EP3150839A1 - Kraftstoffeinspritzventil - Google Patents

Kraftstoffeinspritzventil Download PDF

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Publication number
EP3150839A1
EP3150839A1 EP16190307.5A EP16190307A EP3150839A1 EP 3150839 A1 EP3150839 A1 EP 3150839A1 EP 16190307 A EP16190307 A EP 16190307A EP 3150839 A1 EP3150839 A1 EP 3150839A1
Authority
EP
European Patent Office
Prior art keywords
control chamber
fuel
moveable plate
sealing surface
fuel injector
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
EP16190307.5A
Other languages
English (en)
French (fr)
Other versions
EP3150839B1 (de
Inventor
Thierry Thibault
Nicolas Rodier
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.)
Delphi International Operations Luxembourg SARL
Original Assignee
Delphi International Operations Luxembourg SARL
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 Delphi International Operations Luxembourg SARL filed Critical Delphi International Operations Luxembourg SARL
Publication of EP3150839A1 publication Critical patent/EP3150839A1/de
Application granted granted Critical
Publication of EP3150839B1 publication Critical patent/EP3150839B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • 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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0028—Valves characterised by the valve actuating means hydraulic
    • F02M63/0029—Valves characterised by the valve actuating means hydraulic using a pilot valve controlling a hydraulic chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—Three-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus

