EP2188516B1 - Fuel injection device - Google Patents

Fuel injection device Download PDF

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Publication number
EP2188516B1
EP2188516B1 EP20080783475 EP08783475A EP2188516B1 EP 2188516 B1 EP2188516 B1 EP 2188516B1 EP 20080783475 EP20080783475 EP 20080783475 EP 08783475 A EP08783475 A EP 08783475A EP 2188516 B1 EP2188516 B1 EP 2188516B1
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EP
European Patent Office
Prior art keywords
housing
valve
pressure
high
fuel
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.)
Active
Application number
EP20080783475
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German (de)
French (fr)
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EP2188516A1 (en
Inventor
Marco Ganser
Ulrich Moser
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.)
Ganser-Hydromag AG
Ganser Hydromag AG
Original Assignee
Ganser-Hydromag AG
Ganser Hydromag AG
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.)
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Publication date
Priority to CH14282007 priority Critical
Application filed by Ganser-Hydromag AG, Ganser Hydromag AG filed Critical Ganser-Hydromag AG
Priority to PCT/CH2008/000375 priority patent/WO2009033304A1/en
Publication of EP2188516A1 publication Critical patent/EP2188516A1/en
Application granted granted Critical
Publication of EP2188516B1 publication Critical patent/EP2188516B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/02Fuel-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
    • F02M63/0225Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/02Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
    • F02M55/025Common rails
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/04Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/165Filtering elements specially adapted in fuel inlets to injector
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/40Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator

Abstract

The invention relates to an injection device for injecting high-pressure fuel into the combustion chamber of an internal combustion engine, said device comprising an injection valve assigned to a discrete reservoir chamber (68). A non-return valve (74) operates between said chamber and the high-pressure supply line (44) and the filter (72), which is preferably designed as an edge filter (72'), forms a stop (106) for limiting the opening motion of the valve member (100) that is preferably designed as a valve member plate (100' ).

Description

  • The present invention relates to a device for injecting high-pressure fuel into a combustion chamber in an internal combustion engine according to the preamble of patent claim 1.
  • The DE 10 2005 012 928 A1 discloses a fuel injector in which each injector is connected via a hydraulic line to a high pressure pump and / or to the injector of another cylinder of the internal combustion engine.
  • From the pamphlets US 2004/0251322 A1 . US 4,111,370 and EP 1 223 335 A2 It is known to connect the high pressure supply line to the housing of an injection valve by means of a clamp enclosing the housing.
  • Another injector is out of the WO 2007/009279 A1 known. In this known high-pressure accumulator injection system for an internal combustion engine each injection valve, a storage chamber and a check valve associated with parallel bypass throttle. The injection valves are connected via fuel lines with a high-pressure conveyor. Thanks to the check valve associated with each injection valve with bypass throttle connected in parallel, this high-pressure accumulator injection system can be used to realize stable and reproducible injection processes with a favorable pressure curve in each injection process, even if the discrete storage chambers have an unusually small volume. This high-pressure accumulator injection system does not require a bulky common rail.
  • Another injector is out of the EP 1 108 886 A known. In the cylinder head of an internal combustion engine, an injection valve is used for each combustion chamber. For each injection valve runs through the cylinder head, a bore into which a pressure tube is inserted. The housing of the injection valve has laterally on a high-pressure sealing surface on which rests the pressure tube with its integrally formed on this side end Hochdruckgegendichtfläche. The high-pressure return line to each pressure tube is formed by a single common rail, which is fastened by means of screws and claws directly to the cylinder head. The claws form a structural unit with the common rail, which can be pressed by means of screws for sealing against the pressure tube. Between the common rail and each pressure tube, a flow restrictor may be provided, which is fastened by means of a thread on the common rail and rests with its end remote from the common rail on the pressure tube. The common rail forming the high-pressure feed line forms a common memory for the high-pressure fuel for all injectors. Common Rails are dependent on the number of cylinders of the internal combustion engine, the configuration of the internal combustion engine and their performance and thus specific for each engine type.
  • To fix the associated disadvantages is in the EP 1 485 609 B1 proposed to connect to each a storage space having injection valve via a screw a tubular high-pressure connector, which forms a further storage space. On the other hand, the high-pressure connector is connected via an inlet throttle with a channel for the fuel.
  • At one of the WO 03/027485 A1 known fuel injection system, a number of fuel injectors are pressurized via high-pressure lines with high-pressure fuel via a high-pressure accumulator. The fuel injectors comprise an annular space into which a connecting piece receiving the high-pressure line opens. Associated with the high-pressure feed line is seen in the flow direction before the injector lying an additional volume added, which its distributor side facing a hydraulic decoupling element comprises.
  • The JP 2000-205081 A discloses a storage injection system in which fuel is supplied by means of a high-pressure pump under high pressure to a common rail. An auxiliary storage is connected between a distributor pipe arranged downstream of the common rail and a nozzle holder. The auxiliary storage has a capacity of 3 to 20 times the amount of fuel required for a full load injection.
