EP2156049B1 - Multiplicateur de pression à accumulateur de pression intégré - Google Patents

Multiplicateur de pression à accumulateur de pression intégré Download PDF

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Publication number
EP2156049B1
EP2156049B1 EP08759411.5A EP08759411A EP2156049B1 EP 2156049 B1 EP2156049 B1 EP 2156049B1 EP 08759411 A EP08759411 A EP 08759411A EP 2156049 B1 EP2156049 B1 EP 2156049B1
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EP
European Patent Office
Prior art keywords
pressure
amplifier unit
reservoir
injection system
unit
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
EP08759411.5A
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German (de)
English (en)
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EP2156049A1 (fr
Inventor
Dominik Kuhnke
Dirk Vahle
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2156049A1 publication Critical patent/EP2156049A1/fr
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Publication of EP2156049B1 publication Critical patent/EP2156049B1/fr
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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
    • 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
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/08—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by two or more pumping elements with conjoint outlet or several pumping elements feeding one engine cylinder
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • EP 0 711 914 A1 refers to a pressure-controlled fuel injection system in which fuel is compressed by means of a high-pressure pump to a first high fuel pressure of about 1200 and stored in a first pressure accumulator. Furthermore, the high-pressure fuel is also conveyed into a second pressure accumulator, in which by controlling its fuel supply by means of a 2/2-way valve, a second high fuel pressure of about 400 bar is maintained. Via a valve control unit, either the lower or the higher fuel pressure is conducted into the nozzle chamber of an injector. There, a spring-loaded valve body is lifted from its valve seat by the pressure, so that fuel can escape from the nozzle opening into the combustion chamber.
  • a disadvantage of this known fuel injection system is the fact that first of all the entire fuel must first be compressed to the higher pressure level in order then to relieve some of the fuel back to the lower pressure level.
  • the high-pressure pump since it is driven by the camshaft of the engine, permanently in operation, even if the desired pressure in the respective pressure accumulator is already established. This permanent high pressure generation and the subsequent relief to the low pressure level counteract a better efficiency.
  • the high-pressure fuel pumps used in the field of self-igniting internal combustion engines are currently able to build up pressures of up to about 2200 bar.
  • Exceeding pressures are possible either with two-stage high-pressure pumps or with additional pressure amplifiers outside or inside the fuel injectors.
  • Two-stage high pressure pumps require a much larger space and are therefore not compatible with the current systems.
  • the mechanical stress on the part of the pump development is classified as critical.
  • Internal and external pressure amplifiers are currently used only as local pressure intensifiers for individual injectors used, ie per injector is a pressure booster in use.
  • Such a central pressure booster is for example off EP 1 125 046 B1 known.
  • a pressure intensifier which represents a single separate module, and corresponds approximately to the size of a commonly used pressure accumulator and also assumes its function.
  • a common high-pressure pump is currently a common pressure level in the order of about 2000 bar, which is referred to below as the medium pressure.
  • the pressure intensifier proposed according to the invention advantageously has at least two pistons for achieving the pressure boost, which are operated alternately and thus a continuous delivery at high pressure, i. at a pressure level of> 2500 bar.
