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EP2156050A1 - Système d'amplification de pression pour au moins un injecteur de carburant - Google Patents

Système d'amplification de pression pour au moins un injecteur de carburant

Info

Publication number
EP2156050A1
EP2156050A1 EP08749561A EP08749561A EP2156050A1 EP 2156050 A1 EP2156050 A1 EP 2156050A1 EP 08749561 A EP08749561 A EP 08749561A EP 08749561 A EP08749561 A EP 08749561A EP 2156050 A1 EP2156050 A1 EP 2156050A1
Authority
EP
European Patent Office
Prior art keywords
pressure
pressure booster
piston
booster
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP08749561A
Other languages
German (de)
English (en)
Other versions
EP2156050B1 (fr
Inventor
Dominik Kuhnke
Dirk Vahle
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 EP2156050A1 publication Critical patent/EP2156050A1/fr
Application granted granted Critical
Publication of EP2156050B1 publication Critical patent/EP2156050B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/0265—Pumps feeding common rails
    • F02M63/027—More than one high pressure pump feeding a single 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
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • F02M57/026—Construction details of pressure amplifiers, e.g. fuel passages or check valves arranged in the intensifier piston or head, particular diameter relationships, stop members, arrangement of ports or conduits

Definitions

  • the invention relates to a pressure boosting system for at least one fuel injector of an internal combustion engine having a hydraulic pressure booster according to the preamble of claim 1.
  • a fuel injection system with pressure boosting in which a central hydraulic pressure booster is provided for all fuel injectors, is known from EP 1 125 046 B1.
  • the fuel delivered by means of a high pressure pump is fed to a central pressure accumulator (first common rail).
  • the central pressure booster is connected downstream of the central pressure accumulator in the conveying direction of the fuel and supplies the pressure-boosted fuel to a further pressure accumulator (second common rail), from which a plurality of pressure lines corresponding to the number of injectors are discharged to the individual fuel injectors.
  • the central pressure booster described in EP 1 125 046 B1 but also the further known pressure booster integrated in fuel injectors (eg DE 103 25620 A1), have a pressure booster piston which has a first piston section with a first pressure booster piston part with a larger diameter and a second piston portion having a second pressure booster piston part with a small diameter D 22 has.
  • the one pressure booster piston part acts on a high pressure chamber and the other pressure booster piston part acts on a controllable from a switching valve control chamber or differential pressure chamber.
  • the pressure intensifier piston is guided axially movable within a base body.
  • the pressure intensifier piston is assigned to the pressure booster piston part with the larger diameter on the opposite end side of a pressure surface which is exposed to a working space which acts as a hydraulic storage space and which is acted upon by the system pressure of the first common rail.
  • a disadvantage of the known pressure booster system is the relatively large amount of control for controlling the pressure booster. If a translated injection pressure is required for multiple injections of small injection quantities, the control chamber or differential pressure chamber of the booster with each injection to relieve. This results in a large taxable amount to be deducted, which is thus attributable to the loss amount in the injection system. Multiple injections within the scope of a cylinder stroke movement are only possible within a narrow window in terms of time, since with each triggering of the pressure intensifier the differential pressure chamber must again fill up with fuel. In addition, as the injection pressures increase, the amount of leakage increases in proportion to the fourth power across the gap width in the pressure boosting piston guide, adversely affecting the hydraulic efficiency of such fuel injection systems.
  • the object of the present invention is to minimize the loss quantities occurring due to leaks at guide gaps, in order to thus increase the efficiency of the pressure boosting of the fuel injection system.
  • the object of the invention is achieved with the characterizing measures of claim 1.
  • the hydraulic pressure booster used has a body guide body designed for Koben Adjusts stresses for at least one of the pressure booster piston parts, which is at least partially surrounded by an annular space, which in turn is part of the hydraulic storage space. The same pressure prevails in the annulus as in the hydraulic storage space. Due to the surrounding annular space, in particular in the state of pressure transmission, the piston guide body receives an externally acting support pressure, as a result of which inner piston guides are opened or expanded less widely. As a result, the guide gaps are reduced and the leakage amount is minimized.
  • the pressure boosting system according to the invention is also optimized on the part of the space requirement for individual system components. Overall, a significant increase in the overall efficiency of the pressure boosting system is achieved.
  • a first expedient embodiment is that the first pressure booster piston part with the larger diameter D 2 i is provided for the pressure boosting. "O"
