EP1836385A1 - Fuel injection valve with pressure gain - Google Patents

Fuel injection valve with pressure gain

Info

Publication number
EP1836385A1
EP1836385A1 EP05798800A EP05798800A EP1836385A1 EP 1836385 A1 EP1836385 A1 EP 1836385A1 EP 05798800 A EP05798800 A EP 05798800A EP 05798800 A EP05798800 A EP 05798800A EP 1836385 A1 EP1836385 A1 EP 1836385A1
Authority
EP
European Patent Office
Prior art keywords
control valve
pressure
injection valve
piston
fuel injection
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
EP05798800A
Other languages
German (de)
French (fr)
Other versions
EP1836385B1 (en
Inventor
Marco Ganser
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
Original Assignee
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.)
Filing date
Publication date
Application filed by Ganser Hydromag AG filed Critical Ganser Hydromag AG
Publication of EP1836385A1 publication Critical patent/EP1836385A1/en
Application granted granted Critical
Publication of EP1836385B1 publication Critical patent/EP1836385B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification

Definitions

  • the present invention relates to a fuel injection valve for intermittent fuel injection into the combustion chamber of an internal combustion engine according to claim 1.
  • a fuel injector in which an electromagnetic actuator drives a 3/2 or ⁇ / 3-way valve.
  • an intensifier piston designed as a differential piston and the supply of fuel into a fuel high-pressure space adjacent to an injection valve seat are controlled by means of this control valve such that a pressure-controlled or stroke-controlled injection takes place.
  • the control valve member must each put a long way back to get from one switching position to another switching position. Typically, this path is several 1/10 mm.
  • the multiple injection with such control valves is very demanding and the construction de 's fuel injector extremely costly.
  • the control valve is designed as a flat seat valve.
  • Flat seat valves have the property that they release large flow cross sections at a very small stroke.
  • the control valve member of a fuel injector according to the invention requires a stroke of only about 2/100 to 10/100 mm.
  • the control of the control valve member can thus also be effected by means of a piezoelectric actuator.
  • multiple injections are feasible without problems; this in the use of piezoelectric actuators as well as in the use of very fast electromagnetic actuators.
  • Fig. 1 in a longitudinal section a first
  • FIG. 2 also in longitudinal section a part of that shown in FIG
  • FIG. 4 in the same representation as FIG. 2, a second embodiment of a fuel injection valve according to the invention
  • FIG. 6 shows that shown in FIG
  • Embodiment in a longitudinal section which is perpendicular to the longitudinal section shown in Figure 5 and wherein the control valve member is in the closed position;
  • FIG. 7 in the same representation as FIG. 2, a fourth embodiment of an injection valve according to the invention with a stepped intensifier piston;
  • FIG. 8 in the same representation as Figs. 5 and 6 one of those shown there Embodiment similar further embodiment with a different mechanical structure
  • FIG. 9 shows a control valve seat body of FIG.
  • a fuel injector shown in FIG. 1 is intended to inject fuel intermittently into a generally known combustion chamber of an internal combustion engine. It has a substantially circular cylindrical, stepped housing 10, on the front side - on that side with the lower
  • Valve seat member 12 is fixed by means of a cap nut 14.
  • Valve seat member 12 and the cap nut 14 coincide in the present example and is designated 16. 0
  • Cap nut could also be desaxed or in one
  • valve seat element 12 facing away from the end portion of the housing 10 is in a recess 18 a
  • actuator assembly 20 is arranged.
  • a piezoelectric actuator 22 of the actuator assembly 20 is intended to drive a control valve 24. This connects in open position a control pressure inlet 26 for the fuel on the housing 10 with the control pressure side of
  • a differential piston formed booster piston 28 As a differential piston formed booster piston 28.
  • the high pressure side of the booster piston 28 is provided with a in the valve seat member 12 arranged high-pressure fuel chamber 30 is connected, which adjoins a formed on the valve seat member 12, a cone-shaped like injection valve seat 32.
  • a needle-like injection valve member 34 is arranged centrally movable relative to the axis 16 and in the direction of this axis 16, which is intended on the one hand to cooperate with the injection valve seat 32, and the other piston-like limits a cylinder chamber 36 connected to the control pressure inlet 26.
