EP1403509A2 - 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
EP1403509A2
EP1403509A2 EP03003826A EP03003826A EP1403509A2 EP 1403509 A2 EP1403509 A2 EP 1403509A2 EP 03003826 A EP03003826 A EP 03003826A EP 03003826 A EP03003826 A EP 03003826A EP 1403509 A2 EP1403509 A2 EP 1403509A2
Authority
EP
European Patent Office
Prior art keywords
pressure
limiting device
fuel
pressure limiting
piston
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
EP03003826A
Other languages
German (de)
English (en)
Other versions
EP1403509B1 (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, with a housing which has an inlet and an outlet, and with a prestressed element which fluidically connects the inlet to the outlet from a certain pressure difference between the inlet and the outlet.
  • Such a pressure limiting device is known from the market. It is preferably used in those fuel systems which are used in internal combustion engines with gasoline direct injection. Such fuel systems usually have a low pressure area and a high pressure area. An electric fuel pump conveys the fuel to the low pressure range, from which the fuel flows into a fuel rail ("common rail") via a high pressure pump called) is promoted. The pressure in the fuel rail is usually controlled by a pressure control or a volume control valve.
  • a pressure limiting device is provided in the high-pressure area of the fuel system.
  • This is generally a conventional pressure relief valve with a valve element acted upon by a spring against a valve seat. If the pressure in the fuel rail exceeds a certain limit, the valve element lifts off the valve seat so that fuel can flow from the inlet of the pressure relief valve to the outlet and from there back to the low-pressure area of the fuel system.
  • the known pressure limiting device already works very well and, above all, very reliably. However, the possibilities for arranging the pressure relief valve in the fuel system are limited.
  • the pressure limiting device In general, the pressure limiting device must be arranged in the area of the fuel manifold, that is to say at a certain distance from the high-pressure pump. The reason for this is that the high pressure pump generates pressure pulsations during operation, the peaks of which can exceed the opening pressure of the pressure relief valve. If the pressure relief valve were to be placed directly next to the high pressure pump, there would be a risk that the pressure relief valve would open due to the pressure pulsations, although the maximum system pressure had not yet been reached. Only at a certain distance from the high pressure pump is there a smoothing Pressure pulsations due to the throttling effects in the fuel line and due to the compressibility of the fuel.
  • a pressure limiting device in which the pressure pulsations are reduced by an equalizing 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 pressure limiting device to be arranged in the vicinity of the high-pressure pump.
  • the piston of the pressure limiting device has a first collar, and that the collar acts as a throttle between the compensation chamber and the high-pressure fuel line.
  • This measure makes it possible to reduce the pressure peaks in the high-pressure fuel line by throttling and by increasing the volume of the compensation chamber. It has been found that this combination of two simultaneously acting measures for reducing the pressure pulsations is particularly effective and therefore does not open the pressure limiting device in normal operation of the fuel pump even if the pressure limiting device is arranged in the immediate vicinity of the high pressure pump. Only when the quantity control of the fuel pump has a defect and the fuel pump delivers the full delivery regardless of the operating point of the internal combustion engine, does the pressure limiting device respond and prevent impermissibly high pressures in the high-pressure fuel line and the entire high-pressure area of the fuel system.
  • this pressure limiting device according to the invention can be used in almost all fuel pumps or fuel systems without adaptation measures. This greatly reduces the number of variants required, which brings considerable economic advantages in the manufacture, storage and repair of the fuel systems equipped with the pressure limiting device according to the invention.
  • the piston has a second collar and a control edge is formed on the second collar, and that the control edge thus interacts with a recess in the bore such that in the closed state the Pressure limiting device the hydraulic connection between the high pressure fuel line and the low pressure fuel line is interrupted.
  • a spring is clamped between the piston and the housing and acts on the piston in the direction of the closed position of the pressure limiting device.