Definitions

  • the present invention relates to a fuel injector with an improved valve control arrangement for positioning a valve needle of a fuel injector in a position whereby injection of fuel occurs, and in a position whereby injection of fuel is prevented.
  • the present invention relates to a fuel injector with a valve control arrangement which utilises a moveable plate to control the flow of high pressure fuel between a high pressure fuel supply and an injection valve needle control chamber.
  • valve control arrangement of this type is described in EP 1 163 440 .
  • a thrust surface provided at the end of the valve needle that is distal from the valve seat can be subjected to a force resulting from pressurised fuel within the needle control chamber acting against it and a medial thrust surface provided between the distal and proximal ends of the valve needle can be subjected to a force resulting from pressurised fuel within an associated annular chamber in the nozzle body.
  • Fuel from a high pressure fuel supply source can flow into the valve needle control chamber through an inlet orifice (INO) in the inlet passage.
  • Fuel can flow out from the valve needle control chamber to a low pressure reservoir or drain through an outlet orifice, commonly referred to as a 'spill orifice' (SPO), when the discharge valve is opened by a solenoid actuator.
  • Fuel flows into the annular chamber within the nozzle body from the high pressure fuel supply source and flows out from the chamber through injection orifices which are opened and closed as the valve needle is raised or lowered respectively.
  • the discharge valve In operation, to raise the valve needle and hence open the injection orifices, the discharge valve is opened, under the direct control of the solenoid actuator.
  • the fuel within the valve needle control chamber is then able to flow out to the low pressure drain via the SPO. Because the INO is present in the high pressure fuel supply line to the valve needle control chamber the pressure of the fuel within the valve needle control chamber is reduced and thus the downwards force applied to the valve needle, as a result of the fuel acting upon the distal thrust surface, is reduced. High pressure fuel is still acting on the medial thrust surface of the valve needle and the resulting upwards force applied to the valve needle thrust surface is greater than the downwards force applied to the valve needle and thus the valve needle starts to move upwards.
  • the fuel within the chamber in the nozzle body flows out to an engine cylinder, which is at a relatively low pressure, and thus the fuel pressure within the annular chamber in the nozzle body reduces.
  • the upwards force acting on the valve needle reduces.
  • the upwards force acting on the thrust surface is still greater than the downwards force applied to the valve needle and thus the valve needle remains in a raised position and fuel injection through the injection orifices continues.
  • the discharge valve In order to lower the valve needle, close the injection orifices and thus cease the injection of fuel, the discharge valve is moved to a closed position. This is achieved by stopping the supply of electrical current to the solenoid and under the direct action of a helical compression spring acting on the discharge valve member. This closes the outlet from the valve needle control chamber to the low pressure drain and thus, since high pressure fuel is still being supplied to the needle control chamber, via the INO, the pressure of fuel within the needle control chamber is raised. The downwards force applied to the valve becomes greater than the upwards force and thus the valve needle moves downwards.
  • This prior art valve control arrangement utilises a hydraulically balanced discharge valve. It is necessary to use a hydraulically balanced discharge valve because a small solenoid actuator is used to control movement of the discharge valve and such an actuator is not able to generate sufficient force to close an unbalanced valve against the high pressure of the fuel within the valve needle control chamber acting against it. It is desired to use a small solenoid actuator as this enables the actuator to be placed within the body of the injector. Furthermore, there is a cost reduction associated with the use of a small actuator.
  • a disadvantage of hydraulically balanced valves is that they suffer from static leak. This is leak across the discharge valve from the high pressure side, i.e. the valve needle control chamber, to the low pressure drain and is exacerbated by the high pressures and temperatures of the fuel to which the discharge valve is subjected. This static leak requires a higher pump capacity and results in wasted energy as pressurised fuel escapes to the low pressure drain.
  • the prior art control arrangement suffers from dynamic fuel leakage when the valve needle is raised.
  • the dynamic leakage occurs between the high pressure fuel inlet and the low pressure reservoir or drain when the discharge valve is open.
  • the dynamic leakage is disadvantageous for the same reasons set forth above in respect to static leakage.
  • the inlet orifice and the spill orifice are present in the valve control arrangement of the prior art to enable the greatest closing speed of the valve needle, i.e. the shortest delay between the discharge valve being closed and the pressure of fuel within the valve needle control chamber reaching a level at which the downwards force applied to the valve needle is greater than the force applied upwards, and to enable the greatest opening speed of the valve needle, i.e. the shortest delay between the discharge valve being opened and the pressure of fuel within the valve needle control chamber reducing to a level whereby the upwards force applied to the valve needle is greater than the downwards force applied to the needle.
  • valve needle control chamber In order to have the greatest closing speed for the valve needle it is necessary to fill the valve needle control chamber as quickly as possible.
  • the ideal situation would be to have an unrestricted fuel inlet, i.e. no inlet orifice and a heavily restricted fuel outlet, i.e. a small spill orifice.