  • the high-pressure chamber is arranged inside the piston guide body.
  • the high-pressure chamber is delimited by a spring-loaded high-pressure sleeve, which is guided axially movably on the pressure intensifier piston and is set against the piston guide body at a sealing point. The diameter of the sealing point is less than or equal to a diameter D 2 i of the first pressure booster piston part of the pressure intensifier piston.
  • the control chamber of the pressure booster is designed inside the piston guide body and pressurized by the second pressure booster piston part with the smaller diameter D 22 .
  • a second embodiment provides to reverse the arrangement of the control chamber and high-pressure chamber, in which case the second pressure booster piston part with the smaller diameter D 22 acts on the high-pressure space provided for pressure boosting and the first pressure booster piston part with the larger diameter D 2 i on the control chamber.
  • the high-pressure chamber is formed inside the piston guide body.
  • the control chamber which is acted on by the pressure intensifier piston part with the larger diameter D 2 i, then adjoins the hydraulic storage space.
  • a filling line is provided in all embodiments, which branches off from the hydraulic storage space and via which the control chamber and / or the high-pressure chamber are refilled after the pressure translation phase.
  • the pressure intensifier is provided centrally for a plurality of fuel injectors and is arranged between a high-pressure pump and a high-pressure accumulator. Due to a modular design of the high-pressure pump, pressure booster, high-pressure accumulator and fuel injector, such a central pressure intensifier can be used on all known construction spaces of internal combustion engines.
  • Arrangement of the central hydraulic booster between high-pressure pump and high-pressure accumulator is the central pressure booster per injection cycle of a fuel injector only once to control.
  • the control amount and the leakage amount depending on the number of injections is significantly reduced.
  • the high-pressure pump can be designed smaller dimensions, since less fuel is to be conveyed, since the number of Wiederbe spallphasen the control chamber of the central hydraulic booster is significantly reduced.
  • the central pressure intensifier can be designed in its high-pressure delivery to the maximum possible injection quantity of at least one fuel injector.
  • the hydraulic storage space is filled directly from the high pressure pump via a high-pressure inlet with fuel.
  • the main body, in which the hydraulic storage space is formed may be constructed in one or more parts.
  • the volume of the hydraulic storage space is designed so that the pressure drop is reduced during fuel extraction and the pressure oscillations are damped from the pump delivery to a tolerable for the pressure gain level.
  • At least one bore leads to at least one filling valve.
  • the filling valve is in turn connected via a bore with the hydraulic storage space.
  • From the storage space at least one connecting bore extends to a valve and from there to the control room.
  • From the high-pressure chamber there is at least one hydraulic connection to a high-pressure valve, from where at least one outlet runs to the high-pressure accumulator.
  • the pressure intensifier piston is acted upon by a restoring spring, which moves it back into its initial position, so that it bears against an abutment limit with one end.
  • the spring force of the return spring is designed such that the high pressure piston of the central pressure booster is brought back to its initial position at the stop limit after the pressure boost at a sufficiently high speed.
  • the pressure in the storage space of the high-pressure pump via the inlet further constructed by check valves on the high-pressure flow to the high-pressure accumulator in a first switching position of a switching valve. From there, the fuel reaches the fuel injectors. During this operation, the pressure booster is not activated, so that the pumped by the high-pressure pump fuel passes in the bypass operation of the booster to the high-pressure accumulator (common rail).
  • the pressure booster will be activated.
  • the switching valve which is a 3/2-way valve, electrically, hydraulically or pneumatically operated brought into a second switching position. In this second switching position, the control chamber of the pressure booster is connected to the pressure relief via the switching valve with a pressure booster return.
  • FIG. 1 shows a system structure of a fuel injection system with a central hydraulic pressure booster
  • Figure 2 shows a first embodiment of a hydraulic pressure booster
  • FIG. 3.1 shows the starting position of the hydraulic pressure booster according to FIG. 2
  • FIG. 3.2 shows the pressure transmission phase of the hydraulic pressure booster according to FIG. 2
  • FIG. 3.3 shows a refilling phase of the hydraulic booster proposed according to the invention according to FIG. 2,
  • FIG. 3.4 shows the starting position of the hydraulic proposed according to the invention
  • FIG 4 shows a second embodiment of the hydraulic booster
  • Figure 5 shows a third embodiment of the hydraulic booster
  • Figure 6 shows a fourth embodiment of the hydraulic booster.
  • the fuel injection system shown in Figure 1 shows a modular design of a high-pressure injection system 10, which can be applied, for example, to all installation spaces of internal combustion engines.