  • the piston has a sealing cone on its end facing away from the first collar and the sealing cone rests on a sealing seat of the housing in the closed position of the pressure limiting device, the pressure in the high-pressure region of the fuel system is maintained when the internal combustion engine is switched 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 delimited by the third collar, the diameter of the third collar being smaller than the diameter of the first Is federal.
  • the resulting hydraulic force on the first collar is reduced, which - with otherwise the same hydraulic boundary conditions - enables a smaller spring between the piston and the housing.
  • the spring can be made smaller, which helps to reduce the overall volume of the pressure limiting device. Due to the fact that the hydraulic forces between the first collar and the third collar are partially balanced, 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 of less than 4 mm and great precision, the manufacturing costs increase considerably compared to slightly larger parts. This can reduce the cost of the invention. Pressure limiting device can be minimized.
  • the third collar delimits a space with the bore and this space is at least indirectly hydraulically connected to a low-pressure area of the fuel system, so that any leaks that may occur can be removed.
  • a pressure limiting device for a fuel system of an internal combustion engine the pressure limiting device being arranged between a high-pressure fuel line and a low-pressure fuel line, with a housing, with a piston which is guided in a bore in the housing and which starts from one determined between the high-pressure fuel line and the low-pressure fuel line existing pressure difference connects them hydraulically, and with a compensation chamber, if the compensation chamber through a guided in a compensation hole in the housing Compensating piston is limited when the compensating chamber is hydraulically connected to the delivery chamber and when the compensating piston is biased against a travel limitation in such a way that the volume of the compensating chamber is minimal.
  • buffer store designed as a spring-type storage device which, when short-term pressure pulsations occur, converts their pressure energy into mechanical energy and converts this energy back into pressure energy after the pressure pulsations have subsided. This smoothes the pressure peaks in the high-pressure area of the fuel system and prevents undesired opening of the pressure relief valve.
  • 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 connected on the input side with the first fuel pump via a fuel connection, and with a pressure limiting device which limits the pressure in a fuel connection on the outlet side of the second fuel pump.
  • the Pressure limiting device is designed in the manner described above.
  • the second fuel pump include a 1-cylinder piston pump.
  • the pressure pulsations are particularly pronounced, so that the pressure limiting device according to the invention works very effectively here.
  • the pressure limiting device is attached to the second fuel pump, preferably integrated into it.
  • Such an arrangement of the pressure limiting device within the fuel system has the advantage that a return line from the pressure limiting device, for example to the low pressure area of the fuel system, can be dispensed with. As a result, the costs for the fuel system according to the invention are considerably reduced.
  • a fuel system has the reference number 10 overall. It comprises a low-pressure area 12 and a high-pressure area 14.
  • the low-pressure region 12 comprises a reservoir 16, in which fuel 18 is stored.
  • the fuel 18 is delivered from the reservoir 16 by a first fuel pump 20.
  • This is an electric fuel pump.
  • the electric fuel pump 20 feeds into a low-pressure fuel line 22.
  • a filter 24 is initially provided after the electric fuel pump 20 in the flow direction.
  • a branch line 26 branches off from the low-pressure fuel line 22 and leads back to the storage container 16.
  • a pressure relief valve 28 is arranged in the branch line 26.
  • 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 Pressure damper 32 and a check valve 34 are arranged. Between the filter 24 and the pressure damper 32 branches off from the low-pressure fuel line 22, 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.
  • a leakage line 40 leads from the high-pressure pump 30 to the branch line 36.
  • the high-pressure pump 30 feeds into a high-pressure fuel line 42, which leads via a check valve 44 to a fuel collecting line 46.
  • a fuel collecting line 46 To the fuel rail 46 are in turn.
  • Fuel injection valves 48 are connected, which inject the fuel into a combustion chamber, not shown, of the internal combustion engine.
  • 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 is controlled and / or regulated via a quantity control valve.
  • This connects the area of the high-pressure fuel line 42 located between the check valve 44 and the high-pressure pump 30 to the area of the low-pressure fuel line 22 located between the check valve 34 and the pressure damper 32.