  • Also from the DE 10 2004 055 266 A1 known fuel injection system provides for a pressure accumulator between a high-pressure fuel pump and the injectors for each injector.
  • The WO 03/076794 A1 discloses an injection system, which has delivery units for conveying fuel from a fuel reservoir for supplying at least one high-pressure line to the cylinders of an internal combustion engine. A number of fuel injectors are supplied via the at least one high-pressure line, wherein it comprises line sections with which the individual fuel injectors are connected to one another. The injector bodies comprise an integrated storage space.
  • When out of the EP 0 921 303 A known common rail injection system, the memory is connected directly via a claw and a pressure tube to the injector. In the event that larger leaks should occur in the injection system, a flow restrictor may be interposed between the accumulator and the claw.
  • The EP 1 353 063 A2 discloses a fuel injection system in which at least one injector connected to a feed system is provided for each cylinder of the internal combustion engine. The feed system has an associated fuel pressure accumulator for each cylinder.
  • That in the DE 101 14 219 A1 disclosed fuel injection system for supplying the combustion chambers of an internal combustion engine with fuel has a high-pressure pump, which acts on a number of fuel injectors with high pressure fuel. The individual fuel injectors each have a storage volume is assigned, which is acted upon directly by a high-pressure supply line from the high-pressure pump.
  • Based on this prior art, it is an object of the present invention to provide a generic device, which allows in a simple manner, the supply of another injector with fuel.
  • This object is achieved with a device having the features of claim 1.
  • A feed connection and a clamp can be arranged on a housing of the injection valve itself or a pressure port.
  • A filter preferably retains solid particles in the fuel, which prevents clogging of, in particular, narrow flow cross sections and thus increases the reliability of the injection device. Since the filter also serves as a stop for limiting the opening movement of a valve member of a check valve, a particularly simple, space-saving design is possible.
  • Preferred embodiments of the device according to the invention are indicated in the dependent claims 2 to 12.
  • Optimum injection processes without a common rail also make possible an injection device in which a pressure port assigned to an injection valve has a storage housing and a pressure pipe fastened thereto, for example via a screw connection. The storage enclosure is connected to a high pressure supply line for the fuel and defines a discrete storage chamber for the fuel.
  • The discharge nozzle forms a stable, self-supporting, preassembled unit. If the discharge nozzle has a storage housing and a pressure pipe fastened thereto via a screw connection, it is possible in a particularly simple manner to form the pressure chamber.
  • Moreover, the formation of the device with a screw connection allows the particularly simple installation of further components in the discharge nozzle, such as a check valve, a filter, in particular rod filter, and a flow-limiting valve.
  • With the discrete storage chamber in the discharge nozzle optimal injection processes are possible, even if the high pressure supply line has a small storage volume. It is possible that each injection valve itself is provided with a further storage chamber.
  • With regard to the dimensioning of the storage chamber and the operation of the storage chamber in conjunction with the storage chambers of the respective discharge nozzle associated with the other injectors of the device is on the WO 2007/009297 A directed. Functionally, the discrete storage chambers described there are the same effect with the storage chambers in the discharge nozzle.
  • The present invention will be described with reference to exemplary embodiments illustrated in the drawings. It shows purely schematically:
  • Fig. 1
    four injection valves of a series of arranged in a cylinder head of an internal combustion engine injectors, the injection valves associated pressure port and a high pressure feed line for feeding the injectors with fuel in a perspective view;
    Fig. 2
    in view of two in the Fig. 1 shown injectors with the associated pressure port and the high pressure supply line;
    Fig. 3
    a longitudinal section through a, a storage housing and a pressure tube having discharge nozzle according to the Fig. 1 and 2 as well as a clamping claw;
    Fig. 4
    a section along the line CC the Fig. 3 through the storage enclosure and an encompassing this clamp;
    Fig. 5
    in longitudinal section a part of the storage housing with a check valve and rod filter arranged therein;
    Fig. 6
    also in longitudinal section a part of the storage housing and the pressure tube in the screw connection with a flow-limiting valve arranged therein;
    Fig. 7
    a longitudinal section of a part of an injection valve housing of an injection valve with a connecting piece, in which the check valve and the rod filter are arranged;
    Fig. 8
    also in longitudinal section a part of another embodiment of the injection valve housing (which is not encompassed by a clamp according to claim 1) with a sealing plug, on which the valve seat of the check valve is formed, and a rod filter; and
    Fig. 9
    a cross section through a housing body of an injection valve (which is not encompassed by a clamp according to claim 1), wherein on the sealing plug of the rod filter is formed.
  • Fig. 1 shows the first three and the last of a number of injection valves 10 of an internal combustion engine 12. Such injectors 10 are well known and intended to intermittently inject under very high pressure fuel into combustion chambers 14 of the internal combustion engine 12. The injection valves 10 are inserted into the cylinder head 16 of the internal combustion engine 12 and secured by means of clamping claws 18 and clamping screws 20 on the cylinder head 16.