  • the control pressure - or feed pressure - is about 200 - 1600 bar.
  • the control valve 24, the booster piston 28 and all necessary connection passages are arranged in the housing 10, or formed thereon.
  • the housing 10 is shown in one piece; However, it may be composed of several parts in order to easily form the necessary recesses and connecting passages in the production can.
  • the piezoelectric actuator 22 is accommodated in an actuator housing 38, which rests on the one hand on a shoulder 40 of the recess 18 on the housing 10 and on the other hand by means of a sleeve-shaped fastening screw 42, which is threaded into the housing 10 and is supported on a support shoulder 44 of the actuator 38, held in abutment against the shoulder 40.
  • Electrical control lines, via which the actuator 22 is driven in a known manner by a controller forth, are designated 46.
  • the actuator 22 has an actuator shaft 48, which upon excitation or de-excitation of the actuator 22 in the direction of the axis 16 about a stroke of about 0.02 - 0.1 mm in the one or the opposite direction is moved.
  • the recess 18 has adjacent to the
  • Low pressure outlet port 54 is connected to the housing 10, of which by leakage or the. Control caused loss of fuel is directed into a fuel storage tank.
  • a circular cylindrical control valve chamber 56 is recessed centrally to the axis 16, in which a disc-shaped control valve member 58 is movably received in the direction of the axis 16. From the control valve chamber 56 to the low pressure chamber 50 extends a guide passage 60 which is penetrated in close sliding fit by an actuating shaft 62 which rests on the one hand on the control valve member 58 and on the other hand at the free end of the Aktuatorschafts 48. Further, the control valve chamber 56 is connected to the low pressure chamber 50 via a throttle channel 64.
  • planar control valve seat On the side facing away from the operating shaft 62 of the control valve member 58 of the control valve chamber 56 is formed by a formed on the housing 10, planar control valve seat
  • Control valve seat 66 facing side is also formed with high precision flat.
  • the control valve member 58 is located in one of Control valve seat 66 spaced open position, whereas it is shown in Fig. 1 in its voltage applied to the control valve seat 66 closing position.
  • an annular inlet groove 68 extending around the axis 16 is formed in the housing 10 and is open in the direction of the control valve chamber 56 and closed by the control valve member 58 when the control valve 24 is closed.
  • the inlet groove 68 is fluidly connected to the control pressure inlet 26 via a control pressure channel 70 in the housing 10. Further, it is formed with the largest possible radial outer diameter, so that when opening the control valve 24 very quickly a large flow cross section is free.
  • a circular cylindrical piston guide chamber 74 is formed, in which a control pressure side piston part 28 'of the booster piston 28 is received and guided in close sliding fit in the direction of the axis 16 back and forth.
  • the free cross sections of the control pressure channel 70 and the connecting channel 78 are much larger than the narrowest cross section of the throttle channel 64.
  • the booster piston 28 on its control-pressure side end a projecting stop lug 88, which prevents the booster piston 28 with its side face this side of the housing 10 can create.
  • the piston part 28 'in cross-section smaller, also circular cylindrical trained piston part 28''away which passes through a low-pressure side portion 82 of the piston guide chamber 74 and is guided on the wall of a low-pressure side portion 82 away cylindrical recess in close sliding fit.
  • the low-pressure-side part 82 of the piston guide chamber 74 is permanently connected to the low-pressure outlet 54 via a low-pressure passage 86 leading into the low-pressure passage 52.
  • the check valve 92 designed as a spring-loaded ball valve allows fuel to flow from the control pressure inlet 26 into the piston output space 84, but prevents fuel from flowing out of the piston output space 84 into the control pressure branch line 90.
  • the formed by a recess in the valve seat member 12 fuel high-pressure space 30 to the axis 16 is stepped circular cylindrical and limited on the one hand by the injection valve seat 32 and on the other hand by the end face of the housing 10.