  • the connection is made via a branch line 54.
  • the quantity control valve 42 is operated by a Controlled control unit, not shown in Figure 1, which in turn receives signals from the pressure sensor 50. In this way, a closed control loop is created for controlling the pressure in the high-pressure region 14 of the fuel system 10.
  • a pressure limiting device 56 is combined with the high-pressure pump 30.
  • the exact structure of a first exemplary embodiment of a pressure limiting device 56 according to the invention can be seen in FIG. 2:
  • the high pressure pump 30 and the pressure limiting device 56 are accommodated in a common housing 58.
  • the outlet valve 44 comprises a spherical valve element 64, which is acted upon by a spring 66 against a valve seat 68.
  • the high-pressure fuel line 42 is visible downstream of the exhaust valve 44.
  • the delivery chamber 60 which is only partially shown in FIG. 2, is sealed off from the high-pressure fuel line 42 by the outlet valve 44.
  • Exhaust valve has a bore 70 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 over the second collar 76 in the bore 70.
  • the fit of bore 70 and first collar 74 is dimensioned such 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 dimensioned such that a good sealing effect is achieved between bore 70 and second collar 76 and the piston 72 can still be displaced in bore 70.
  • the Piston 72 has an annular groove 78 which is hydraulically connected to the high-pressure fuel line 42.
  • a base 80 of the bore 70 and the first collar 74 of the piston 72 delimit 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.
  • An annular recess 84 is provided in the housing 58 concentrically with the bore 70.
  • the annular groove 78 and the second collar 76 of the piston 72 form a control edge 86 which interacts with the recess 84.
  • the control edge 86 has an overlap with the recess 84, which is indicated in FIG. 2 by the reference number 88.
  • the hydraulic connection between the high-pressure fuel line 42 and the 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 guided through the first collar 74 and the second collar 76 in the bore 70, regardless of its position in the bore 70.
  • a sealing cone 90 is formed on the piston 72 above the second collar 76.
  • 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 is hydraulically connected to 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 at the other end against the piston 72 and presses it with its sealing cone 90 into 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 equalization chamber 82 and the pressure in the equalization chamber 82 increases somewhat delayed.
  • the delay in the pressure rise in the compensation chamber 82 is caused by the throttling action of the annular gap between the first collar 74 and the bore 70.
  • the piston 72 lifts off from the sealing seat 92; that is, it moves up in Figure 2. This also increases the volume of the compensation chamber 82, so that the pressure increase in the high-pressure fuel line 42 and thus in the entire high-pressure region 14 (see FIG.
  • the overlap 88 and the volume of the compensation chamber 88 are designed such 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 are reduced so that they no longer have a negative impact on the operation of the fuel system 10.
  • the overlap 88 and the volume of the compensation chamber 88 are designed such that the hydraulic connection between the high-pressure fuel line 42 and the low-pressure fuel line 22 is not released during normal operation of the fuel system 10. This means that through the use of the pressure limiting device 56 according to the invention, the efficiency of the fuel system 10 remains virtually unchanged in normal operation.
  • the fuel pump 30 (see FIG. 1) always delivers the full delivery rate
  • the pressure in the high-pressure region 14 and thus also in the high-pressure fuel line 42 rises above one compared to the pressure pulsations in normal operation - long period.
  • 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 the recess 84 and fuel flows from the high-pressure fuel line 42 via the spring chamber 94 into the low-pressure fuel line 22, so that a The overpressure prevailing in the high-pressure fuel line 42 takes place.
  • the high-pressure region 14 of the fuel system 10 is thus effectively protected against impermissibly high pressures in the event of malfunctions in the delivery rate control.
