure line 22.
  • the sealing cone 90 and the sealing seat 92 serve to maintain the pressure in the high-pressure region 14 when the internal combustion engine is switched off.
  • a compression spring 96 is arranged, which is supported at one end against the housing 58 and the other end against the piston 72 and this presses with its sealing cone 90 in the sealing seat 92.
  • the pressure in the delivery chamber 60 increases and the check valve 44 opens, the pressure in the high-pressure fuel line 42 also increases and fuel flows from the high-pressure fuel line 42 into the compensation chamber 82 and the pressure in the compensation chamber 82 increases delayed in time.
  • the delay of the pressure rise in the compensation chamber 82 is caused by the throttling action of the annular gap between the first collar 74 and bore 70.
  • the overlap 88 and the volume of the compensation chamber 88 are designed so that during normal operation of the fuel system 10, the pressure pulsations in the high-pressure region 14 of the fuel system 10 so far be degraded that they have no negative impact on the operation of the fuel system 10 more.
  • the overlap 88 and the volume of the balance chamber 82 are designed so that during normal operation of the fuel system 10, the hydraulic connection between the high-pressure fuel line 42 and low-pressure fuel line 22 is not released. This means that the efficiency of the fuel system 10 remains virtually unchanged during normal operation as a result of the use of the pressure limiting device 56 according to the invention.
  • the fuel pump 30 (see Fig. 1) always delivers the full flow, the pressure in the high pressure region 14 and thus also in the high-pressure fuel line 42 via a - compared with the pressure pulsations during normal operation - long period strongly.
  • the volume of the compensation chamber 82 increases so much that the control edge 86 releases the hydraulic connection between the annular groove 78 and recess 84 and fuel flows from the high-pressure fuel line 42 via the spring chamber 94 in the low-pressure fuel line 22, so that a Degradation of prevailing in the high-pressure fuel line 42 overpressure takes place.
  • the high pressure area 14 of the fuel system 10 is effectively protected against impermissibly high pressures in case of disturbances in flow control.
  • the pressure rise in the high-pressure fuel line 42 and the fuel rail 46 is lower, which is qualitatively represented in the figure 3 by the solid line.
  • the check valve 44 closes and the spring 96 pushes the piston 72 in the direction of the compensation chamber 82 and thereby reduces the volume of the compensation chamber 82 to its original value.
  • the fuel displaced from the compensation chamber 82 flows via the annular groove 78 into the high-pressure fuel line 42 and thus contributes to the pressure maintenance in the high-pressure region 14 of the fuel system 10.
  • the overlap 88 between the control edge 86 and recess 44, the bias and spring rate of the spring 96 and the volume of the compensation chamber 82 and the throttling action between the first collar 74 and bore 70 must, as already mentioned, be matched to one another that at a delivery stroke of the second Fuel pump 30 during proper operation of the fuel system 10, the control edge 86, the recess 84 is not released and thus no fuel from the high-pressure region 14 flows into the low-pressure region 12.
  • FIG. 4 shows a further exemplary embodiment of a pressure limiting device 56 according to the invention.
  • the same components are provided with the same reference numerals and it is the case with respect to Figure 2 said accordingly.
  • the essential difference from the first exemplary embodiment according to FIG. 2 is that the piston 72 has a third collar 100 below the first collar 74.
  • the balance chamber 82 is present in this embodiment between the first collar 74 and the third collar 100 and is an annular space whose volume increases as the piston 72 moves in the direction of the spring 96.
  • the collar 80 of the bore 70 and the third collar 100 define a space 102 which communicates hydraulically via a bore 104 with the spring chamber 94 and thus with the low-pressure fuel line 22.
  • the force acting on the end faces of the piston 72 hydraulic forces are compensated.
  • FIG. 5 shows a third exemplary embodiment of a pressure limiting device 56 according to the invention.
  • the piston 72 has no sealing cone 90.
  • the piston 72 rests with its third collar 100 on a shoulder 106 of the housing 58 and thus defines the maximum overlap 88 of the control edge 86.
  • the third embodiment of an inventive Pressure limiting device 56 is preferably used in fuel systems 10, in which after stopping the engine or in overrun mode, the pressure in the high-pressure region 14 is lowered via a defined leakage.
  • the opening pressure of the pressure limiting device 56 is as independent as possible from the flow through the high pressure fuel line 42.