  • a sleeve-like design needle guide element 94 is arranged, the on the one hand via three radially outwardly projecting ribs 94 'on Ventililsitzelei ⁇ ent 12 is centered supported and on the other hand radially inwardly the this side end portion of the injection valve member 34 is guided in tight sliding fit.
  • the ribs 94 ' may also be omitted (guidance of the needle guide element 94 would be assumed by ribs 100, see below).
  • the needle guide element 94 circumferentially bounded the cylinder chamber 36 and is under the force of a closing spring 96 sealingly against the end face of the housing 10.
  • the closing spring 96 is supported on the one hand at the free end of the needle guide element 94 and on the other hand via an annular disc 98 and a support element 98 'in a known manner on the injection valve member 34 from.
  • the closing spring 96 presses the fuel injection valve member 34 in the direction against the injection valve seat 32. Between the valve seat member 12 and the needle guide member 94, the closing spring 96 and the injection valve member 34 remains a large flow area for the fuel free.
  • the injection valve member 34 has in the radial direction three projecting guide ribs 100, via which it is guided on the valve seat member 12, in the region of the narrower in cross section part of the high-pressure fuel chamber 30, in the axial direction. In the region between the three guide ribs 100, a large flow cross-section is present so that fuel can flow unhindered to the injection valve seat 32.
  • Nozzle passages 102 are excluded, by which at an injection of the fuel is injected under very high pressure in the combustion chamber.
  • control valve 34 designed as a flat seat valve acts as a 2/2-way valve.
  • Fuel injection valve the same reference numerals are used for equivalent or identical parts, as in connection with the embodiment shown in FIGS. 1-3. Furthermore, only the differences from the already described embodiment will be discussed below.
  • a circular cylindrical recess is formed in the region of the control valve seat 66, centric to the axis 16, which forms an outlet opening 104 encompassed by a distance from the inlet groove 68.
  • This is flow-connected to the piston drive chamber 76 via a further connecting channel 78 '.
  • the injection valve member 34 is again plate-shaped or disk-shaped, but now with the
  • control valve member 58 In the closed position, the control valve member 58 bears sealingly against an annular sealing surface of the control valve seat 66 which adjoins the inlet groove 68 radially on the one hand, and against a further annular sealing face of the control valve seat 66 between the inlet groove 68 and the outlet opening 104. 4, the control valve member 58 releases the connection from the inlet groove 68 to the connection channel 78 and further connection channel 78 '.
  • the control valve member 58 has on the side facing away from the control valve seat 66 an annular sealing shoulder 106 which protrudes in the axial direction with respect to the adjoining operating shaft 62 in the radial direction and with respect to the remaining part of the control valve member 58.
  • the sealing shoulder 106 is in the open position of the control valve 24 sealingly on the housing 10.
  • the guide passage 60 in which the operating shaft 62 is guided in sliding fit, is widened in its, the control valve chamber 56 facing end portion to a circumferential relief groove 108, which via a discharge channel 64 'permanently - and without throttle - with the low-pressure chamber 50 and thus the Low pressure outlet 54 is connected.
  • FIGS 5 and 6 show an embodiment of a fuel injection valve according to the invention, in which this problem is solved and which also allows the control of the control valve 24 by means of an electromagnetic actuator 22; this by at least partial compensation of the forces caused by the pressure differences forces on the control valve member 58th
  • a shaft 62 ' At the disk-like control valve member 58 is on the side facing away from the operating shaft 62, a shaft 62 ', preferably integrally arranged, which is guided in a shaft passage 110 in the housing 10 in close sliding fit and carries in its free end a compensating piston 112.
  • the compensation piston 112 is guided in a cylinder recess 114, also in close sliding fit.
  • the cylinder recess 114 and the compensating piston 112 delimit, on the side of the compensation piston 112 facing the control valve member 58, a compensation pressure chamber 116, which is flow-connected to the control pressure channel 70 and thus to the control pressure inlet 26.
  • the circumferential inlet groove 68 is narrower in its radial width, as compared to the embodiments shown in Figs. formed slit-like, whereby the force acting on the control valve member 58 is closed when the control valve 24 is closed.
  • the inlet groove 68 is fed via a ring channel 68 'which is larger in cross section and which communicates with the control pressure channel 70.