  • the high-pressure injection system 10 comprises a fuel tank 12, from which fuel is conveyed via a high-pressure pump 14, which is supplied to a hydraulic pressure booster 16.
  • the hydraulic pressure booster 16 is connected via a pressure booster inlet 44 on the one hand with the already mentioned high-pressure pump 14 and applied on the other hand a high-pressure accumulator 18 (common rail).
  • a high-pressure accumulator 18 common rail
  • the central hydraulic pressure booster 16 supplies according to Figure 1 thus all fuel injectors 20 with pressure-translated fuel.
  • the fuel under high pressure is introduced into the combustion chamber of a self-igniting fuel.
  • Both the pressure booster return 24 and the injector return 22 represent the low-pressure side of the fuel injection system as shown in Figure 1, in which the diverted amount, whether control amount or leakage amount, is fed back into the fuel tank 12.
  • the pressure booster 16 Due to the arrangement of the central pressure booster 16 between the high-pressure pump 14 and the high-pressure accumulator 18, the pressure booster 16 per injection cycle of a fuel injector 20 only once with the switching valve 26 to control. As a result, the amount of control or leakage is significantly reduced depending on the number of injections.
  • the high pressure pump 14 has less fuel to deliver and can be made smaller.
  • the pressure booster 16 is designed in its high-pressure delivery to the maximum possible injection quantity of at least one of the fuel injectors 20.
  • the hydraulic pressure booster 16 comprises a main body 30, which may be constructed in one or more parts.
  • a hydraulic storage chamber 48 is integrated.
  • the hydraulic storage chamber 48 is acted upon by the high-pressure pump 14 via the pressure booster inlet 44 with fuel.
  • the storage volume of the hydraulic storage chamber 48 is designed so that the pressure drop is reduced and can be pressure vibrations resulting from the promotion of the high-pressure pump 14, damped to an endurable for the pressure amplification measure.
  • the central pressure amplifier 16 further comprises a pressure booster piston 32.
  • This in turn comprises a first piston portion with a first pressure booster piston part 54, designed in diameter D 2 i, and a second piston portion with a second pressure booster piston part 56, designed in diameter D 22nd
  • the pressure amplifier 16 also includes a high-pressure chamber 50 for pressure boosting or pressure transmission and a control chamber 52, the latter being also referred to as the differential pressure chamber.
  • a piston guide body 36 is formed, which is surrounded by an annular space 49.
  • the first pressure booster piston part 54 with the diameter D 2 i and the second pressure booster piston part 56 with the diameter D 22 is axially movably guided in the embodiment of Figure 2.
  • the annular space 49 is part of the hydraulic storage space 48 and extends in the axial direction over the guide length for the pressure booster piston 32 within the base body 30.
  • the pressure that rests in the hydraulic storage chamber 48 and is provided by the high-pressure pump 14, represents a mean pressure compared to the increased pressure in the high-pressure chamber 50 and the prevailing in the control chamber 52 low pressure, which occurs when driving the control chamber 52 sets on the basis of the derivative of the control amount on the pressure booster return 24.
  • the pressure booster piston 32 acts with a first pressure surface on the first Duckvertownrkbubenteil 54 with the larger diameter D 2 i on the high-pressure chamber 50 and a second pressure surface on the second pressure booster piston part 56 with the smaller diameter D 22nd on the
  • Control room 52 a In the embodiment according to FIG. 4, it is reversed. There, the pressure booster piston 32 acts with the first pressure surface on the first pressure booster piston part 54 with the larger diameter D 2 i on the control chamber 52 and with a second pressure surface on the second pressure booster piston part 56 with the smaller diameter D 22 on the high pressure chamber 52 a.
  • the pressure booster piston 32 is acted upon by a restoring spring 34, which on the other hand is supported on the piston guide body 36 on the one hand and a collar 33 formed on the pressure booster piston part 56 on the other hand.
  • the pressure booster piston 32, the return spring 34 and the piston guide body 36 are in turn arranged in the storage space 48 that surrounds the piston guide body 36 in the region of the leadership of the pressure booster piston 32, expediently in the range of diameter D 2 i formed first pressure booster piston part 54.
  • a high-pressure drain 46 which extends to the high-pressure accumulator 18 (common rail).
  • a high pressure valve 40 which is designed as a check valve and a return flow of fuel -Q-
  • Pressure booster piston 32 is arranged, presses the pressure booster piston 32 in its initial position so that it rests with a stop limit 42 on the base body 30.
  • the spring force of the return spring 34 is designed so that the pressure booster piston 32 is brought back to the starting position at the stop limit 42 after the pressure boost at a sufficiently high speed.
  • the pressure of the high-pressure pump 14 is transferred via the pressure amplifier inlet 44 into the storage space 48 and from there via the high-pressure valves 38, 40 designed as check valves promoted the high pressure drain 46 to the high-pressure accumulator 18. From there, the fuel reaches the fuel injectors 20 to be supplied with fuel under system pressure.