  • the pressure curve over time t is shown qualitatively. If a constant volume were present on the outlet side of the high-pressure pump 30, that is to say, for example, in the high-pressure fuel line 42 and the fuel collecting line 46, the Fuel system 10 occur due to the pressure pulsations of the high pressure pump 30 pressure peaks up to a peak value of approximately 180 bar. Such a pressure peak is shown in dashed lines in FIG. This pressure peak results from the acceleration of the fuel column in the high-pressure fuel line 42 by the high-pressure pump 30.
  • the pressure limiting device 56 avoids these pressure peaks occurring during normal operation of the fuel system 10 in the manner described above.
  • the pressure increase in the high-pressure fuel line 42 and the fuel rail 46 is less, which is shown qualitatively in FIG. 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 maintaining pressure in the high-pressure region 14 of the fuel system 10.
  • the overlap 88 between the control edge 86 and the recess 44, the pretension and spring rate of the spring 96 and the volume of the compensating chamber 82 and the throttling action between the first collar 74 and the bore 70 must, as already mentioned, be coordinated with one another such that the second stroke during a delivery stroke When the fuel system 30 is operating correctly, the control edge 86 does not open the recess 84 and therefore no fuel flows from the high-pressure region 14 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 what has been said with regard to FIG. 2 applies 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 compensation chamber 82 is present in this embodiment between the first collar 74 and the third collar 100 and is an annular space, the volume of which increases when the piston 72 moves in the direction of the spring 96.
  • the collar 80 of the bore 70 and the third collar 100 delimit a space 102 which is hydraulically connected to the spring chamber 94 and thus to the low-pressure fuel line 22 via a bore 104. This compensates for the hydraulic forces acting on the end faces of the piston 72.
  • a small hydraulic force which acts counter to the closing force of the spring 96, can be generated in a relatively simple manner in terms of production engineering, with diameters of the piston 72 that are unproblematic in terms of manufacturing engineering.
  • 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 the pressure in the high-pressure region 14 is reduced via a defined leak after the engine is switched off or in overrun mode.
  • the leakage required for this operating state of the internal combustion engine can be set by the fit between the second collar 76 and the bore 70 and the dimensioning of the cover 88.
  • FIG. 6 describes a third exemplary embodiment of a pressure limiting device 56 according to the invention.
  • a conventional pressure-limiting valve 108 known from the prior art is arranged in such a way that the pressure of the high-pressure fuel line 42 is applied to it.
  • the pressure relief valve 108 can be designed as a seat valve or as a piston valve.
  • pressure relief valve 108 When pressure relief valve 108 opens, it establishes a hydraulic connection between high pressure fuel line 42 and low pressure fuel line 22.
  • the pressure limiting valve 108 is integrated in the fuel pump 30. Without additional measures, the pressure relief valve 108 would open at least briefly with each delivery stroke of the fuel pump 30, since with each delivery stroke a pressure surge that passes through the high-pressure fuel line 42 is greater than the opening pressure of the pressure relief valve 108.
  • the measures which prevent the undesired opening of the pressure relief valve 108 during normal operation of the fuel system 10 are described below:
  • a compensating bore 110 is provided in the housing 58 of the fuel pump 30, in which a compensating piston 112 is guided in a sealing manner.
  • the compensating piston 112 is pressed by a compression spring 114, which is supported at one end against the housing 58 and at the other end against the compensating piston 112, against a shoulder 116 of the compensating bore 110 which serves as a first travel limitation.
  • the compensating piston 112 delimits a compensating chamber 82 which connects directly to the delivery chamber 60 of the fuel pump 30. 6, the delivery space 60 is shown completely.
  • a pump piston 118 can be seen, which is sealingly guided in the housing 58 and delimits the delivery space 60. The drive of the pump piston 118 is not shown.
  • the volume of the compensating chamber 82 is minimal. If the pressure acting on the compensating piston 112 in the delivery chamber 60 during the delivery stroke of the pump piston 118 of the fuel pump 30 overcomes the prestressing of the compression spring 114, the compensating piston 112 lifts off from the shoulder 116 and moves away from the delivery chamber 60. As a result, the volume of the compensating chamber 82 increases to, so that the pressure increase in the delivery chamber and thus also in the high-pressure fuel line 42 is limited.