  • a high opening speed for the valve needle it is also desirable to have a high opening speed for the valve needle and this requires that the valve needle control chamber is emptied as quickly as possible through the outlet passage.
  • an unrestricted fuel outlet i.e. no spill orifice and a heavily restricted fuel inlet, i.e. a small inlet orifice.
  • the prior art control arrangement is limited by suffering from undesirable levels of static and dynamic leakage and from having a relatively long delay time between actuation of the discharge valve and movement of the valve needle.
  • the present invention provides a fuel injector for an internal combustion engine, in particular a compression ignition internal combustion engine, the fuel injector comprising: a fuel injection valve having an injection valve member moveable, in use, under the influence of fuel pressure within a control chamber acting upon it, between a closed position and an open position; a high pressure fuel supply channel to the control chamber; a fuel outlet channel leading from the control chamber to a low pressure reservoir or drain; an actuator operable to open and close a discharge valve located in the fuel outlet channel; a moveable plate located in the control chamber and arranged to move into and out of contact with a sealing surface of the control chamber; a spill orifice provided in the moveable plate and arranged to communicate with the fuel outlet channel when the moveable plate is located in contact with the sealing surface of the control chamber, the spill orifice defining a restricted flow path for fuel to flow out of the control chamber to the fuel outlet channel; and an inlet orifice provided in the moveable plate and arranged to communicate with the high pressure fuel supply channel when the moveable plate is located
  • inlet and spill orifices in the moveable plate enables significantly smaller inlet and outlet orifices to be used in comparison to the prior art. Consequently, the present invention results in a significant reduction of dynamic leakage as low pressure fuel flows out of the control chamber during an emptying phase of the control chamber.
  • the moveable plate In use, when the moveable plate is in contact with the sealing surface of the control chamber and the discharge valve is open, fuel flows from the high pressure fuel supply channel into the control chamber through the inlet orifice in the moveable plate, and fuel flows out of the control chamber through the spill orifice in the moveable plate and through the fuel outlet channel to the low pressure reservoir or drain.
  • the provision of the inlet orifice in the moveable plate therefore allows a restricted flow of fuel to enter the control chamber during the emptying phase of the control chamber.
  • the relative sizes of the inlet and spill orifices can advantageously be selected to enable a smooth and controlled lifting of the injection valve member.
  • the moveable plate is preferably configured such that one or more additional fluid passages are defined between the control chamber and the high pressure fuel supply channel when the moveable plate is moved out of contact with the sealing surface of the control chamber.
  • the additional fluid passages may be defined at least in part by formations such as flats or grooves in a periphery of the moveable plate.
  • the additional fluid passages advantageously enable fuel from the high pressure fuel supply channel to enter the control chamber bypassing the inlet orifice.
  • the rate of filling of the control chamber is not governed exclusively by the size of the inlet orifice.
  • the inlet orifice can therefore be made smaller without compromising the rate at which the control chamber is filled, and hence the fuel injector can terminate an injection event rapidly despite having a small inlet orifice.
  • the high pressure fuel supply channel upstream of the additional fluid passage(s) is substantially unrestricted. This allows a substantially unrestricted flow of fuel to enter the control chamber via the additional fluid passages resulting in a very rapid termination of an injection event.
  • the injector may be configured such that, in use, when the moveable plate moves out of contact with the sealing surface of the control chamber, fuel flows from the high pressure fuel supply channel into the control chamber through the additional fluid passage(s) and through the inlet orifice and spill orifice in the moveable plate.
  • a plurality of flow paths for high pressure fuel entering the control chamber are therefore provided thus allowing faster termination of an injection event in comparison to the prior art.
  • the fuel injector preferably comprises bias means, for example in the form of a helical spring, in the control chamber for biasing the moveable plate into contact with the sealing surface of the control chamber.
  • the bias means may advantageously assist with returning the moveable plate into sealing contact with the sealing surface of the control chamber, and assist with retaining the moveable plate in sealing contact with the sealing surface.
  • the inlet orifice is located substantially centrally in the moveable plate. This advantageously provides an even force distribution on the plate and prevents the plate from twisting in the control chamber.
  • the spill orifice is preferably laterally offset from the inlet orifice.
  • the moveable plate may comprise a substantially central recess via which the inlet orifice communicates with the high pressure fuel supply channel when the moveable plate is in contact with the sealing surface of the control chamber.
  • the substantially central recess may be defined by a circular inner wall of the moveable plate.
  • the inner wall preferably comprises a sealing surface arranged to seal against the sealing surface of the control chamber when the moveable plate is in contact with the sealing surface of the control chamber.
  • the size of the central recess may be selected to achieve an appropriate force differential across the moveable plate to retain the plate in sealing contact with the sealing surface of the control chamber during the emptying phase of the control chamber.
  • the moveable plate may comprise an annular recess via which the spill orifice communicates with the fuel outlet channel when the moveable plate is in contact with the sealing surface of the control chamber.