  • the delivered quantity can therefore be made available to the individual NEN fuel injectors even without large high-pressure accumulator, since a pressure drop can be compensated by injector-side removal largely by immediate Nachêt.
  • FIG. 1 a first embodiment of the high-pressure injection system can be seen.
  • the high-pressure injection system 10 as shown in FIG. 1
  • a high-pressure pump 14 is provided in addition to a tank 12, a high-pressure pump 14 is provided.
  • the high-pressure pump acts on a pressure booster unit 16 which, according to this first embodiment, comprises an intermediate rail 18 and an optionally activatable pressure booster 24.
  • the pressure intensifier unit 16 in turn acts on an externally arranged high pressure accumulator 20, which in turn has a number of high pressure ports 26.
  • FIG. 2 shows a second embodiment of the present invention proposed high-pressure injection system, in which, in contrast to the representation according to FIG. 1 the pressure booster unit 16 comprises the intermediate rail 18, the optionally activatable pressure booster 24 and the high-pressure accumulator 20 as an integrated component.
  • the high pressure ports 26 are provided on the pressure booster unit 16 in a number corresponding to the number of fuel injectors 22 to be supplied with fuel.
  • the leakage or control quantity is returned via the lines indicated by dashed lines both from the pressure intensifier unit 16 and from the at least one fuel injector 22 to the tank 12 of the high-pressure accumulator injection system 10.
  • FIG. 3 shows the schematic structure of the booster, of which two in the in FIGS. 1 and 2 illustrated pressure booster units are installed.
  • a pressure amplifier 24, of which at least one is installed in a pressure amplification unit 16 comprises a base body 30.
  • pressure booster piston 32, 33 In the base body 30 are pressure booster piston 32, 33.
  • Pressure booster units 16 shown each comprise two pressure boosters 24.
  • the pressure booster piston 32 In the main body 30 of the pressure booster piston 32 is arranged, which has a first piston part 34 in a larger diameter and a second piston part 36 in a smaller diameter. On the first pressure piston part 34 is an annular collar 38, on which a return spring 40 is supported. The return spring 40 is further supported on an annular surface of a piston guide body 42.
  • pressure booster 24 In the main body 30 of the in FIG. 3 illustrated pressure booster 24 is a high pressure valve 44 and a filling valve 46. These two valves 44, 46 are preferred designed as check valves.
  • the high-pressure valve 44 is located in a storage supply line 54 which communicates with a high-pressure chamber 60.
  • the high-pressure chamber 60 is limited on the one hand by the piston guide body 42 and on the other hand by a high-pressure surface 64.
  • the filling valve 46 is located in a hydraulic line, which, as shown in FIG. 3 connects a control chamber 62 via a switching valve 50 and a bypass with a storage volume 58. Furthermore, in the main body 30 of the in FIG. 3 illustrated pressure intensifier 24, the switching valve 50 is integrated, which may be formed, for example, operated as a solenoid valve switching valve, as a 3/2-way valve.
  • a pressure booster 56 which is located downstream of the switching valve 50, the storage supply line 54 with integrated high-pressure valve 44, which is the high-pressure accumulator 20 according to the system overviews in FIGS. 1 and 2 extends as well as a pressure booster inlet 52, via the in the Figures 1 and 2 shown high-pressure pump 14 is acted upon.
  • the storage volume 58 which is also referred to as a medium-pressure accumulator, communicates via a bypass 68 with the control chamber 62.
  • a medium pressure designated here by the high pressure pump 14 via the pressure booster inlet 52 in the one or more parts trained storage volume 58 and further promoted via the filling valve 46 and the high pressure valve 44 directly to the storage feed 54. From there it enters either an external high-pressure accumulator 20 - as in FIG. 1 represented - or via the internal high-pressure accumulator - to the fuel injectors 22, as in FIG. 2 shown.