  • the fuel compressed by the high-pressure pump 14 thus passes directly from the high-pressure pump 14 to the high-pressure accumulator 18 (so-called bypass rail) in the so-called bypass mode. the pressure amplifier 16 is not active in this operating mode.
  • the pressure amplifier 16 is to be controlled.
  • the switching valve 26 is brought electrically, hydraulically or pneumatically into a second switching position.
  • the control chamber 52 is connected to the pressure booster return 24.
  • the pressure booster piston 32 against the spring force of Return spring 34 moves axially, so that the first pressure booster piston part 54, formed in the diameter D 2 i, presses in the high-pressure chamber 50 and there increases the pressure.
  • the filling valve 38 is in the direction of the pressure booster return 24.
  • the high-pressure accumulator 18 (common rail) by the high-pressure valve 40.
  • the high pressure accumulator 18 is thus filled with the increased pressure from the high pressure chamber 50.
  • the fuel injectors 20 are then subjected to the increased fuel pressure, so that the injection via the fuel injectors with the above the delivery pressure of the high-pressure pump 14 fuel pressure.
  • the pressure in the high-pressure chamber 50 increases until a force equilibrium is again established at the pressure intensifier piston 32.
  • the control chamber 52 Upon deactivation of the switching valve 26, the control chamber 52 is hydraulically connected to the storage space 48 again. Due to this hydraulic connection, the pressure in the control chamber 52 increases and the pressure booster piston 32 terminates the operation of the pressure ratio according to the pressure transmission ratio i in the high pressure chamber 50. At the same time, the high pressure valve 40 closes due to the upcoming pressure difference. The spring force of the return spring 34 now presses the pressure booster piston 32 with the stop limit 42 to the main body 30 of the pressure booster 16. During this period fuel is sucked from the storage space 48 via the filling valve 38 into the high-pressure chamber 50. If the pressure booster piston 32 has reached the limit stop 42, the switching valve 26 can be actuated for renewed pressure transmission. Before reaching the stop limit 42, although a renewed control is possible, but not meaningful due to the then still indefinite reset position of a first pressure booster piston part 54 and a second pressure booster piston part 56 having pressure booster piston 32.
  • FIGS. 3.1 to 3.4 shows the operating phases of the pressure booster 16 according to FIG. 2, namely the starting position, the pressure ratio, the refilling phase and again the initial position.
  • the storage space 48 is applied in the main body 30 via the pressure booster inlet 44 with pressurized fuel.
  • the pressure that prevails in the storage space 48 is available via the filling line 58 both in the control chamber 52 and via the filling valve 38 in the high-pressure chamber 50.
  • the pressure booster 16 is not activated by the switching valve 26.
  • the memory space 48 and the control chamber 52 are short-circuited due to the switching position of the switching valve 26.
  • FIG. 3.2 shows the self-adjusting activation of the pressure booster 16 during a pressure transmission process.
  • the switching valve 26 is energized and the control chamber 52 with the pressure booster return 24, that is connected to the low pressure region of the fuel injection system 10. Due to the pressure relief of the control chamber 52 of the drives second pressure booster piston part 56 in the control chamber 52, so that the stockpiled in the high pressure chamber 50 fuel by further retraction of the pressure booster piston 32, in particular the first pressure booster piston part 54, is compressed.
  • the maximum pressure prevailing in the high-pressure chamber 50 is discharged via the high-pressure valve 40 into the high-pressure drain 46 and from there reaches the high-pressure accumulator 18 (common rail), which is not shown in FIG. 3.2.
  • An outflow of the fuel from the high pressure chamber 50 is not possible contrary to the effective direction of the filling valve 38. This blocks in the direction of medium pressure, the connection geometry shown in Figure 3.2 on the switching valve 26 to the low pressure.
  • FIG. 3.3 shows a refilling phase of the pressure intensifier, wherein the switching valve 26 is switched back to its switching position shown in FIG. 3.1.
  • FIG. 3.3 shows that the storage space 48 via the pressure booster inlet 44 is continuously pressurized, according to the pressure level of the high-pressure pump 14 pre-compressed fuel is applied.
  • the fuel stored in the storage space 48 flows via the filling line 58 and via the switching valve 26 both to the control chamber 52 and fills it, as well as the high-pressure chamber via the filling valve 38, so that in this again fuel is filled.
  • the pressure booster piston 32 with its first booster piston part 54 and its second booster piston part 56 returns to its initial position according to FIG 3.4, in the stop limit 42 contacts the inside of the main body 30.
  • FIG. 4 shows that according to this embodiment, the pressure booster 16 comprises the main body 30 in which the piston guide body 36 is formed.