  • the annular recess and the substantially central recess may be substantially concentric.
  • the annular recess may be defined between a circular outer wall of the moveable plate and the circular inner wall of the moveable plate.
  • the outer wall preferably comprises a sealing surface arranged to seal against the sealing surface of the control chamber when the moveable plate is in contact with the sealing surface of the control chamber.
  • the size of the annular recess may be selected to achieve an appropriate force differential across the plate when the discharge valve is closed to cause the plate to move out of sealing contact with the sealing surface of the control chamber.
  • FIG 1 shows a fuel injector 10 according to an embodiment of the present invention.
  • the fuel injector 10 comprises an injector valve 12 comprising a valve needle 14 located within an injector nozzle body 16.
  • the injector nozzle body 16 is connected to a lower part 18 of an injector housing. Only a lower part 18 of the injector housing and upper parts of the valve needle 14 and injector nozzle body 16 are shown in Figure 1 .
  • a lower end (not shown) of the valve needle 14 controls the flow of fuel out of the injector 10 as the valve needle 14 moves up and down in the injector nozzle body 16 between open and closed positions, as described by way of background.
  • Movement of the valve needle 14 is controlled by fuel pressure within a control chamber 20.
  • the control chamber 20 is defined within the injector nozzle body 16 at an upper end 21 of the valve needle 14.
  • the control chamber 20 is supplied with high pressure fuel via a high pressure fuel supply channel 22 defined in the injector housing part 18.
  • a fuel outlet channel 24 is also defined in the injector housing part 18 and is arranged to convey fluid which empties from the control chamber 20 to a low pressure reservoir or drain (not shown). Accordingly, the control chamber 20 is filled via the high pressure fuel supply channel 22 and emptied via the fuel outlet channel 24.
  • the arrows 23 and 25 in Figure 1 indicate the direction of fuel flow into and out of the control chamber via the high pressure fuel supply channel 22 and the fuel outlet channel 24 respectively.
  • filling the control chamber 20 with high pressure fuel causes a downward force to act on the upper end 21 of the valve needle 14. This causes the needle 14 to move downwards in the nozzle body 16 to terminate an injection event. Conversely, emptying the control chamber 20 causes a reduction in pressure in the control chamber 20 resulting in the needle 14 lifting to commence an injection event.
  • a discharge valve 26 is provided in the fuel outlet channel 24.
  • the discharge valve 26 is operated by a solenoid actuator (not shown).
  • the discharge valve 26 is opened to commence an injection event, which causes fuel to exit the control chamber 20 via the fuel outlet channel 24, resulting in the valve needle 14 lifting in the nozzle body 16.
  • the discharge valve 26 is closed to terminate an injection event, which causes the control chamber 20 to be re-filled with high pressure fuel, resulting in the lower end (not shown) of the valve needle 14 re-engaging with a valve seat (not shown) at a lower end of the nozzle body 16.
  • a moveable plate 28 is provided inside the control chamber 20.
  • the moveable plate 28 is substantially circular, and is made from metal.
  • the material from which the moveable plate is made may be a high performance steel (such as high speed steel) which has high wear resistance and hardness up to high temperatures (around 500°C).
  • the moveable plate 28 comprises a first side 30 and a second side 32.
  • the first side 30 is an upper side and the second side 32 is a lower side.
  • the first (upper) side 30 faces a sealing surface 34 of the control chamber 20, whilst the second (lower) side 32 faces the upper end 21 of the valve needle 14.
  • the sealing surface 34 of the control chamber 20 is provided by a portion of a lower end surface 35 of the injector body 18.
  • the sealing surface 34 is highly polished such that it has a mirror finish.
  • a helical spring 36 is provided inside the control chamber 20 between the second (lower) side 32 of the plate 28 and the upper end 21 of the valve needle 14.
  • the second (lower) side 32 of the moveable plate 28 is substantially flat.
  • the spring 36 is arranged to bias the upper side 30 of the moveable plate 28 into sealing contact with the sealing surface 34 of the control chamber 20.
  • An inlet orifice 38 and a spill orifice 40 are defined in the moveable plate 28.
  • Each orifice 38, 40 extends through the full thickness of the plate 28 between the first and second sides 30, 32 of the plate 28.
  • the inlet orifice 38 is located substantially centrally in the plate 28, whilst the spill orifice 40 is laterally offset from the inlet orifice 38.
  • the inlet orifice 38 is in fluid communication with the high pressure fuel supply channel 22, and provides a restricted flow path for fuel entering the control chamber 20.
  • the spill orifice 40 is in fluid communication with the fuel outlet channel 24, and provides a restricted flow path for fuel exiting the control chamber 20.
  • a spill volume 41 is defined in the fuel outlet channel 24 between the discharge valve 26 and the spill orifice 40.
  • the inlet orifice 38 communicates with the high pressure fuel supply channel 22 via a substantially central recess 42 defined in the first (upper) side 30 of the moveable plate 28.
  • the central recess 42 is substantially circular and defined by a substantially circular inner wall 44 of the moveable plate 28.
  • An upper surface 46 of the inner wall 44 defines a sealing surface for sealing against the sealing surface 34 of the control chamber 20.
  • the central recess 42 defines a circular surface 48 on the first (upper) side 30 of the moveable plate 28 against which the force of the high pressure fuel in the fuel supply channel 22 acts when the moveable plate 28 is sealed against the sealing surface 34 of the control chamber 20.