  • the pressure booster 24 is operated according to the schematic representation in Figure 3 in the bypass mode in which no pressure boosting is necessary and therefore no appreciable efficiency losses occur. In bypass operation is simultaneously by all available pressure booster 24 a pressure booster unit 16 - as in the Figures 1 and 2 presented - promoted.
  • the pressure amplifiers 24 of the pressure booster unit 16 can be used alternately or simultaneously.
  • the corresponding switching valve 50 which is preferably a 3/2-way valve, is switched.
  • the control space 62 of the pressure intensifier piston 32 becomes due to the activation the switching valve 50 is connected to the pressure booster return 56 and therefore depressurized. Due to this, the pressure in the high-pressure chamber 60 of the pressure intensifier 24 increases until an equilibrium of forces has been established between the high pressure on the high-pressure surface 64 of the high-pressure piston 32 and the force generated by the return spring 40 and the mean pressure at the medium-pressure surface 66 of the pressure intensifier pistons 32, 33 ,
  • the transmission ratio i defined by the two pressure surfaces 64 and 66 preferably corresponds to the quotient of the desired maximum pressure required at the storage supply line 54 and the high-pressure pump delivery pressure.
  • the high pressure amount is fed back through the high pressure valve 44 when at the high pressure port, i. in the storage supply line 54, the pressure drops due to quantity removal.
  • the connection to the storage volume 58 is closed.
  • control chamber 62 of the high pressure piston 32 When deactivating the switching valve 50, the control chamber 62 of the high pressure piston 32 is connected to the storage volume 58, whereby the pressure in the control chamber 62 increases and the pressure booster piston 32, 33 is positioned at hydraulic force balance by the spring force of the return spring 34 at its stop limit 48.
  • each of a pressure intensifier 24 associated switching valves 50 is synchronized with the injections, so that per cylinder of fuel to be supplied internal combustion engine and each 720 ° crankshaft angle in a four-stroke internal combustion engine, a delivery stroke of the booster 24 takes place. Accordingly, it is ensured that the reset time of each pressure booster piston 32 or 33 of the at least one pressure booster 24 is sufficiently short in order to be able to deliver at every second injection at a pressure booster unit 16 equipped with two pressure booster 24.
  • the pressure booster unit 16 according to the representations of Figures 1 and 2 In addition to the buffer (Zwischenrail) preferably comprises two pressure booster 24 and optionally - as in the embodiment according to FIG. 2 illustrated - a high-pressure accumulator 20 (high-pressure rail), which is integrated in the pressure booster unit 16.
  • FIGS. 4 and 5 are various embodiments of pressure booster units incorporated in the Figures 1 and 2 are shown only schematically reproduced.
  • the buffer 18 (Zwischenrail) does not necessarily represent a separate component, but is divided into a storage volume 38 (see FIG. 3 ) preferably two built in a pressure booster unit 16 pressure booster 24.
  • the pressure booster unit 16 may comprise a U-shaped central body 94 having storage pots 92, in which the individual pressure booster 24 of the booster unit 16 are embedded. On one end face of the central body 94 is in each case a first switching unit 84 and a second switching unit 86, each formed as a 3/2-way valve 50. Side of the U-shaped central body 94 of the pressure booster unit 16 ports 82 are executed, in which there around the in FIG. 3 represented connections 82, namely pressure booster inlet 52, storage supply line 54 and pressure booster 56 return. At the pressure booster inlet 52, cf. also reference numeral 98, for example, the in FIG. 1 shown high pressure pump 14 connected, see. Position 98 in FIG. 1 , Furthermore, the connections on the 82 U-shaped central body 94 of the pressure booster unit 16 as shown in FIG FIG. 4 , High Pressure Connections 100, for example, to the in FIG. 1 lead described high-pressure accumulator 20 lead.