  • the further connecting channel 78' opens radially outward from the outlet opening 104 and leads into the connecting channel 78.
  • the control valve 24 is in the open position.
  • the control valve member 58 acts on the control valve member 58, as indicated by the thick arrow directed against the actuator 22 force, which the pressure difference between the pressure of the fuel in the control pressure inlet 26 connected to the control valve chamber 56 and the low-pressure outlet 54 connected to the relief groove 108, multiplied by the difference of the area of the compensation piston 112 - diameter D2 - and the surface of the sealing shoulder 106 - diameter Dl corresponds.
  • the control valve 104 of the Actuator 48 thus apply a force opposing this force.
  • the control valve 24 is in the closed position, wherein the control valve member 58 rests against the control valve seat 66 and the inlet groove 68 seals.
  • D3 in FIG. 6 designates the diameter of the outlet opening 104. With D4. the diameter of the control valve member 58 is indicated, and D5 denotes the diameter of the shaft 62 '.
  • a force opposite to the direction of the thick arrow, which the Druckdifferenz- between the pressure of the fuel in the connected to the control pressure inlet 26 inlet groove 68 and the pressure of the fuel in the low-pressure outlet 54 connected Control valve chamber 56 multiplied by the annular surface with an outer diameter of D4 and an inner diameter of D3 corresponds.
  • This force is at least partially compensated by the force generated by the compensation piston 112, which corresponds to the pressure difference of the fuel in the compensation pressure chamber 116 connected to the high pressure inlet 26 and the compensation low pressure chamber 118 connected to the low pressure outlet 54 multiplied by the hydraulically effective area of the compensation piston 112.
  • This is given by the difference of the cross-sectional area of the compensation piston 112 - diameter D2 in Fig. 5 - and the cross section of the shaft 62 '- diameter D5 - in Fig. 6.
  • the actuator 22 thus, in the closed position of the control valve, in the direction Apply reduced force acting on the thick arrow.
  • the hydraulic forces on the control valve 58 in its open or closed position be designed for optimal operation of the actuator 22.
  • FIG. 7 shows a further embodiment of the injection valve according to the invention, which is of the same design as that of FIG. 4 with respect to the control valve 24.
  • the C-shaped connection channel does not discharge directly into the piston drive chamber 76 but into the further connection channel arranged concentrically with the axis 16 78 '.
  • control-pressure-side piston part 28 'of the booster piston 28 is formed stepwise. He has on its the piston drive chamber 76 side facing a circular cylindrical, central axis 16 to the piston projection 122 whose designated Da diameter is slightly larger than 'designated by Db diameter of the high-pressure side piston member 28' '.
  • the piston guide space 74 has an extension 124 into which the piston projection 122 is immersed by the length designated L when the booster piston 28 is in the rest position shown in FIG. In this stop the lugs 80 at the bottom of the extension 124 at.
  • Figs. 8 and 9 show an embodiment with pressure compensation, which is very similar to that shown in Figs. 5 and 6 embodiment. The structural design is shown with more details.
  • a pill-like control valve seat body 130 is inserted in a graduated recess 16 to the axis of the housing recess 128 - this connects to the recess 18 - a pill-like control valve seat body 130 is inserted. With one end face of this sealingly against the bottom of the housing recess 128 and at the other end face of the control valve seat 66, the inlet groove 68 and the outlet opening 104 are formed.
  • a bore passing through the control valve seat body 130 parallel to the axis 16 forms part of the connection channel 78 which is fluidly connected to the bottom of the housing recess 128 with a further part of the connection channel 78 formed on the housing 10 leading to the piston drive chamber 76.
  • These webs 132 connect with respect to the annular channel 68 'radially inner part of the control valve seat body 130 with the radially outer part; see in particular Fig. 9.
  • the further connecting channel 78 'forming inclined bore extends from the outlet opening 104 to the connecting channel 78.
  • Through a further web 132 passes through the Kompensationsniederdruck barnlass 120. This opens out of the cylinder recess 114, which blind hole on Control valve seat body 130 except and on the other hand closed from the bottom of the housing recess 128.