  • the spill orifice 40 communicates with the fuel outlet channel 24 via an annular recess 50 defined in the first (upper) side 30 of the moveable plate 28.
  • the annular recess 50 is defined between the inner wall 44 and a substantially circular outer wall 52 of the moveable plate 28.
  • the inner and outer walls 44, 52 are substantially concentric.
  • An upper surface 54 of the outer wall 52 defines a sealing surface for sealing against the sealing surface 34 of the control chamber 20.
  • the annular recess 50 defines an annular surface 56 on the first (upper) side 30 of the moveable plate 28 against which the force of the high pressure fuel between the spill orifice 40 and discharge valve 26 acts when the moveable plate 28 is sealed against the sealing surface 34 of the control chamber 20 and the discharge valve 26 is closed.
  • the moveable plate 28 comprises a generally circular peripheral surface 58, which is provided with flats 60a, 60b and grooves 62a, 62b.
  • the peripheral surface 58 of the plate 28 includes a pair of diametrically opposed flat surfaces 60a, 60b, and a pair of diametrically opposed grooves 62a, 62b.
  • the flats 60a, 60b and grooves 62a, 62b provide additional fluid flow paths between the peripheral surface 58 of the plate 28 and side wall 64 (see Figure 1 ) of the control chamber 20 for high pressure fluid entering the control chamber 20.
  • this shows the fuel injector 10 at rest, i.e. prior to commencing an injection event, or after termination of an injection event.
  • the discharge valve 26 is closed, and the control chamber 20 is full of high pressure fuel.
  • the spill volume 41 between the discharge valve 26 and the spill orifice 40 is also full of high pressure fuel.
  • the forces acting on both sides of the moveable plate 28 due to the pressure of fuel in the control chamber 20 and fuel supply and outlet channels 22, 24 are substantially equal, and the moveable plate 28 is maintained in sealing contact with the sealing surface 34 of the control chamber 20 by the helical spring 36.
  • the discharge valve 26 is opened. Referring now to Figure 3 , opening the discharge valve 26 causes a sudden large pressure drop in the spill volume 41 downstream of the spill orifice 40 as the fuel in the spill volume 41 flows past the discharge valve 26 (shown in Figure 1 ) to the low pressure reservoir or drain.
  • the control chamber 20 then begins to empty via the spill orifice 40.
  • the pressure acting on the upper end 21 of the nozzle needle 14 reduces, and a net upward force acts on the nozzle needle 14 causing the needle 14 to lift inside the nozzle body 16 to commence injection of fuel through the outlets at the lower end of the nozzle body 16 (not shown).
  • the moveable plate 28 remains sealed against the sealing surface 34 of the control chamber 20 during this nozzle opening phase, due to the spring biasing force and due to the relative forces acting on the respective first and second sides 30, 32 of the moveable plate 28.
  • the fuel pressure in the control chamber 20 acts over a larger area of the second (lower) side 32 of the moveable plate 28 compared to the fuel pressure in the high pressure fuel supply channel 22, which acts against the relatively small circular surface 48 of the central recess 42. Consequently, a net upward force on the moveable plate 28 maintains the plate 28 in sealing contact with the sealing surface 34 of the control chamber 20 during emptying on the control chamber 20.
  • the discharge valve 26 (shown in Figure 1 ) is closed. This causes the spill volume 41 between the spill orifice 40 and the discharge valve 26 to fill with high pressure fuel.
  • the accumulation of high pressure fuel in the sealed annular recess 50 exerts a downwards force on the annular surface 56 of the moveable plate 28. This initially causes the forces acting on both sides 30, 32 of the moveable plate 28 to equalise, bringing the plate 28 into equilibrium.
  • a net downward force acts on the moveable plate 28 causing the plate 28 to move downwardly.
  • the high pressure fuel entering the control chamber 20 via the additional flow paths 65 is able to bypass the inlet orifice 38.
  • the rate of filling of the control chamber 20, and hence the rate of termination of the injection event is not governed exclusively by the size of the inlet orifice 38. Consequently, the provision of the inlet orifice 38 in the moveable plate 28 allows a much smaller inlet orifice 38 to be used than in the prior art, whilst at the same time achieving a more rapid filling of the control chamber 20 and hence a more rapid termination of an injection event.
  • the spill orifice 40 can also be made smaller. This is because the smaller inlet orifice 38 results in a more restricted flow of fuel entering the control chamber 20 during emptying of the control chamber 20 to initiate an injection event (as shown in Figure 3 ) and hence a more restricted spill orifice 40 can be used without compromising the rate at which the control chamber 20 is emptied. Hence a rapid lifting of the nozzle needle 14 is still achieved.
  • the moveable plate 28 provided with inlet and outlet orifices 38, 40 therefore allows both the inlet and outlet orifices 38, 40 to be made smaller in comparison to prior art injectors, whilst still achieving rapid initiation of an injection event and even faster termination of the injection event.
  • the relatively small inlet and outlet orifices 38, 40 results in a significant reduction of dynamic leakage during emptying of the control chamber 20, as shown in Figure 3 , since the fuel flow path from the high pressure fuel supply channel 22 to the fuel outlet channel 24 via the control chamber 20 is more restricted than in the prior art.
  • the additional flow paths 65 need not be defined by the particular arrangement of flats 60a, 60b and grooves 62a, 62b shown in Figure 2 . Any number of flats or grooves alone or in combination may be used, or indeed any other suitable formations in the outer periphery 58 of the moveable plate 28 may provide the additional flow paths 65.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
EP16190307.5A 2015-09-29 2016-09-23 Kraftstoffeinspritzventil Not-in-force EP3150839B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GBGB1517148.1A GB201517148D0 (en) 2015-09-29 2015-09-29 Fuel injector