  • the maximum stroke of the compensating piston 112 is designated by "h" in FIG. The maximum stroke h is reached when the compensating piston 112 abuts the base 120 of the compensating bore 110.
  • the preload of the compression spring 114 and the diameter of the compensating piston 112 are dimensioned such that the compensating piston 112 only opens at pressures which are above the normal operating pressure in the high-pressure region 14 of the fuel system 10.
  • the compensating piston 112 lifts off the shoulder 116 before the opening pressure of the pressure limiting valve 108 is reached. This ensures good efficiency of the fuel pump 30 and at the same time effectively prevents short-term pressure peaks from opening the pressure limiting valve 108.
  • a first throttle 122 is provided between the delivery chamber 60 and the check valve 44.
  • This first throttle 122 is designed such that it contributes to damping pressure peaks in the high-pressure fuel line 42 in the case of high pressure gradients in the delivery chamber 60.
  • care must be taken to ensure that the pressure losses in the first throttle 122 do not become too great, since the entire delivery volume of the fuel pump 30 flows through the first throttle 122.
  • a second throttle 126 and an additional volume 128 are arranged in a branch line 124, which connects the high-pressure fuel line 42 to the pressure relief valve 108.
  • the second throttle 126 and the additional volume 128 act as a low-pass filter and thus additionally prevent an undesired brief opening of the Pressure limiting valve 108 due to pressure pulsations that are triggered by the delivery stroke of the fuel pump 30.
  • the pressure relief valve 108 and the rear of the compensating piston 112 are connected to the low-pressure fuel line 22 via leakage lines 130.
  • FIG. 7 shows a further exemplary embodiment of a pressure limiting device 56 according to the invention.
  • the essential difference from the third exemplary embodiment according to FIG. 6 is that the compensating piston 112 and the compensating bore 110 are arranged in the pump piston 118 of the fuel pump 30.
  • the compensating piston 112 has the same hydraulic effect in the exemplary embodiments according to FIG. 6 and FIG. 7.
  • the leakage discharge from the rear of the compensating piston 112 takes place via a longitudinal bore 132 and a transverse bore 134 as well as an annular groove 136 which is connected to the leakage line 130.
  • the compensating piston 118 is secured by a locking ring 140, which also serves as a travel limitation.
  • the locking ring 140 is inserted into a groove 142 in the compensating bore 110.

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)
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
DE10245084 2002-09-27
DE2002145084 DE10245084A1 (de) 2002-09-27 2002-09-27 Druckbegrenzungseinrichtung sowie Kraftstoffsystem mit einer solchen Druckbegrenzungseinrichtung

Publications (3)

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

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1826396A1 (fr) * 2005-12-27 2007-08-29 Robert Bosch Gmbh Système d'Injection Rampe Commune
WO2008016435A1 (fr) * 2006-07-28 2008-02-07 Caterpillar Inc. Soupape de détente de pression à plusieurs étapes ayant différentes pressions d'ouverture
WO2009065761A1 (fr) * 2007-11-23 2009-05-28 Robert Bosch Gmbh Soupape de sûreté et pompe haute pression comprenant ladite soupape de sûreté