  • the main body 30 of the storage space 48 is formed, which is acted upon by the pressure booster inlet 44 of the high-pressure pump 14 shown in Figure 1 at below its maximum pressure level standing pressure.
  • the pressure booster piston 32 In the storage space 48 is also the pressure booster piston 32, on which the collar 33 is executed, on which the return spring 34 is supported.
  • the return spring 34 is supported on the other hand on an annular surface of the piston guide body 36.
  • the high-pressure chamber 50 is limited by the second pressure booster piston part 56 with the small diameter D 22 in the embodiment shown in FIG 4, while the control chamber 52 through the first pressure booster piston part 54 of the pressure booster piston 32 with the larger diameter D 2 i is limited.
  • This change in comparison with the embodiment according to FIG. 2 results in a changed pressure transmission ratio i according to the following relationship:
  • the number of leakage points to the low pressure at the pressure booster piston 32 is higher.
  • the pressure booster with reversed control and high pressure chamber 52 and 50 respectively based on the embodiment of Figure 2, a refilling of the control chamber 52 through the storage chamber 48, the filling line 58, the short circuit on the switching valve 26, while refilling the by Reference numeral 50 designated high-pressure chamber through the filling valve 38 from the storage space 48 takes place.
  • the high-pressure outlet is designated by reference numeral 46
  • the pressure-intensifier return assigned to the switching valve 26 is designated by reference numeral 24.
  • FIG. 5 shows a further exemplary embodiment of the pressure intensifier 16, in which the high-pressure chamber 50 is delimited by a high-pressure sleeve 60.
  • the high-pressure chamber 50 is formed by a high-pressure sleeve accommodated on the first pressure intensifier piston part 54 60 limited.
  • the high-pressure sleeve 60 is acted upon by a biasing spring 64. This is based as well as the return spring 34 on the collar 33 of the first pressure booster piston part 54 of the pressure booster piston 32 from.
  • the biasing spring 64 By the action of the biasing spring 64 is a biting edge of the high-pressure sleeve 60, forming a sealing point 62, made against the piston guide body 36.
  • the return spring 34 which is supported on the collar 33 of the first pressure booster piston part 54, passes through the entire storage space 48 and is supported on the base body 30.
  • the second pressure booster piston part 56 of the pressure booster piston 32 projects into the piston guide body 36.
  • the high-pressure sleeve 60 performs the filling function of the high-pressure chamber 50.
  • a constructive advantage of this variant is the fact that the high-pressure sleeve 60 is guided by the pressure intensifier piston 32.
  • the sealing diameter at the sealing point 62 must always be smaller or at most the same size as the piston diameter of the first pressure booster piston part 54, ie D 2 i. So that the high-pressure sleeve 60 is always held in a defined starting position, this is acted upon by the biasing spring 64.
  • the design of the spring force for the biasing spring 64 is interpreted as a function of the spring force of the return spring 34 and the remaining annular surface between the sealing point 62 and the piston diameter of the second pressure booster piston part 56 D 22 .
  • the refilling of the control chamber 52 can in principle take place via the high-pressure chamber 50, the filling line 66 and by using the short-circuit switching position of the switching valve 26, as shown in FIG. Due to the lifting movement of the high pressure sleeve 60 when refilling the high pressure chamber 50, this can perform uncontrolled opening and closing movements. Without suitable countermeasures, this would lead to high wear on the sealing point 62 and on the guidance of the pressure booster piston 32, which negatively influenced the function of the embodiment of the pressure booster 16. With a suitable adjustment of seat geometry and pressure level, a clean switching function is ensured.
  • the high-pressure drain 46 which extends to the high-pressure accumulator 18, not shown in FIG. 5, accommodates the high-pressure valve 40, which in this embodiment is designed as a check valve.
  • the high-pressure sleeve 60 is likewise used to delimit the high-pressure chamber 50.
  • This includes an external recess in which a Hubanschlagelement 70 which is fixed to the piston guide body 36 engages, and thus defines the maximum Axialhub 68 of the high-pressure sleeve 60 relative to the piston guide body 36. If the high-pressure sleeve 60 has passed through its maximum permissible stroke 68, the stroke stop element 70 limits further lifting movements. For this purpose, the stroke stop element 70 between the return ⁇ _ o ⁇
  • Stellfeder 34 and the piston guide body 36 is arranged.
  • the biasing force of the return spring 34 prevents lifting of the Hubantschiatas 70 of the bearing surface on the piston guide body 36, which is part of the base body 30 of this embodiment of the booster 16.
  • the biasing spring 64 and the return spring 34 are based on the collar 33 of the first booster piston part 54.
  • the storage space 48 which acts on the guide body 36 with an externally acting support pressure to keep the leakage amounts low, is acted upon analogously to the above-described embodiments of the pressure booster 16 via the pressure booster inlet 44 from the high pressure pump 14 (see illustration of Figure 1).