Publications (2)

Publication Number Publication Date
EP3150839A1 true EP3150839A1 (de) 2017-04-05
EP3150839B1 EP3150839B1 (de) 2018-05-23

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP16190307.5A Not-in-force EP3150839B1 (de) 2015-09-29 2016-09-23 Kraftstoffeinspritzventil

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EP (1) EP3150839B1 (de)
GB (1) GB201517148D0 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019016399A1 (de) * 2017-07-20 2019-01-24 Liebherr-Components Deggendorf Gmbh Vorrichtung zum steuern eines injektors
GB2587015A (en) * 2019-09-13 2021-03-17 Delphi Tech Ip Ltd Fuel injector

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003071122A1 (de) * 2002-02-22 2003-08-28 Crt Common Rail Technologies Ag Brennstoffeinspritzventil für verbrennungskraftmaschinen
US20100301143A1 (en) * 2009-06-02 2010-12-02 Denso Corporation Fuel injection device
EP2628939A1 (de) * 2012-02-20 2013-08-21 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102012204837A1 (de) * 2012-03-27 2013-10-02 Continental Automotive Gmbh Injektorbaugruppe für ein Einspritzventil und Einspritzventil

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003071122A1 (de) * 2002-02-22 2003-08-28 Crt Common Rail Technologies Ag Brennstoffeinspritzventil für verbrennungskraftmaschinen
US20100301143A1 (en) * 2009-06-02 2010-12-02 Denso Corporation Fuel injection device
EP2628939A1 (de) * 2012-02-20 2013-08-21 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102012204837A1 (de) * 2012-03-27 2013-10-02 Continental Automotive Gmbh Injektorbaugruppe für ein Einspritzventil und Einspritzventil

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019016399A1 (de) * 2017-07-20 2019-01-24 Liebherr-Components Deggendorf Gmbh Vorrichtung zum steuern eines injektors
US11608805B2 (en) 2017-07-20 2023-03-21 Liebherr-Components Deggendorf Gmbh Device for controlling an injector
GB2587015A (en) * 2019-09-13 2021-03-17 Delphi Tech Ip Ltd Fuel injector
GB2587015B (en) * 2019-09-13 2021-12-08 Delphi Tech Ip Ltd Fuel injector

Also Published As

Publication number Publication date
GB201517148D0 (en) 2015-11-11
EP3150839B1 (de) 2018-05-23

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