  • FIG. 4 From the illustration according to FIG. 4 also shows that the two pressure amplifiers 24, of which the pressure booster 24, the pressure booster piston 32 and the pressure booster 24 has the pressure booster piston 33, are arranged parallel to each other.
  • the pressure booster 24 with pressure booster piston 32 is inactive, the other pressure booster 24 with pressure booster piston 33 is active.
  • At the central body 94 of the pressure booster unit 16 is a pressure control valve 102 and a pressure sensor 104.
  • the structure of in the embodiment according to FIG. 4 illustrated pressure amplifier 24 substantially corresponds to the representation of the pressure booster 24 according to FIG. 3 ,
  • the pressure booster unit 16 in the in FIG. 5 illustrated embodiment also has ports 82, each representing the pressure booster inlet 52 and the memory feed 54.
  • the pressure booster return is not shown.
  • each pressure booster units 16 are shown, which have a reduced overall length, which is achieved due to the formed in a U-shaped one-piece central body 94. Furthermore, in the embodiments according to the FIGS. 4 and 5 Connection possibilities for the pressure sensor 104 or the one shown there schematically Pressure control valve 102 provided on the end face of the integrally formed central body.
  • FIG. 4 an embodiment of the first embodiment according to FIG. 1 represents shows FIG. 5 an embodiment of the second embodiment according to FIG. 2 with integrated high pressure accumulator 20.
  • the pressure booster unit 16 has a very compact design, which is achieved by the integrally formed central body 94.
  • the pressure booster unit 16 according to the schematic representation in the FIG. 1 , two pressure storage pots 92 are provided, which are placed side by side.
  • the two pressure accumulator heads 92 are located opposite the one-piece central body 94, the first switching unit 84 and the second switching unit 86, which may be formed, for example, as solenoid valves, see.
  • Position 50 in FIG. 3
  • FIG. 5 From the illustration according to FIG. 5 is an embodiment of the pressure intensifier unit 16 with integrated high-pressure accumulator according to FIG. 2 out.
  • the representation according to FIG. 5 is also a pressure amplifier unit 16 with a here also analogous to FIG. 4 to take one-piece formed central body 94.
  • the two pressure storage pots 92 and the first switching unit 84 and the second switching unit 86 are adjacent to each other lying on the one-piece central body 94.
  • reference numeral 98 denotes a pump port analogous to reference numeral 52 in the embodiment according to FIG. 3 , which denotes the pressure booster unit inlet.
  • the reference numeral 100 denotes a high pressure port, analogous to reference numeral 54 in the embodiment according to FIG. 3 , there are the fuel injectors or high pressure lines that run to these, connected.
  • the illustrated embodiment of the pressure booster unit 16 is one with which, for example, a 4-cylinder internal combustion engine can be supplied with under system pressure fuel.
  • On the side of the one-piece central body 94 are the connections 82. Together with the side of the central body 94 arranged high-pressure connections 82 and 100 can be connected to the in FIG. 5 For example, 4 fuel injectors or 4 high-pressure lines leading to 4 fuel injectors shown connected.
  • FIG. 6 shows an alternating operation of two pressure booster piston with synchronous injection.
  • FIG. 6 shows that a piston stroke h of a first pressure booster piston 32 and a second - indicated by dashed lines - pressure booster piston 33 is plotted over time.
  • Reference numeral 22 represents the activation of each fuel injector 22, wherein the fuel injectors 22 have, for example, an in each case ramp-shaped injection characteristic, while the fuel is introduced into the respective cylinders of the internal combustion engine. In addition to a ramp-shaped injection characteristic, multiple injections can also be run, or any further injection strategies can be implemented. As shown in the illustration FIG. 6 As can be seen, respective strokes 112 and 114 may overlap each other slightly in alternate operation 110 of the intensifier pistons 32,33.