  • Each of the identically trained and also in FIG. 2 Injectors 10 shown has an at least approximately cylindrical valve housing 22, the housing body is provided on its outer side with an outwardly directed high pressure sealing surface 24, which a fuel inlet opening of the valve housing 22 (see also Fig. 3 ) surrounds. In a preferred manner, the high-pressure sealing surface 24 formed on the valve housing 22 tapers conically - seen in the radial direction with respect to the longitudinal axis 28 of the injection valve 10 - from the outside against the inside.
  • Viewed in the direction of the longitudinal axis 28, the generally known injection valves 10 have, on the one hand, nozzle openings for injecting the fuel and, on the other hand, connections for the electrically controlled actuator and optionally the fuel return. The actuator controls a hydraulic control device for intermittently injecting the fuel.
  • Each injection valve is associated with a discharge nozzle 30 whose longitudinal axis 32 is preferably at least approximately, in this case exactly right angles to the longitudinal axis 28 of the injection valve 10 and this longitudinal axis 28 intersects. The discharge nozzles 30 each have a pressure tube 34 and a storage housing 36, which by means of a Screw 38 are firmly connected.
  • At the pressure tube 34, at the memory housing 36 remote from the free end portion, a preferably conical or spherical Hochdruckgegendichtfläche 40 is formed. The pressure tube rests with its Hochdruckgegendichtfläche 40 on the high-pressure sealing surface 24 of the valve housing 22. If the Hochdruckgegendichtfläche 40 conically tapering towards the end of the pressure tube 34 or spherical at the end, the pressure tube 34 engages in the valve housing 22, resulting in an automatic centering of the pressure tube 34 with respect to the injection valve 10.
  • The discharge ports 30 are, as in the Fig. 1 is indicated, inserted into the cylinder head 16 and by means of further clamping claws 18 'and other clamping screws 20' attached thereto and pressed in the direction against the injectors 10 such that the high-pressure sealing surfaces 24 and high-pressure counter-sealing surfaces 40 sealingly abut each other. The further clamping claws 18 'and clamping screws 20' form clamping devices 41 for the discharge nozzle 30. The valve housing 22 and storage housing 36 are in the region of the attack of the clamping claws 18 and 18 'formed the same, so that for fixing the injectors 10 and for fixing the discharge nozzle 30 identical trained clamps 18, 18 'and clamping screws 20, 20' can be used.
  • The storage housings 36 have, at their free end facing away from the pressure tube 34, a feed connection 42 arranged concentrically to the longitudinal axis 28. To the supply port 42 of the first injection valve 10th leads a high pressure feed line 44, which in the Fig. 2 is shown. This is the other hand connected to a not shown, well-known high-pressure pump, which supplies the injectors 10 under very high pressure, for example, about 1600 to more than 2000 bar standing fuel.
  • Subsequent to the supply connection 42, each storage housing 36 is encompassed by a clamp 48. In the region of the clamp 48, each storage housing 36 has a radial connection passage 50 - see Fig. 3 to 5 - To supply via another high pressure feed line 44 'the discharge nozzle 30 of the next injection valve 10 fuel. The connecting passage 50 of the last of the series of injection valves 10 associated pressure port 30 is sealed by means inserted into the clip 48 locking pin 52. As a result, all storage enclosures 36 and clamps 48 can be made the same. If the internal combustion engine 12 is an in-line engine, then the respective further high-pressure feed lines 44 'may optionally be of identical design.
  • Like this from the Fig. 3 shows particularly clearly, extends through the substantially circular cylindrical storage housing 36 through a bore 54, which extends several times from the supply port 42 to the pressure tube side end. In an end region facing the pressure tube 34, the bore 54 has its largest diameter and is provided there with an internal thread 56. In the internal thread 56 which is provided in the present end region with an external thread 58 pressure tube 34 is screwed. For tightening the screw 38 formed by the internal thread 56 and external thread 58 has on the one hand the pressure tube 34 a hexagon socket 60 for the attack of a fork wrench and on the other hand, the storage housing 36 two parallel chamfers 62, which serve the attack of another fork wrench or clamping in a jig (see Fig. 1 and 2 ). In the recesses formed by these chamfers 62 engages in each case also the further clamping claw 18 ', which cooperates with their pressure shoulders 64 with counter shoulders 66 on the storage housing 36. Subsequent to the threaded portion, the bore 54 narrows over two small shoulders - to which in connection with the description of Fig. 6 to a discrete storage chamber 68 for storing fuel. Adjoining the storage chamber 68 is a filter section 70, in which the bore is cylindrical with a smaller diameter than in the cylindrical region of the storage chamber 68. Between the cylindrical region of the storage chamber 68 and the filter section 70, the bore 54 has a relatively short conical section in the axial direction. In the filter section 70, a filter 72 and a check valve with throttle passage 74 is arranged, which in conjunction with Fig. 5 to be described in more detail.
  • From the filter section 70 to the feed port 42, the bore 54 is cylindrical and, as in Fig. 5 shown with a relation to the filter section 70 again smaller diameter. This at least approximately coincides with the inner diameter of the high pressure supply lines 44, 44 'match.