WO2009130153A1 (fr) * 2008-04-23 2009-10-29 Continental Automotive Gmbh Dispositif et procédé de répartition du carburant et moteur à combustion interne équipé de celui-ci
WO2011003789A1 (fr) * 2009-07-08 2011-01-13 Delphi Technologies Holding S.À.R.L. Unité pompe
ITMI20101115A1 (it) * 2010-06-18 2011-12-19 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
WO2012089376A1 (fr) * 2010-12-27 2012-07-05 Robert Bosch Gmbh Pompe, notamment pompe d'un système d'injection de carburant
US8240291B2 (en) 2009-10-23 2012-08-14 Caterpillar Inc. Pressure relief valve
US20140050597A1 (en) * 2011-01-31 2014-02-20 Michael Absmeier Pump Unit for a High-Pressure Pump
WO2014206639A1 (fr) * 2013-06-28 2014-12-31 Robert Bosch Gmbh Ensemble hydraulique pour système d'alimentation en carburant d'un moteur à combustion interne
CN108386357A (zh) * 2018-04-18 2018-08-10 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
CN111608833A (zh) * 2020-05-07 2020-09-01 一汽解放汽车有限公司 一种用于平衡共轨***压力的安全限压阀

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008014250A1 (de) * 2008-03-13 2009-09-17 Man Diesel Se Kraftstoffversorgungsanlage 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
KR102540496B1 (ko) * 2021-08-30 2023-06-07 주식회사 현대케피코 맥동 체적 확장형 고압펌프

Citations (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
US5927323A (en) * 1997-04-23 1999-07-27 Zexel Corporation Pressure control valve
EP0950810A2 (fr) * 1998-04-15 1999-10-20 Mitsubishi Denki Kabushiki Kaisha Dispositif d'arrêt d'une membrane pour un accumulateur de haute pression
WO2002044549A2 (fr) * 2000-11-30 2002-06-06 Robert Bosch Gmbh Pompe d'injection de carburant de moteurs a combustion interne, notamment de moteurs diesel
DE10118936A1 (de) * 2001-04-18 2002-11-07 Bosch Gmbh Robert Druckbegrenzungseinrichtung sowie Kraftstoffsystem mit einer solchen Druckbegrenzungseinrichtung

Patent Citations (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
US5927323A (en) * 1997-04-23 1999-07-27 Zexel Corporation Pressure control valve
EP0950810A2 (fr) * 1998-04-15 1999-10-20 Mitsubishi Denki Kabushiki Kaisha Dispositif d'arrêt d'une membrane pour un accumulateur de haute pression
WO2002044549A2 (fr) * 2000-11-30 2002-06-06 Robert Bosch Gmbh Pompe d'injection de carburant de moteurs a combustion interne, notamment de moteurs diesel
DE10118936A1 (de) * 2001-04-18 2002-11-07 Bosch Gmbh Robert Druckbegrenzungseinrichtung sowie Kraftstoffsystem mit einer solchen Druckbegrenzungseinrichtung

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1826396A1 (fr) * 2005-12-27 2007-08-29 Robert Bosch Gmbh Système d'Injection Rampe Commune
WO2008016435A1 (fr) * 2006-07-28 2008-02-07 Caterpillar Inc. Soupape de détente de pression à plusieurs étapes ayant différentes pressions d'ouverture
US8371268B2 (en) 2007-11-23 2013-02-12 Robert Bosch Gmbh Safety valve and high-pressure pump comprising said safety valve
WO2009065761A1 (fr) * 2007-11-23 2009-05-28 Robert Bosch Gmbh Soupape de sûreté et pompe haute pression comprenant ladite soupape de sûreté
WO2009130153A1 (fr) * 2008-04-23 2009-10-29 Continental Automotive Gmbh Dispositif et procédé de répartition du carburant et moteur à combustion interne équipé de celui-ci
US10041457B2 (en) 2009-07-08 2018-08-07 Delphi Technologies Ip Limited Pump unit
WO2011003789A1 (fr) * 2009-07-08 2011-01-13 Delphi Technologies Holding S.À.R.L. Unité pompe
EP2287462A1 (fr) * 2009-07-08 2011-02-23 Delphi Technologies Holding S.à.r.l. Unité de pompe
US8240291B2 (en) 2009-10-23 2012-08-14 Caterpillar Inc. Pressure relief valve