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

Abstract

L'invention concerne un système d'amplification de pression pour au moins un injecteur de carburant d'un système d'injection haute pression d'un moteur à combustion interne, comportant un amplificateur de pression hydraulique (16) commandé par une soupape de commande (26). L'amplificateur de pression hydraulique comporte un piston d'amplificateur hydraulique (32) présentant une première partie de piston (54) ayant un diamètre D<SUB>21</SUB> et une deuxième partie de piston (56) ayant un diamètre D<SUB>22, </SUB>le diamètre D<SUB>21</SUB> étant supérieur au diamètre D<SUB>22</SUB>. Le piston d'amplificateur hydraulique (32) est disposé avec la première partie de piston (54) de diamètre D<SUB>21</SUB> supérieur dans un espace d'accumulateur hydraulique (48) pressurisé, créé quant à lui dans un corps de base (30). Le corps de base (30) présente un corps de guidage de piston (36) pour au moins une des parties de piston (54, 56). Le corps de guidage de piston (36) est au moins partiellement entouré par un espace annulaire (49) faisant partie de l'espace d'accumulateur hydraulique (48).
EP08749561A 2007-05-07 2008-04-15 Système d'amplification de pression pour au moins un injecteur de carburant Not-in-force EP2156050B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007021326A DE102007021326A1 (de) 2007-05-07 2007-05-07 Druckverstärkungssystem für mindestens einen Kraftstoffinjektor
PCT/EP2008/054531 WO2008135349A1 (fr) 2007-05-07 2008-04-15 Système d'amplification de pression pour au moins un injecteur de carburant

Publications (2)

Publication Number Publication Date
EP2156050A1 true EP2156050A1 (fr) 2010-02-24
EP2156050B1 EP2156050B1 (fr) 2012-08-15

Family

ID=39671973

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08749561A Not-in-force EP2156050B1 (fr) 2007-05-07 2008-04-15 Système d'amplification de pression pour au moins un injecteur de carburant

Country Status (6)