  • At this side end, the bore 54 is conically widening designed to form a connection sealing surface 76 for the high-pressure supply line 44 or further high-pressure supply line 44 '. The end of the high pressure supply line 44 and the further high pressure line 44 'is held in a known manner by means of a union nut 78 on a nozzle-like projection of the storage housing 36.
  • How this in particular from a synopsis of Fig. 3 and 4 shows, branches off from the bore 54, between the filter section 70 and the supply port 42, in the radial direction, the connection passage 50 from. The connecting passage 50 expands in its radially outer half conically around a sealing surface 80 of a Wegleitungsanschlusses 82 to form. This further has the clamp 48, which surrounds the storage housing 36 and is provided with a threaded neck 84 formed in the radial direction with internal thread 86. With the internal thread 86, a pressure screw 88 cooperates, which is penetrated by the further high-pressure feed line 44 'and the sealing end portion 90 of the further high-pressure feed line 44' presses sealingly against the sealing surface 80.
  • The volume of the discrete storage chamber 68 preferably corresponds to four to twenty times the volume of the fuel for engine full load injection. It should also be mentioned at this point that the volume of the storage chamber 68 is greater than, preferably two to three times as large as the storage volume for fuel in the pressure pipe 34.
  • The construction of the substantially cylindrical storage housing 36 with the bore 54, which in the one direction widened or narrowed in the other direction, and the formation of the Wegleitungsanschlusses 82 with an attachable to the storage housing 36 clamp 48 is extremely simple, allows the formation of the storage chamber 68, the fixed connection with the pressure tube 34 and the installation of other components, in conjunction with the Fig. 5 and 6 to be discribed.
  • How this in particular the Fig. 5 can be removed, it is in the present case in the filter section 70 of the bore 54 used filter 72 is a rod filter 72 '. This is cylindrical in shape and has distributed along its circumference longitudinal grooves 92, 92 ', which alternately open to the storage chamber 68 and the supply port 42 towards the other, however, are closed, and each other, measured in the axial direction, over a substantial part of the length of the rod filter 72 'overlap. In the region of this overlap, the outer diameter of the rod filter 72 'is slightly smaller than in the two axial end portions 94 and 94', which the longitudinal grooves 92 and 92 'close and with which the rod filter 72' in the filter section 72 of the bore 54 in the manner of Press fit is held. The reduced diameter in the overlap area, together with the bore 54, limits filter gaps 96, which allow the fuel to flow from the longitudinal grooves 92 'into the longitudinal grooves 92, but retain solid particles.
  • Further, in the filter section 70 on the side facing away from the storage chamber 68, the check valve 74 is arranged with throttle passage. A ring-like, flat valve seat 98 of the check valve 74 is on Storage housing 36 formed by a shoulder 98 'of the bore 54 at the feed port side end of the filter section 70. As a valve member 100 is a valve member plate 100 ', on which the throttle passage 102 is formed centrally. The valve member plate 100 'by means of a coil spring 104, which at the other end on the rod filter 72' is supported, held in zurückdrängbarer contact with the valve seat 98. The valve member plate 100 'facing the end of the rod filter 72' forms a stop 106 for the valve member plate 100 'in order to limit its opening movement. The task and operation of the check valve 74 with throttle passage 102, in connection with a possibly small discrete storage chamber 68 is in the WO 2007/009279 A described in detail. On the one hand, rapid flow of fuel into the storage chamber 68 and into the relevant injection valve 10 is ensured and, on the other hand, the dynamic pressure waves are attenuated from one injection process of the injection valve to the injection process of the next injection valve to the extent that all injection events take place under virtually identical conditions. For the sake of completeness, it should also be mentioned here that the design of the storage chamber 68 and the interaction of the storage chambers 68 of the series of injection valves 10 are set forth in detail in the cited document.
  • With dashed lines is in Fig. 5 a variant indicated, which is described below.
  • The axially extending through the pressure tube 34 through longitudinal bore 108 - see in particular Fig. 6 - Is in her the storage enclosure 36 facing end 108 'widened for receiving a flow-limiting valve 110. The seat 112 of this flow restricting valve 110 is formed by a conical configuration of the longitudinal bore 108 at the transition from the cylindrical portion of small diameter in the cylindrical end portion 108 'with a larger diameter. With the seat 112 acting as a valve member punch 114 cooperates, which is biased by a further coil spring 116 in the direction of the open position of the flow control valve 110. In the Fig. 6 the punch 114 is shown in the open position. In the closed position, it engages in the seat 112 and prevents the further inflow of fuel to the associated injection valve 10.
  • On the side facing away from the seat 112 of the stamp 114, due to the force of the other coil spring 116, on a sleeve-shaped piston member 118 into which a shutter member 120 is inserted. The piston element 118 is arranged with a relatively narrow sliding fit 122 of for example 1/100 mm to 3/100 mm in the pressure tube 34 and slidably mounted in the direction of the longitudinal axis 32. The diaphragm element 120 is pressed sealingly in the piston element 118 and has a diaphragm passage 120 'in the axial direction. At the piston element 118 and the diaphragm element 120 facing the end of the punch 114 has this crosswise extending radial grooves 124, which allow the passage of fuel from the storage bracket 68 and the aperture passage 120 'to the associated injection valve 10.