ITMI20101115A1 (it) * 2010-06-18 2011-12-19 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
WO2012089376A1 (fr) * 2010-12-27 2012-07-05 Robert Bosch Gmbh Pompe, notamment pompe d'un système d'injection de carburant
US10047740B2 (en) * 2011-01-31 2018-08-14 Continental Automotive Gmbh Pump unit for a high-pressure pump
EP3059437A1 (fr) * 2011-01-31 2016-08-24 Continental Automotive GmbH Unite de pompe pour une pompe a haute pression
EP3059439A1 (fr) * 2011-01-31 2016-08-24 Continental Automotive GmbH Unite de pompe pour une pompe a haute pression
EP2670971B1 (fr) * 2011-01-31 2017-03-15 Continental Automotive GmbH Unité pompe pour une pompe haute pression
US20140050597A1 (en) * 2011-01-31 2014-02-20 Michael Absmeier Pump Unit for a High-Pressure Pump
WO2014206639A1 (fr) * 2013-06-28 2014-12-31 Robert Bosch Gmbh Ensemble hydraulique pour système d'alimentation en carburant d'un moteur à combustion interne
CN108386357A (zh) * 2018-04-18 2018-08-10 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
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
CN111608833A (zh) * 2020-05-07 2020-09-01 一汽解放汽车有限公司 一种用于平衡共轨***压力的安全限压阀
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***压力的安全限压阀

Also Published As

Publication number Publication date
JP2004116526A (ja) 2004-04-15
DE50304554D1 (de) 2006-09-21
EP1403509B1 (fr) 2006-08-09
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
DE10327411B4 (de) Druckbegrenzungsventil sowie Kraftstoffsystem mit einem solchen Druckbegrenzungsventil
EP1776523B1 (fr) Systeme d'injection de carburant
EP2273115B1 (fr) Pompe à fluide, en particulier pompe à carburant haute pression, avec amortisseur de pression
EP1403509B1 (fr) Dispositif de limitation de pression et système de combustible avec tel dispositif de limitation de pression
EP2670971B1 (fr) Unité pompe pour une pompe haute pression
DE10115324A1 (de) Kraftstoffsystem
DE19541507A1 (de) Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
DE102005033638A1 (de) Kraftstoff-Fördereinrichtung, insbesondere für eine Brennkraftmaschine
DE19846157A1 (de) Pumpenanordnung zur Kraftstoffhochdruckerzeugung
EP2932086A1 (fr) Ensemble pompe et système pour véhicule automobile
DE10118936A1 (de) Druckbegrenzungseinrichtung sowie Kraftstoffsystem mit einer solchen Druckbegrenzungseinrichtung
DE69822125T2 (de) Membrananschlagkonstruktion für einen Hochdruckspeicher
EP2156050B1 (fr) Système d'amplification de pression pour au moins un injecteur de carburant
WO2007141094A1 (fr) Dispositif d'injection de carburant pour un moteur à combustion interne
DE10208576A1 (de) Hydraulische Druckentlastungseinrichtung für eine Kraftstoffeinspritzanlage
WO2004027250A1 (fr) Dispositif d'injection de carburant pour moteur à combustion interne
DE102020206034A1 (de) Kraftstoffhochdruckpumpe
WO2008122521A1 (fr) Soupape et système d'injection pour un moteur à combustion interne comprenant une soupape
EP2659127B1 (fr) Conjoncteur-disjoncteur pour un système d'injection de carburant d'un moteur à combustion interne
DE102011089626A1 (de) Druckbegrenzungsventil für eine Kraftstofffördereinrichtung sowie Kraftstofffördereinrichtung
DE10160490B4 (de) Kraftstoff-Einspritzvorrichtung, Kraftstoffsystem sowie Brennkraftmaschine
DE102011089964A1 (de) Drucksteuerventil für ein Kraftstoffeinspritzsystem sowie Kraftstoffeinspritzsystem
DE102004007317A1 (de) Kraftstoffhochdruckpumpe für eine Brennkraftmaschine

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