Country Link
US (1) US8161947B2 (fr)
EP (1) EP2156050B1 (fr)
JP (1) JP4848047B2 (fr)
CN (1) CN101680412B (fr)
DE (1) DE102007021326A1 (fr)
WO (1) WO2008135349A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007022857A1 (de) * 2007-05-15 2008-11-20 Robert Bosch Gmbh Druckverstärker mit integriertem Druckspeicher
DE102008003347A1 (de) 2008-01-07 2009-07-09 Robert Bosch Gmbh Druckverstärkeranordnung
CA2758246C (fr) * 2011-11-16 2013-02-12 Westport Power Inc. Procede et appareil pour pomper du carburant dans un systeme d'injection de carburant
RU2543926C1 (ru) * 2014-04-28 2015-03-10 Федеральное государственное унитарное предприятие "Центральный ордена Трудового Красного Знамени научно-исследовательский автомобильный и автомоторный институт "НАМИ" Устройство для подачи топлива к форсунке дизельного двигателя
JP6583304B2 (ja) * 2017-02-17 2019-10-02 トヨタ自動車株式会社 内燃機関の制御装置

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3059433A (en) * 1961-02-14 1962-10-23 Hirsch George Pressure and force multiplying devices
US3737254A (en) * 1972-02-22 1973-06-05 Fluid Controls Inc Regenerative rapid stroke reciprocating hydraulic pressure converter
US4233000A (en) * 1979-12-03 1980-11-11 Halliburton Company Variable ratio intensifier
JP2885076B2 (ja) * 1994-07-08 1999-04-19 三菱自動車工業株式会社 蓄圧式燃料噴射装置
US5730104A (en) * 1997-02-19 1998-03-24 Caterpillar Inc. Injection rate shaping device for a fill metered hydraulically-actuated fuel injection system
DE19908418C1 (de) * 1999-02-26 2000-10-26 Siemens Ag Steuerventil zum Einsatz in einem Speichereinspritzsystem für einen Dieselmotor
DE19910970A1 (de) * 1999-03-12 2000-09-28 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung
JP2000303933A (ja) * 1999-04-20 2000-10-31 Mitsubishi Electric Corp 高圧燃料ポンプ装置
DE19939422A1 (de) 1999-08-20 2001-03-01 Bosch Gmbh Robert Kraftstoffeinspritzsystem für eine Brennkraftmaschine
JP2002004975A (ja) * 2000-06-21 2002-01-09 Toyota Motor Corp 高圧燃料供給装置
GB0215488D0 (en) * 2002-07-04 2002-08-14 Delphi Tech Inc Fuel injection system
DE10247903A1 (de) * 2002-10-14 2004-04-22 Robert Bosch Gmbh Druckverstärkte Kraftstoffeinspritzeinrichtung mit innenliegender Steuerleitung
DE10393780T5 (de) * 2002-11-25 2005-10-27 Hartho-Hydraulic Aps Verstärkerbaueinheit
DE10325620A1 (de) 2003-04-02 2004-10-14 Robert Bosch Gmbh Servoventilangesteuerter Kraftstoffinjektor mit Druckübersetzer
DE10355041A1 (de) * 2003-11-25 2005-06-23 Robert Bosch Gmbh Druckübersetzer mit Führungseinsatz für einen Kraftstoffinjektor
DE10359170A1 (de) * 2003-12-17 2005-08-11 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
US7455049B2 (en) 2004-02-11 2008-11-25 Mazrek Ltd. Actuating mechanism for hydraulically driven pump-injector for internal combustion engines
DE102005026514B4 (de) * 2005-02-18 2008-12-24 Robert Bosch Gmbh Einspritzdüse
JP2007154797A (ja) 2005-12-06 2007-06-21 Denso Corp 燃料噴射装置
DE102008003347A1 (de) * 2008-01-07 2009-07-09 Robert Bosch Gmbh Druckverstärkeranordnung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2008135349A1 *

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US8161947B2 (en) 2012-04-24
JP4848047B2 (ja) 2011-12-28
CN101680412A (zh) 2010-03-24
DE102007021326A1 (de) 2008-11-13
WO2008135349A1 (fr) 2008-11-13
CN101680412B (zh) 2012-01-04
US20100212636A1 (en) 2010-08-26
EP2156050B1 (fr) 2012-08-15
JP2010526248A (ja) 2010-07-29

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