Landscapes

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

Claims (9)

  1. Dispositif de limitation de pression (56) pour un système d'alimentation en carburant d'un moteur à combustion interne, le dispositif de limitation de pression (56) étant disposé entre une conduite de carburant haute pression (42) et une conduite de carburant basse pression (22), comportant un carter (58), un piston (72) passant dans un alésage (70) du carter (58), qui, à partir d'une certaine pression différentielle entre la conduite de carburant (42) et la conduite de carburant basse pression (22), les relie hydrauliquement, l'alésage (70) et le piston (72) délimitant une chambre de compensation (82) et comportant un papillon entre la conduite de carburant haute pression (42) et la chambre de compensation (82), le piston (72) présentant une première collerette (74) qui agit comme un papillon entre la chambre de compensation (82) et la conduite de carburant haute pression (42),
    caractérisé en ce que
    le piston (72) présente une deuxième collerette (76) avec sur la deuxième collerette (76) une rampe hélicoïdale (86), la rampe hélicoïdale (86) interagit avec un évidement (84) de l'alésage (70) pour que, lorsque le dispositif de limitation de pression (56) est fermé, la liaison hydraulique entre la conduite de carburant haute pression (42) et la conduite de carburant basse pression (22) soit interrompue, et le dispositif de limitation de pression (56) ne s'ouvre que lorsque la chambre de compensation (82) a atteint un volume minimal prédéfini, ce volume minimal dépendant de la superposition (88) de la rampe hélicoïdale (86) dans l'alésage (70) lorsque le dispositif de limitation de pression (56) est fermé.
  2. Dispositif de limitation de pression (56) selon la revendication 1,
    caractérisé en ce qu'
    entre le piston (72) et le carter (58), un ressort (96) sollicite le piston (72) dans le sens de la position de fermeture.
  3. Dispositif de limitation de pression (56) selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le piston (72) présente un cône d'étanchéité (90) sur son extrémité opposée à la première collerette (74), et le cône d'étanchéité (90) repose sur un siège d'étanchéité (92) du carter (58) lorsque le dispositif de limitation de pression (56) est fermé.
  4. Dispositif de limitation de pression (56) selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    dans le carter (58), il y a un décrochement (106) et le piston (72) repose contre le décrochement (106) lorsque le dispositif de limitation de pression (56) est fermé.
  5. Dispositif de limitation de pression (56) selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le piston (72) présente une troisième collerette (100), la chambre de compensation (82) est limitée en plus par la troisième collerette (10) et le diamètre (D3) de la troisième collerette (100) est inférieur au diamètre (D1) de la première collerette (74).
  6. Dispositif de limitation de pression (56) selon la revendication 5,
    caractérisé en ce que
    la troisième collerette (100), avec l'alésage (70), délimite un espace (102), et cet espace (102) est en liaison hydraulique, au moins indirectement, avec une zone basse pression (12) du système d'alimentation en carburant (10).
  7. Système d'alimentation en carburant (10) pour fournir du carburant (18) à un moteur à combustion interne, comportant un réservoir (16), une première pompe à carburant (20) reliée côté entrée au réservoir (16), une deuxième pompe à carburant (30) reliée côté entrée à la première pompe à carburant (20) et un dispositif de limitation de pression (56) qui délimite la pression dans une liaison de carburant (42, 46) côté sortie de la deuxième pompe à carburant (30), caractérisé en ce que
    le dispositif de limitation de pression (56) est configuré selon l'une quelconque des revendications 1 à 6.
  8. Système d'alimentation en carburant (10) selon la revendication 7,
    caractérisé en ce que
    la deuxième pompe à carburant comporte une pompe à piston monocylindre (30).
  9. Système d'alimentation en carburant (10) selon l'une quelconque des revendications 7 ou 8,
    caractérisé en ce que
    le dispositif de limitation de pression (56) est monté sur la deuxième pompe à carburant (30), de préférence intégré dans celui-ci.
EP20030003826 2002-09-27 2003-02-20 Dispositif de limitation de pression et système de combustible avec tel dispositif de limitation de pression Expired - Lifetime EP1403509B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2002145084 DE10245084A1 (de) 2002-09-27 2002-09-27 Druckbegrenzungseinrichtung sowie Kraftstoffsystem mit einer solchen Druckbegrenzungseinrichtung
DE10245084 2002-09-27