  • FIG. 6 indicated by reference numeral 110 alternately operation of the pressure booster unit 16 assumes that the schematic in the Figures 1 and 2 illustrated pressure booster unit 16 two pressure booster 24 as shown in FIG. 3 includes.
  • the representation according to FIG. 7 can be a synchronous operation of a pressure booster unit 16 with two pressure amplifiers 24 refer.
  • the first stroke 112 and the second stroke 114 shows that in this case the first high-pressure piston 32 and the second - dashed lines indicated - high-pressure piston 33 are operated synchronously. In this case fall respectively the first strokes 112 and the second strokes 114 together.
  • the flow rate can be increased and the pressure drop in the high pressure accumulator 20 of the high pressure injection system 10 according to the schematic overview drawings in the Figures 1 and 2 further reduce.
  • the individual injection processes preferably take place synchronously with the delivery - as shown in the illustration FIG.
  • the injections can be made between the individual intensifier strokes 112 and 114 of the first pressure intensifier piston 32 and the second pressure intensifier piston 33, which shows an alternate operation of the pressure booster piston in asynchronous injection.
  • an after-delivery may be provided in the pauses between the individual injection processes, as indicated in the illustration according to FIG.
  • a further hub 114 may partially, completely or not coincide with an injection. Characteristic in this context is that the first hub 112 does not coincide with the injection, but takes place in an injection pause.
  • the pressure booster unit 16 according to the schematic representation in the Figures 1 and 2 be hydraulically connected in various ways with the fuel injectors.
  • Figure 9.1 shows that the high-pressure pump 14, the pressure booster unit 16 with high-pressure fuel at a pressure level of about 2000 applied bar.
  • the pressure booster unit 16 in turn pressurizes the externally arranged high-pressure accumulator 20 with a pressure which is increased in accordance with the transmission ratio i of the two pressure booster 24, wherein it is an externally arranged high-pressure accumulator 20 according to the illustration 9.1. From this, in each case individual high-pressure lines 140 extend to the fuel injectors 22.
  • These supply in accordance with this piping variant Figure 9.1 a six-cylinder combustion engine.
  • FIG. 9.2 The representation according to FIG. 9.2 is to be taken in view of the variant according to 9.1 slightly modified casing variant.
  • the pressure booster unit 16 which in turn acts on the external high-pressure accumulator 20.
  • Between the individual fuel injectors 22 according to FIG. 9.2 runs through a single connecting pieces 144 indicated ring line 142.
  • the ring line 142 for connecting the fuel injectors 22 has a significant hydraulic advantage, because the storage volume in the fuel injectors 22 at low spatial distances reduces pressure drops and resulting pressure oscillations.
  • Rail disposed externally with respect to the pressure intensifier unit 16, that is to say the high-pressure accumulator 20 is dispensed with can, in addition, be provided via the ring line 142 in comparison to the embodiment variant according to FIG Figure 9.3 the number of necessary connections to the pressure booster unit 16 are reduced, cf. such as in the embodiments according to Figure 9.4 and 9.5 ,
  • FIG. 9.3 illustrated embodiment of the piping scheme are at the there schematically indicated pressure booster unit 16 six single high-pressure lines 140 to connect to the individual fuel injectors 22, while in the embodiment according to 9.3 facing embodiments according to the Figures 9.4 or 9.5 are connected to the pressure booster units 16 shown there only two single high-pressure lines 140, since the fuel injectors 22 are in turn connected to each other via connecting pieces 144 within the loop 142.
  • the high-pressure accumulator 20 is located externally with respect to the pressure booster unit 16 and acts on a connector 144 of the ring line 142 between the fuel injectors 22 directly.