  • the compensation pressure chamber 116 is connected via a radially extending passage with the annular channel 68 ', which in turn at the bottom of the housing recess 128 with the recessed on the housing 10 control pressure channel 70 is fluidly connected.
  • control valve seat body 130 two positioning pins 134 are inserted, which engage in corresponding blind holes in the bottom of the housing recess 128 for fixing the rotational position of the control valve seat body 130 with respect to the housing 10.
  • annular disc 136 On the bottom of the housing recess 128 facing away from the end face of the control valve seat body 130 sits an annular disc 136, which limits the control valve chamber 56 circumferentially and the inner diameter is selected such that the connecting channel 78 is fluidly connected to the control valve chamber 56.
  • control valve chamber 56 On the side facing away from the control valve seat body 130, the control valve chamber 56 is delimited by a disc 138, which rests on the annular disc 136 and is provided with a central bore 140 which is penetrated by the operating shaft 62 with radial play. The annular gap between the operating shaft 62 and the disc 138 forms the discharge channel 64 '. In the control valve chamber 56 sits the disk-like control valve member 58 on the operating shaft 62nd
  • an annular, provided with a hexagon screw 142 is arranged, which is threaded with its external thread in an internal thread in the region of the housing recess 128. This acts on the disc 138, the washer 136 and the control valve seat body 130 with an axial force, so that these sealingly against each other and the control valve seat body 130 sealingly abut the bottom of the housing recess 128.
  • the hexagon socket screw 142 bounded inside a partial space of the housing recess 128, which adjoins the low pressure chamber 50.
  • the low pressure passage 52 is formed by a radial bore in the housing 10.
  • the actuator housing 38 which together with the actuator 22 inserted therein defines the low-pressure space 50, sits on the downstream end of the housing 10.
  • the operating shaft 62 is fixedly connected to the actuator shaft 48.
  • the compensating piston 112 may be configured to fully compensate for the forces acting on the control valve member 58.
  • the disc 138 also forms the seat for the sealing shoulder 106 of the control valve member 58 in order to separate the control valve chamber 56 from the low-pressure chamber 50 when the control valve 24 is open.
  • the disc 138 in cooperation with the control valve member 58 also forms the stop for the actuator or its armature. Further, in this embodiment, by selecting the thickness of the washer 136 and the axial dimension of the control valve member 58, the stroke of the actuator 22 can be adjusted.
  • control valve 24 designed as a flat seat valve acts as a 2/3-way valve.
  • the fuel injectors shown in Figs. 1-9 operate as follows. Starting from the state shown in FIGS. 1 and 6 with the control valve 24 closed and injection valve member 34 resting against the injection valve seat 32, the actuator 22 is actuated in such a way for fuel injection, the actuator shaft 48 moves away from the control valve seat 66. As a result, the control valve member 58 moves away from the control valve seat member 66 in the open position shown in Figs. 2, 4, 5, 7 and 8, whereby the piston drive chamber 76 is supplied with control pressure.
  • the actuator 22 is driven such that the actuator shaft 48 moves in the direction against the control valve seat 66 and thereby the control valve 24 is closed.
  • the differential piston By connecting the control valve chamber 56 and thus the piston drive chamber 76 through the throttle channel 64 and discharge channel 64 'with the low-pressure chamber 50, the differential piston now moves in the opposite direction, causing the pressure of the fuel in the high-pressure fuel chamber 30 drops rapidly and the injection valve member 34th moved toward the injection valve seat 32 and thereby terminates the injection process.
  • Is between the control pressure inlet 26 and the Kolbenabtriebsraum 84th Given pressure equalization, flows - by the check valve 92 opens - fuel in the Kolbenabtriebsraum 84 until the booster piston 28 rests with its stop lug 80 on the housing 10.
  • the fuel injection valve is now ready for another injection process.
  • the booster piston 28 need not necessarily move back or even all the way toward the end of the piston drive chamber 76 in the short pauses between each injection.
  • Flat seat valves have, as explained with reference to the exemplary embodiments shown, the property of releasing a very large flow cross-section even at a very small opening stroke.
  • the fuel injection valve according to the invention is also suitable for multiple injections.