  • The piston element 118 has, on its end face facing the punch 114, a depression 126, with respect to which the diaphragm element 120 is set back and which serves to center the punch 114 engaged therein. On the side facing away from the punch 114, the piston element 118 has a further depression 126 'in order to form a peripheral stop bead 128 radially outward. This cooperates with a stop disk 130, which on the other hand is supported via a spring washer 132 on a support shoulder 134 of the storage housing 36 at this. On the other hand, the pressure tube 34 abuts against the stop disk 130 with its side on this side and presses it against the spring ring disk 132. Relocated opposite this end face, the pressure pipe 34 has, on its radial outer side, a sealing shoulder 136 against which a sealing ring 138 rests. On the other hand, this sealing ring 138 bears against a counter-sealing shoulder 140 of the storage housing 36. When tightening the screw 38 between the accumulator housing 36 and the pressure tube 34 of the sealing ring 138 is pressed sealingly.
  • The cross-section of the orifice passage 120 'is substantially smaller than any other in the inflow to the injection valve 10 acting passages of the flow path for the fuel in the discharge nozzle 30. This means that during normal injection operations, the piston member 118 together with the punch 114 toward the seat 112th However, even with full-load injections, the punch 114 does not come into contact with the seat 112. After completion of an injection process, the punch 114 moves together with the piston member 118, supported by the force of the other coil spring 116, again in the direction of the stop plate 130th
  • However, due to a defect downstream of the flow restriction valve 110, if the pressure drop across the piston member 118 and the orifice member 120 continues for a longer time than a full load injection, the plunger 114 moves to the closed position and prevents further fuel from flowing to the respective injector 10 ,
  • The installation of the flow control valve 110, the filter 72 and the check valve 74 with throttle passage in the discharge nozzle 30 allows a simpler and space-saving design of otherwise optionally equipped with these elements injectors 10. Of course, the discharge nozzle 30 may be formed with only one or none of these elements , In any case, however, it has a storage chamber 68.
  • The two-part construction of the housing of the pressure port 30, namely by a pressure tube 34 and a storage housing 36, allows a simple and inexpensive production of the pressure port 30 with integrated storage chamber 68 and optionally other elements - as stated above -. For the sake of completeness it should be mentioned that a part of the storage chamber 68 can also be formed on the pressure pipe 34.
  • It is also possible to integrally form the shutter member 120 on the piston member 118. The separation of the piston member 118 and punch 114 is in manufacturing to the effect that the concentricity tolerances between on the one hand the outer surface of the piston member 118 and the sealing surface of the punch 114 and on the other hand, the inner surface of the Pressure tube 34 in the region of the sliding fit 122 and the seat 112 barely needs attention.
  • At the in Fig. 5 indicated by dashed lines variant of the inventive device, the connection sealing surface 76 and the thread for the nut 78 are integrally formed on a substantially circular cylindrical connecting part 142, on the other hand inserted into the correspondingly extended in this area running bore 54 of the storage enclosure 36 and by means of a screw 144 at this is attached. The connection part 142 can have engagement surfaces, for example a hexagon, between the threads for the union nut 78 and the screw connection 144 for a tool for tightening or loosening the further screw connection 144.
  • A portion of the communication passage 50 is formed on the connection part 142, and another portion on the storage case 36. To ensure the connection between these sections, the connecting part 142 has a circumferential groove 146.
  • Between this circumferential groove 146 and the wide screw 144 144 sealing shoulders 148 are integrally formed on the connecting part 142 and the storage housing, which bear sealingly against each other.
  • The filter 72 facing end face of the connecting part 142 forms the valve seat 98 for the valve member 100 and the valve member plate 100 '. Between this end face and the circumferential groove 146 there is either a sealing element or a relatively close fit between the connecting part 142 and the storage housing 36 in order to prevent leakage or keep it as small as possible.
  • This variant shown has the advantage that the filter 72 or the bar filter 72 'can be introduced into the filter section 70 from the here end of the storage housing 96. For positioning the filter 72 or the rod filter 72 ', the storage housing 36 at the transition of the bore 54 from the filter section 70 into the storage chamber 68 have a stop bead 150.
  • It is also conceivable to form the storage housing 36 and the pressure tube 34 together in one piece. In this case, the filter section 70 may have a diameter which corresponds to the diameter of the bore of the storage chamber 68 and the bore is closed with a suitably adapted in a simple manner connector 142.
  • Further, the illustrated and described embodiment of filter 72, check valve 74, flow control valve 110, and connection section with supply port 42 and clamp 48, individually and in combination, also suitable for use directly in injectors 10. In this case, occurs in place of the storage housing 36 and optionally the pressure tube 34, the valve housing 22nd
  • Fig. 7 shows a portion of an injector 10 in which the discrete storage chamber 68 is arranged in a known manner in the valve housing 22 of the injection valve 10. In the embodiment shown, the housing body 152 of the valve housing 22 does not have a high pressure sealing surface 24 for the pressure tube 34 of a Pressure port 30, but the high-pressure feed line 44 is connected to the supply port 42, which is integrally formed on a connecting piece 150 of the valve housing 22. This is eingindet in the housing body 152 and with respect to the terminal sealing surface 76 and the supply port 42 is formed the same as that described above and in Fig. 5 shown connection part 142.