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

Claims (14)

  1. Système d'injection à haute pression (10), en particulier pour des moteurs à combustion interne à autoallumage, comprenant au moins une pompe à haute pression (14) et un accumulateur haute pression (20) par le biais desquels au moins un injecteur de carburant (22) est alimenté en carburant sous pression, le système d'injection à haute pression (10) comportant au moins une unité d'amplificateurs de pression (16),
    caractérisé en ce que
    l'unité d'amplificateurs de pression (16) comprend au moins deux amplificateurs de pression (24) présentant respectivement un piston haute pression (32, 33), lesquels pistons peuvent fonctionner indépendamment les uns des autres,
    soit l'unité d'amplificateurs de pression (16) sollicitant l'accumulateur haute pression (20) et l'accumulateur haute pression (20) étant disposé à l'extérieur et comprenant des raccords haute pression (26),
    soit l'accumulateur haute pression (20) étant réalisé sous forme de composant intégré de l'unité d'amplificateurs de pression (16), laquelle comprend des raccords haute pression (26),
    le nombre des raccords haute pression (26) correspondant au nombre des injecteurs de carburant (22) devant être alimentés.
  2. Système d'injection à haute pression (10) selon la revendication 1, caractérisé en ce que l'unité d'amplificateurs de pression (16) comporte un accumulateur intermédiaire (18) en tant que composant intégré.
  3. Système d'injection à haute pression (10) selon la revendication 1, caractérisé en ce que l'unité d'amplificateurs de pression (16) comporte un accumulateur intermédiaire (18) et un accumulateur haute pression (20).
  4. Système d'injection à haute pression (10) selon la revendication 1, caractérisé en ce que l'unité d'amplificateurs de pression (16) est réalisée sous forme de construction allongée (80) et au moins une unité de commutation (84) est reçue du côté frontal.
  5. Système d'injection à haute pression (10) selon la revendication 1, caractérisé en ce que l'unité d'amplificateurs de pression (16) présente des positions latérales de montage (90) pour au moins une unité de commutation (84, 86) et une tête d'accumulateur de pression (92) est respectivement prévue du côté frontal sur l'unité d'amplificateurs de pression (60).
  6. Système d'injection à haute pression (10) selon la revendication 1, caractérisé en ce que l'unité d'amplificateurs de pression (16) comporte un corps central (94) en une seule partie, sur lequel sont prévus des raccords (82) qui comportent des raccords de pompe (52, 58), des raccords haute pression (54) pour des accumulateurs de pression (20) ainsi que des raccords haute pression (100) pour le raccordement d'injecteurs de carburant (22).
  7. Système d'injection à accumulateur haute pression (10) selon la revendication 1, caractérisé en ce que pour des pressions d'injection en dessous de la pression maximale de la pompe à haute pression (14), le volume nécessaire est acheminé jusqu'aux injecteurs de carburant (22) sans activation de l'unité d'amplificateurs de pression (16).
  8. Système d'injection à accumulateur haute pression (10) selon la revendication 1, caractérisé en ce que l'unité d'amplificateurs de pression (16) comporte au moins une soupape de commutation (50) qui est associée à l'au moins un accumulateur de pression (24) et dans laquelle l'au moins une soupape de commutation (50) est synchronisée avec les opérations d'injection de telle sorte qu'une course de refoulement (112, 114) de l'au moins un amplificateur de pression (24) ait lieu par cylindre et par angle de vilebrequin de 720°.
  9. Système d'injection à accumulateur haute pression (10) selon la revendication 1, caractérisé en ce que l'unité d'amplificateurs de pression (16) sollicite l'accumulateur haute pression (20) disposé à l'extérieur, lequel sollicite quant à lui, avec du carburant haute pression, les injecteurs de carburant (22) qui sont reliés les uns aux autres par le biais d'une conduite annulaire (142, 144), ou l'accumulateur haute pression (20) sollicite la conduite annulaire (142) reliant les injecteurs de carburant (22) les uns aux autres.
  10. Système d'injection à accumulateur haute pression (10) selon la revendication 1, caractérisé en ce que l'unité d'amplificateurs de pression (16) est sollicitée par la pompe à haute pression (14) et sollicite les injecteurs de carburant (14) qui sont en liaison hydraulique les uns avec les autres par le biais d'une conduite annulaire (142, 144).
  11. Système d'injection à accumulateur haute pression (10) selon la revendication 1, caractérisé en ce qu'au moyen d'un chevauchement au moins partiel de déplacements de course de refoulement (112, 114) des pistons d'amplificateur de pression (32, 33), le débit de refoulement de l'unité d'amplificateurs de pression (16) est augmenté et une baisse de pression dans l'accumulateur haute pression (20) est réduite.
  12. Système d'injection à accumulateur haute pression (10) selon la revendication 1, caractérisé en ce que des injections (122) ont lieu de manière synchrone (120) au fonctionnement de l'unité d'amplificateurs de pression (16).
  13. Système d'injection à accumulateur haute pression (10) selon la revendication 1, caractérisé en ce que l'injection (122) a lieu de manière asynchrone (130) au fonctionnement de l'unité d'amplificateurs de pression (16).
  14. Système d'injection à accumulateur haute pression (10) selon la revendication 11, caractérisé en ce qu'un post-refoulement à haute pression de l'unité d'amplificateurs de pression (16) pendant l'injection (122) réduit la perte de pression dans l'accumulateur haute pression (20) par extraction de volume.
EP08759411.5A 2007-05-15 2008-05-05 Multiplicateur de pression à accumulateur de pression intégré Not-in-force EP2156049B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007022857A DE102007022857A1 (de) 2007-05-15 2007-05-15 Druckverstärker mit integriertem Druckspeicher
PCT/EP2008/055456 WO2008138790A1 (fr) 2007-05-15 2008-05-05 Multiplicateur de pression à accumulateur de pression intégré