Publications (3)

Publication Number Publication Date
EP1403509A2 EP1403509A2 (fr) 2004-03-31
EP1403509A3 EP1403509A3 (fr) 2005-01-05
EP1403509B1 true EP1403509B1 (fr) 2006-08-09

Family

ID=31969645

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20030003826 Expired - Lifetime EP1403509B1 (fr) 2002-09-27 2003-02-20 Dispositif de limitation de pression et système de combustible avec tel dispositif de limitation de pression

Country Status (3)

Country Link
EP (1) EP1403509B1 (fr)
JP (1) JP2004116526A (fr)
DE (2) DE10245084A1 (fr)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005062548A1 (de) * 2005-12-27 2007-07-05 Robert Bosch Gmbh Common-Rail-Kraftstoffsystem
US20080022974A1 (en) * 2006-07-28 2008-01-31 Caterpillar Inc. Multi-stage relief valve having different opening pressures
ITMI20072219A1 (it) 2007-11-23 2009-05-24 Bosch Gmbh Robert Valvola di sovrappressione e pompa di alta pressione comprendente tale valvola di sovrappressione
DE102008014250A1 (de) * 2008-03-13 2009-09-17 Man Diesel Se Kraftstoffversorgungsanlage einer Brennkraftmaschine
DE102008020329A1 (de) * 2008-04-23 2009-10-29 Continental Automotive Gmbh Vorrichtung und Verfahren zur Kraftstoffzuteilung sowie damit ausgestattete Brennkraftmaschine
EP2287462B1 (fr) * 2009-07-08 2012-04-18 Delphi Technologies Holding S.à.r.l. Unité de pompe
US8240291B2 (en) 2009-10-23 2012-08-14 Caterpillar Inc. Pressure relief valve
IT1400581B1 (it) * 2010-06-18 2013-06-14 Bosch Gmbh Robert Valvola di lubrificazione e di troppopieno per un impianto di alimentazione del carburante da un serbatoio ad un motore a combustione interna e detto impianto comprendente detta valvola.
DE102010064216A1 (de) * 2010-12-27 2012-06-28 Robert Bosch Gmbh Pumpe, insbesondere eines Kraftstoffeinspritzsystems
DE102011003396A1 (de) * 2011-01-31 2012-08-02 Continental Automotive Gmbh Pumpeneinheit für eine Hochdruckpumpe
DE102013212553A1 (de) * 2013-06-28 2014-12-31 Robert Bosch Gmbh Hydraulische Baugruppe für ein Kraftstoffsystem einer Brennkraftmaschine
DE102015205114B4 (de) 2015-03-20 2022-08-04 Volkswagen Aktiengesellschaft Verfahren zur Vermeidung zu hoher Systemdrücke in Common-Rail-Systemen
US10443595B2 (en) * 2015-04-20 2019-10-15 Hitachi, Ltd. Automotive fuel pump
CN108386357B (zh) * 2018-04-18 2024-05-28 北京燕都碧城科技有限公司 一种单螺杆压缩机防液击装置
CN111608833B (zh) * 2020-05-07 2021-08-06 一汽解放汽车有限公司 一种用于平衡共轨系统压力的安全限压阀
KR102540496B1 (ko) * 2021-08-30 2023-06-07 주식회사 현대케피코 맥동 체적 확장형 고압펌프

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5558068A (en) * 1994-05-31 1996-09-24 Zexel Corporation Solenoid valve unit for fuel injection apparatus
JPH10299925A (ja) * 1997-04-23 1998-11-13 Zexel Corp 圧力制御弁
JP3455419B2 (ja) * 1998-04-15 2003-10-14 三菱電機株式会社 高圧アキュムレータのダイヤフラムストッパ構造
DE10059425A1 (de) * 2000-11-30 2002-06-06 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Brennkraftmaschinen, insbesondere Dieselmotoren
DE10118936A1 (de) * 2001-04-18 2002-11-07 Bosch Gmbh Robert Druckbegrenzungseinrichtung sowie Kraftstoffsystem mit einer solchen Druckbegrenzungseinrichtung