  • Through the connecting piece 150 passes, in the direction of the longitudinal axis 28, the bore 54 with the filter portion 70 and the adjoining, in cross-section smaller, leading to the connection sealing surface 76 bore portion 54. The filter portion 70 opens into the molded on the housing body 152 storage chamber 68, wherein in the filter section 70, from the storage chamber 68 side facing, the filter 72 is inserted in the form of a rod filter 72 '. This has, as already described above, the longitudinal grooves 92, 92 ', wherein the longitudinal grooves 92 by means of the axial end portion 94, which sealingly abuts the connecting piece 150, sealed in the direction of the check valve 74 and the supply port 42 out with a close fit practically are. Accordingly, the longitudinal grooves 92 'open toward the check valve 74 and the supply port 42 are sealed off from the storage chamber 68 by the axial end region 94'. As is the case with the embodiments described above. In the embodiment according to Fig. 7 However, the rod filter 72 'in the storage chamber 68 facing the axial end portion 94' in a direction radially outwardly open circumferential groove 154 which via crosswise extending radial bores 156 and a sack-like, to Storage chamber 68 toward open axial bore 158 is fluidly connected to the storage chamber 68. While the longitudinal grooves 92 open into the circumferential groove 154 and end there, the longitudinal grooves 92 'are separated therefrom. For completeness, it should be mentioned that the circumferential groove 154 is radially outwardly covered by the connecting piece 150.
  • The end region of the rod filter 72 'protruding in the direction of the storage chamber 68 via the connecting piece 150, forming a flange 160, has a larger diameter than the part of the rod filter 72' arranged in the filter section 70. The flange 160 rests with its surface facing the connection piece 150 against a front-side counter-shoulder 162 of the connecting piece 150 and is encompassed by a sealing bead 164 of the connecting piece 150 projecting in the axial direction with respect thereto. At the height of the free end of the sealing bead 164, a peripheral shoulder 166 forming the outer diameter is integrally formed on the transparent cross section of the storage chamber 68 on the flange 160. The shoulder 166 and the free end of the sealing bead 164 abut against a sealing ring 168, which on the other hand bears against a sealing shoulder 170 of the housing body 152 and is supported radially outward by the housing body 152 and radially inward by the flange 160. With the free end portion of the flange 160 engages this in the storage chamber 68 forming portion of the axial bore in the housing body 152 a. The preferably rectangular cross-section sealing ring 168 may be made of a soft metal and is compressed when tightening the screw 172 between the connecting piece 150 and the housing body 152, in order to very high pressures to ensure a reliable seal.
  • The valve seat 98 for the valve member plate 100 'designed as a valve member 100 of the check valve 74 is integrally formed on the connecting piece 150. During the transition from the filter section 70 into the section of the bore 54 leading to the connection sealing surface 76, the connecting piece 150 has a circumferential, axial undercut 174 so that a ring-like, axially exposed bead is formed with the annular valve seat 98.
  • The valve member plate 100 'with the centrally arranged throttle passage 102 is held by the coil spring 104 zurückdrängbar on the valve seat 98 in abutment, wherein the coil spring 104 the other end on the rod filter 72' is supported. It engages in a world-side centering recess 176 of the rod filter 72 ', which has a relative to the axial end portion 94 in the direction of the valve member plate 100' projecting, sleeve-shaped projection whose free end forms the stop 106 to limit the opening travel of the valve member plate 100 '.
  • The clamping claw 18 engages with its pressure shoulder 64 on the connecting piece 150 side end face of the housing body 152, which forms the counter-shoulder 66.
  • For the sake of completeness it should be mentioned that the injection valve 10 can otherwise be configured as in the WO 2007/009279 A disclosed. Further, it is also possible the connection piece 150 for feeding a further injection valve 10 according Fig. 4 train. Moreover, it should be mentioned that the discharge nozzle 30 analog Fig. 7 can be trained. When in the Fig. 7 In the embodiment shown, the rod filter 72 'is held between the connecting piece 150 and the sealing ring 168. However, it is also possible, as described above, to fix the rod filter 72 'by means of a press fit in the connecting piece 150.
  • At the in Fig. 8 As shown, the discrete storage chamber 68 is also formed on the housing body 152 of the injection valve 10. The extending in the direction of the longitudinal axis 28, the storage chamber 68 forming bore 54 is sealed at the connection-side end of the housing body 152 by means of a threaded in this sealing plug 178 of the valve housing 22. The end face of the sealing plug 78 facing the storage chamber 68 forms the valve seat 98 for the valve member 100 'of the check valve 74. The throttle passage 102 extends centrally through the valve member plate 100'. The valve member plate 100 'extends on the side facing away from the sealing plug 178. a cylindrical centering projection 180, which is encompassed by this side end of the coil spring 104. Furthermore, this engages in a centering recess 176 of the rod filter 72 'inserted into the bore 54. The valve member plate 100 'facing end face of the rod filter 72' forms the stop 106 to limit the opening movement of the valve member plate 100 '.