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

Abstract

The invention relates to a fuel injection valve for intermittent fuel injection into the combustion chamber of internal combustion engines. A needle-shaped injection valve member (34) is arranged in the high-pressure fuel chamber (30) adjacent to the injection valve seat (32), said injection valve member co-operating with the injection valve seat (32) and defining, in a piston-type manner, the cylinder chamber (36) which is connected to the high-pressure inlet (26). The booster piston (28) is controlled by means of the control valve (34) embodied as a flat seat valve, increasing the pressure of the fuel in the high-pressure fuel chamber (30) for an injection, and thus lifting the injection valve member from the injection valve seat. In this way, the injection is carried out with increased pressure.

Description

Brennstoffeinspritzventil mit DruckverstärkungFuel injection valve with pressure boost
Die vorliegende Erfindung betrifft ein Brennstoffeinspritzventil zur intermittierenden Brennstoffeinspritzung in den Brennraum einer Verbrennungskraftmaschine gemäss Patentanspruch 1.The present invention relates to a fuel injection valve for intermittent fuel injection into the combustion chamber of an internal combustion engine according to claim 1.
In der DE-A-10250130 ist ein Brennstoffeinspritzventil offenbart, bei welchem ein elektromagnetischer Aktuator ein 3/2- oder β/3-Wege-Ventil ansteuert. Mittels dieses Steuerventils wird je nach Ansteuerung des Aktuators ein als Differenzialkolben ausgebildeter Verstärkerkolben und die Zufuhr von Brennstoff in einen an einem Einspritzventilsitz angrenzenden Brennstoffhockdruckraum derart gesteuert, dass eine druckgesteuerte oder hubgesteuerte Einspritzung erfolgt. Bei derartigen Steuerventilen muss das Steuerventilglied jeweils einen grossen Weg zurück legen, um von einer Schaltstellung in eine andere Schaltstellung zu gelangen. Typischerweise beträgt dieser Weg mehrere 1/10 mm. Weiter ist die Mehrfacheinspritzung mit derartigen Steuerventilen sehr anspruchsvoll und ist der Aufbau de's Brennstoffeinspritzventils äusserst aufwendig.In DE-A-10250130 a fuel injector is disclosed in which an electromagnetic actuator drives a 3/2 or β / 3-way valve. Depending on the activation of the actuator, an intensifier piston designed as a differential piston and the supply of fuel into a fuel high-pressure space adjacent to an injection valve seat are controlled by means of this control valve such that a pressure-controlled or stroke-controlled injection takes place. In such control valves, the control valve member must each put a long way back to get from one switching position to another switching position. Typically, this path is several 1/10 mm. Furthermore, the multiple injection with such control valves is very demanding and the construction de 's fuel injector extremely costly.
Es ist eine Aufgabe der vorliegenden Erfindung, ein druckverstärkendes Brennstoffeinspritzventil zu schaffen, dessen Steuerventil mit einem sehr kleinen Hub des Steuerventilgliedes auskommt.It is an object of the present invention to provide a pressure boosting fuel injector whose control valve manages with a very small stroke of the control valve member.
Diese Aufgabe wird mit einem Brennstoffeinspritzventil gelöst, das die Merkmale des Patentanspruchs 1 aufweist. Erfindungsgemäss ist das Steuerventil als Flachsitzventil ausgebildet. Flachsitzventile haben die Eigenschaft, dass sie bei einem sehr geringen Hub grosse Durchströmungsquerschnitte freigeben. Typischerweise benötigt das Steuerventilglied eines erfindungsgemassen Brennstoffeinspritzventils einen Hub von nur ca. 2/100 bis 10/100 mm. ■ Die Ansteuerung des Steuerventilglieds kann somit auch mittels eines piezoelektrischen Aktuators erfolgen. Weiter sind problemlos Mehrfacheinspritzungen machbar; dies bei der Verwendung von piezoelektrischen Aktuatoren als auch bei der Verwendung von sehr schnellen elektromagnetischen Aktuatoren.This object is achieved with a fuel injection valve having the features of claim 1. According to the invention, the control valve is designed as a flat seat valve. Flat seat valves have the property that they release large flow cross sections at a very small stroke. Typically, the control valve member of a fuel injector according to the invention requires a stroke of only about 2/100 to 10/100 mm. ■ The control of the control valve member can thus also be effected by means of a piezoelectric actuator. Furthermore, multiple injections are feasible without problems; this in the use of piezoelectric actuators as well as in the use of very fast electromagnetic actuators.