Also Published As

Publication number Publication date
DE50304554D1 (de) 2006-09-21
EP1403509A2 (fr) 2004-03-31
JP2004116526A (ja) 2004-04-15
EP1403509A3 (fr) 2005-01-05
DE10245084A1 (de) 2004-04-01

Similar Documents

Publication Publication Date Title
EP1411238B1 (fr) Soupape de limitation de pression pour un système d'injection de carburant
DE102004013307B4 (de) Kraftstoffhochdruckpumpe mit einem Druckbegrenzungsventil
EP1403509B1 (fr) Dispositif de limitation de pression et système de combustible avec tel dispositif de limitation de pression
DE10327411B4 (de) Druckbegrenzungsventil sowie Kraftstoffsystem mit einem solchen Druckbegrenzungsventil
EP2670971B1 (fr) Unité pompe pour une pompe haute pression
DE102005033638A1 (de) Kraftstoff-Fördereinrichtung, insbesondere für eine Brennkraftmaschine
DE10115324A1 (de) Kraftstoffsystem
DE19541507A1 (de) Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
WO2002084105A1 (fr) Pompe a carburant haute pression destinee au systeme a carburant d'un moteur a combustion interne a injection directe, systeme a carburant et moteur a combustion interne
EP2932086A1 (fr) Ensemble pompe et système pour véhicule automobile
EP1251266B1 (fr) Dispositif de limitation de pression et système de combustible avec tel dispositif de limitation de pression
EP1298379B1 (fr) Dispositif pour amortir les pulsations de pression dans un système à fluide, en particulier dans un système à carburant d'un moteur à combustion, et système à carburant
WO2007012510A1 (fr) Systeme d'injection de carburant pour moteur a combustion interne a injection directe de carburant
EP1395753B1 (fr) Pompe haute pression pour un systeme de carburant d'un moteur a combustion interne
EP2156050B1 (fr) Système d'amplification de pression pour au moins un injecteur de carburant
EP1262658B1 (fr) Système de combustible pour amener du combustible pour un moteur à combustion interne
EP1338787B1 (fr) Système hydraulique de décharge de pression pour un dispositif d'injection de carburant
DE19945785B4 (de) Kraftstoffeinspritzsystem für Brennkraftmaschinen und Verfahren zum Einspritzen von Kraftstoff in den Brennraum einer Brennkraftmaschine
WO2023052039A1 (fr) Pompe à piston et amortisseur de pulsations de pression
DE102008045193A1 (de) Kraftstoffversorgungsanlage einer Brennkraftmaschine
WO2004027250A1 (fr) Dispositif d'injection de carburant pour moteur à combustion interne
DE102020206034A1 (de) Kraftstoffhochdruckpumpe
DE102011089626A1 (de) Druckbegrenzungsventil für eine Kraftstofffördereinrichtung sowie Kraftstofffördereinrichtung
DE102008041393A1 (de) Kraftstoffsystem für eine Brennkraftmaschine
DE10210300B4 (de) Pumpenelement für eine Hochdruckpumpe und Hochdruckpumpe mit steuerbarer Fördermenge

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

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT SE SI SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO

RIC1 Information provided on ipc code assigned before grant

Ipc: 7F 02M 63/02 B

Ipc: 7F 02M 55/04 B

Ipc: 7F 02M 59/46 A

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT SE SI SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO

17P Request for examination filed

Effective date: 20050705

AKX Designation fees paid

Designated state(s): DE FR GB IT

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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): DE FR GB IT

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20060809

Ref country code: GB

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: 20060809

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 50304554

Country of ref document: DE

Date of ref document: 20060921

Kind code of ref document: P

GBV Gb: ep patent (uk) treated as always having been void in accordance with gb section 77(7)/1977 [no translation filed]

Effective date: 20060809

EN Fr: translation not filed
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

26N No opposition filed

Effective date: 20070510

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070511

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060809

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

Ref country code: DE

Payment date: 20120423

Year of fee payment: 10

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50304554

Country of ref document: DE

Effective date: 20130903

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

Ref country code: DE

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

Effective date: 20130903