  • On the side facing away from the check valve 74, the bar filter 72 'is supported on a circumferential support shoulder 182 in the axial direction. The rod filter 72 ', according to Fig. 8 , is in principle the same education as that according to the Fig. 3 and 5 However, he is in the direction of Seen longitudinal axis 28 may be formed shorter, because it has approximately the same diameter as the storage chamber 68. Thus, it can have more longitudinal grooves 92, 92 'as the embodiment according to the Fig. 3 and 5 to form the same flow area in the narrow filter gaps between the rod filter 72 'and the housing body 152. The rod filter 72 'is preferably held in the housing body 152 by means of a press fit.
  • The sealing plug 178 is provided with a fuel channel 184 which is connected on the one hand to the high-pressure feed line 44 and on the other hand to the further high-pressure feed line 44 'and leads to the check valve 74. It is formed by a blind hole embraced by the annular valve seat 98, a radial bore 190 intersecting with it, and a circumferential connecting groove 192 which is open in the radial direction with respect to the longitudinal axis 28 and opens into the bottom region of the radial bore 190. For the sake of completeness, it should be mentioned that the sealing plug 178 between the connecting groove 192 and its front side facing the storage chamber 68 is held in a relatively tight fit in the housing body 152 in order to prevent or at least minimize leakage from the fuel from the connecting groove 192 to the rod filter 72 ' , Toward the free end of the housing body 152, a seal 194 prevents the escape of fuel to the environment.
  • In the compound groove 192 extends through the housing body 152 through the connecting passage 50, which on both sides, in the radial direction outwardly, flared to form the sealing surfaces 80, to which the corresponding sealing surfaces 80 of High-pressure supply line 44 and further high-pressure supply line 44 'come to the plant. The sealing end portions 90 of these high-pressure feed lines 44, 44 'are held in sealing contact with the sealing surfaces 80 in a known manner by means of pressure screws 88 threaded into the housing body 152.
  • Via the high-pressure feed line 44 fuel supplied to the injection valve 10 can thus flow virtually unhindered to the further high-pressure feed line 44 'and at the same time via the check valve 74 and the rod filter 72' of the storage chamber 68 are supplied. Incidentally, the injection valve 10, for example, as in the WO 2007/009279 A disclosed to be designed. Next in the Fig. 8 shown embodiment are also applied to discharge port 30.
  • Also in the in the Fig. 9 shown example of the injection valve 10, the storage chamber 68 is integrally formed on the housing body 152 of the valve housing 22, from which, in the direction towards the nozzle openings facing away from the end, a connecting hole 196 parallel to the longitudinal axis 28 and with respect to this laterally offset in the housing body 152. Denoted at 198 is the further communication bore leading from the storage chamber 68 to the nozzle openings. The connecting hole 196 is either executed like a blind hole or closed by a plug.
  • Perpendicular to the longitudinal axis 28 and with respect to this laterally offset passes through the housing body 152 through the bore 54. This intersects the connecting hole 196 so that the bore 54 is fluidly connected to the discrete storage chamber 68. The However, bore 54 could also be arranged such that its axis 54 'intersects the longitudinal axis 28.
  • The bore 54 is designed to taper in a stepwise manner, wherein it widens conically from its narrowest part, which forms an inflow section 200, in the direction towards the outside, in order to form a high pressure sealing surface 24. At this is a pressure pipe socket 202 with its Hochdruckgegendichtfläche 40 sealingly. The pressure pipe stub 202 is generally known construction and has no discrete storage chamber 68 in the present case. In principle, however, it can be provided with such a storage chamber and constructed as described above.
  • At the other end, the bore 54 is tightly closed by means of a sealing plug 178 threaded into the housing body 152. For this purpose, a sealing ring 168 acts between the sealing plug 178 and the housing body 152.
  • At one of the sealing plug 178 projecting and integrally formed with this plug shaft 204 of the rod filter 72 'is formed, which is otherwise exactly the same as described above and, for example in the Fig. 3 and 5 shown. Again, the longitudinal grooves 92 in the direction of the check valve 74 and thus to the fuel-supplying pressure pipe stub 202 open and on the other hand closed by the axial end portion 94, which seen in the inflow direction of the fuel, sealingly against the housing body 152 upstream of the flow connection to the connecting hole 196. Accordingly, the through the axial end portion 94 extending through longitudinal grooves 92 ' upstream through the axial end portion 94 'closed.
  • Between the axial end portion 94 and the sealing plug 178, the plug stem 204 is provided with a reduced cross section to produce an adequate flow area to the communication bore 196.