Publications (2)

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EP2156049A1 EP2156049A1 (fr) 2010-02-24
EP2156049B1 true EP2156049B1 (fr) 2014-02-26

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EP08759411.5A Not-in-force EP2156049B1 (fr) 2007-05-15 2008-05-05 Multiplicateur de pression à accumulateur de pression intégré

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US (1) US8281767B2 (fr)
EP (1) EP2156049B1 (fr)
JP (1) JP5130354B2 (fr)
CN (1) CN101680411B (fr)
DE (1) DE102007022857A1 (fr)
WO (1) WO2008138790A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016200643B4 (de) * 2016-01-19 2018-04-19 Continental Automotive Gmbh Kraftstoffeinspritzanordnung
CN108730085A (zh) * 2017-04-14 2018-11-02 康明斯公司 低成本共轨燃料系统

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3809502A (en) * 1973-04-06 1974-05-07 Bertea Corp Pressure transformer
CA1052234A (fr) * 1976-05-17 1979-04-10 Gerard G.F. Smeets Systeme surpresseur a deux etages
JPS5512272A (en) * 1978-07-13 1980-01-28 Giichi Yamatani Booster pump
JPS6196169A (ja) * 1984-10-15 1986-05-14 Diesel Kiki Co Ltd 多段燃料噴射装置
DK171121B1 (da) * 1989-08-15 1996-06-17 Johannes Vagn Baatrup Hydraulisk trykforstærker
EP0661459A1 (fr) * 1993-12-31 1995-07-05 Nowsco Well Service Ltd. Multiplicateur de pression hydraulique pour trous de forage
US5337561A (en) * 1992-11-17 1994-08-16 Flow International Corporation Ultra high pressure multiple intensifier system
GB9422864D0 (en) 1994-11-12 1995-01-04 Lucas Ind Plc Fuel system
DE19939422A1 (de) 1999-08-20 2001-03-01 Bosch Gmbh Robert Kraftstoffeinspritzsystem für eine Brennkraftmaschine
US6786205B2 (en) * 2003-01-08 2004-09-07 The United States Of America As Represented By The Environmental Production Agency Hydraulically intensified high pressure fuel system for common rail application
JP4329704B2 (ja) * 2005-02-23 2009-09-09 トヨタ自動車株式会社 燃料噴射装置
DE102007021326A1 (de) * 2007-05-07 2008-11-13 Robert Bosch Gmbh Druckverstärkungssystem für mindestens einen Kraftstoffinjektor
US7451742B2 (en) * 2007-10-29 2008-11-18 Caterpillar Inc. Engine having common rail intensifier and method
US7543568B1 (en) * 2008-02-14 2009-06-09 Gm Global Technology Operations, Inc. Fuel pressure amplifier for improved cranking performance

Also Published As

Publication number Publication date
WO2008138790A1 (fr) 2008-11-20
JP2010526965A (ja) 2010-08-05
US20100154744A1 (en) 2010-06-24
CN101680411A (zh) 2010-03-24
DE102007022857A1 (de) 2008-11-20
CN101680411B (zh) 2012-07-18
JP5130354B2 (ja) 2013-01-30
US8281767B2 (en) 2012-10-09
EP2156049A1 (fr) 2010-02-24

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