  • The inflow section 200 facing the end face of the rod filter 72 'forms the stop 106 for the valve member plate 100' formed valve member 100 of the check valve 74. It has on its side facing the rod filter 72 on the centering 180, which is encompassed by this side end of the coil spring 104 the latter engaging in the centering recess 176 of the rod filter 72 'and resting against the bottom thereof. By the coil spring 104, the valve member plate 100 'is held back against the valve seat 98 in abutment, which is formed by a step-like constriction of the bore 54. Again, the central throttle passage 102 through the valve member plate 100 'passes, even in the closed position of the check valve 74, the high pressure supply line 44 to the storage chamber 68 continuously. Incidentally, here too, the injection valve 10 corresponding to the WO 2007/009279 A be educated.
  • The operation and effect of the check valve 74 with bypass throttle is the same in all embodiments and as described above.

Claims (10)

  1. A device for injecting highly pressurized fuel into a combustion chamber (14) of an internal combustion engine (12), having an injection valve (10), having a discrete accumulator chamber (68), which is arranged in a housing (36) and is assigned to the injection valve (10), for the fuel, which accumulator chamber (68) is connected by means of a supply line connection (42) of the housing (36) to a high-pressure supply line (44), whereby a further high-pressure supply line (44'), which serves to feed a further injection valve (10), is connected to the housing (36) and the housing (36) has a connecting passage (50) which leads to the further high-pressure line (44'), characterized in that the housing (36) has, at its free end, a supply line connection (42) which is arranged concentrically with respect to the longitudinal axis (32), and the housing (36) is engaged around by a clamp (48) by means of which a further high-pressure supply line (44'), is connected to the housing (36).
  2. The device as claimed in claim 1, characterized in that a flow-restricting valve (110) for the fuel is arranged in the housing (36).
  3. The device as claimed in claim 2, characterized in that the flow-restricting valve (110) has a plunger (114), which is designed for interacting with a seat (112), and a piston element (118) against which the plunger (114), by means of its side facing away from the seat (112), bears in spring-loaded fashion.
  4. The device as claimed in one of claims 1 to 3, characterized in that a non-return valve (74), which acts between the accumulator chamber (68) and the high-pressure supply line (44), is arranged in the housing (36), for the fuel, which non-return valve (74) has a valve member (100) which interacts with a valve seat (98) having a throttle passage (102) for the fuel and a filter (72) for the fuel, which filter (72) is arranged in the housing (36) and forms a stop (106) for limiting the opening movement of the valve member (100).
  5. The device as claimed in claim 4, characterized in that the filter (72) has an edge-type filter (72') which forms the stop (106).
  6. The device as claimed in claim 4 or 5, characterized in that the valve member (100) is designed as a valve member plate (100') with the throttle passage (102).
  7. The device as claimed in one of claims 4 to 6, characterized in that the valve seat (98) is integrally formed on the housing (36).
  8. The device as claimed in one of claims 4 to 7, characterized in that the injection valve (10) has a valve housing (22) with a high-pressure sealing surface (24) which points toward the outside and which surrounds a fuel inlet opening (26) of the valve housing (22), a pressure connector (30) for conducting fuel to the fuel inlet opening (26), an accumulator housing (36) which delimits the discrete accumulator chamber (68) for the fuel, which accumulator housing (36) comprising the supply line connection (42) is at one side connected to the high-pressure supply line (44, 44') and at the other side has a pressure pipe (34) which bears, by means of a high-pressure counterpart sealing surface (40) formed in a free end region, against the high-pressure sealing surface (24), and a clamping device (41) for pressing the high-pressure counterpart sealing surface (40) sealingly against the high-pressure sealing surface (24) engages on the pressure connector (30).
  9. The device as claimed in one of claims 4 to 7, characterized in that the injection valve (10) has an injection valve housing (22) comprising the supply line connection (42), in which injection valve housing (22) the accumulator chamber (68), the non-return valve (74) and the filter (72) are arranged and which is engaged around by the clamp (48).
  10. The device as claimed in claim 9, characterized in that the injection valve housing (22) has a housing body (152), which delimits the accumulator chamber (68), and a connection piece (150) which is arranged on said housing body (152) and which is connected to the high-pressure supply line (44), in which connection piece (150) the non-return valve (74) and the filter (72) are arranged and on which connection piece (150) the valve seat (98) is preferably integrally formed.
EP20080783475 2007-09-13 2008-09-05 Fuel injection device Active EP2188516B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CH14282007 2007-09-13
PCT/CH2008/000375 WO2009033304A1 (en) 2007-09-13 2008-09-05 Fuel injection device

Publications (2)

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EP2188516A1 EP2188516A1 (en) 2010-05-26
EP2188516B1 true EP2188516B1 (en) 2011-10-26

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US (1) US8336524B2 (en)
EP (1) EP2188516B1 (en)
AT (1) AT530761T (en)
BR (1) BRPI0816923A2 (en)
WO (1) WO2009033304A1 (en)

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Also Published As

Publication number Publication date
US8336524B2 (en) 2012-12-25
WO2009033304A1 (en) 2009-03-19
BRPI0816923A2 (en) 2015-03-17
WO2009033304A8 (en) 2010-03-18
US20100170476A1 (en) 2010-07-08
AT530761T (en) 2011-11-15
EP2188516A1 (en) 2010-05-26

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