Bevorzugte Ausführungsformen des erfindungsgemassen Brennstoffeinspritzventils sind in den abhängigen Patentansprüchen angegeben.Preferred embodiments of the fuel injection valve according to the invention are specified in the dependent claims.
Die Erfindung wird anhand in der Zeichnung dargestellten Ausführungsbeispielen näher beschrieben.The invention will be described with reference to embodiments illustrated in the drawings.
Es zeigen rein schematisch:It shows purely schematically:
Fig. 1 in einem Längsschnitt eine ersteFig. 1 in a longitudinal section a first
Ausführungsform eines erfindungsgemassen Brennstoffeinspritzventils;Embodiment of a fuel injection valve according to the invention;
Fig. 2 ebenfalls im Längsschnitt einen Teil des in der Fig. 1 gezeigtenFig. 2 also in longitudinal section a part of that shown in FIG
Brennstoffeinspritzventils mit einem Steuerventil und einem Verstärkerkolben; Fig. 3 ebenfalls im Längsschnitt einen Teil des in der Fig. 1 gezeigten Brennstoffeinspritzventils mit einem mittels einer Schliessfeder belasteten Einspritzventilglied, das kolbenartig einen Zylinderraum begrenzt;Fuel injection valve with a control valve and a booster piston; Fig. 3 also in longitudinal section a portion of the fuel injection valve shown in Figure 1 with a loaded by means of a closing spring injection valve member which defines a cylinder-like cylinder space.
Fig. 4 in gleicher Darstellung wie Fig.2 eine zweite Ausführungsform eines erfindungsgemässen Brennstoffeinspritzventils;FIG. 4 in the same representation as FIG. 2, a second embodiment of a fuel injection valve according to the invention;
Fig. 5 in gleicher Darstellung wie Fig. 2 undFig. 5 in the same representation as Fig. 2 and
4 eine dritte Ausführngsform eines erfindungsgemässen4 shows a third embodiment of an inventive method
Brennstoffeinspritzventils mit einer Druckkompensation für dasFuel injection valve with a pressure compensation for the
Steuerventilglied, welches in Offenstellung gezeigt ist;Control valve member which is shown in the open position;
Fig. 6 die in der Figur 5 gezeigteFIG. 6 shows that shown in FIG
Ausführungsform in einem Längsschnitt, der rechtwinklig zum in der Figur 5 gezeigten Längsschnitt verläuft und wobei das Steuerventilglied sich in Schliessstellung befindet;Embodiment in a longitudinal section which is perpendicular to the longitudinal section shown in Figure 5 and wherein the control valve member is in the closed position;
Fig. 7 in gleicher Darstellung wie Fig. 2 eine vierte Ausführungsform eines erfindungsgemässen Einspritzventils mit einem abgestuften Verstärkerkolben;FIG. 7 in the same representation as FIG. 2, a fourth embodiment of an injection valve according to the invention with a stepped intensifier piston;
Fig. 8 in gleicher Darstellung wie Fig. 5 und 6 eine der dort gezeigten Ausführungsform ähnliche weitere Ausführungsform mit einem unterschiedlichen mechanischen Aufbau; undFig. 8 in the same representation as Figs. 5 and 6 one of those shown there Embodiment similar further embodiment with a different mechanical structure; and
5 Fig. 9 einen Steuerventilsitzkörper der inFIG. 9 shows a control valve seat body of FIG
Fig. 8 gezeigten Ausführungsform in einem Querschnitt entlang der Linie IX - IX der Fig. 8.8 in a cross section along the line IX - IX of FIG. 8.
Ein in der Fig. 1 gezeigtes Brennstoffeinspritzventil ist 0 dazu bestimmt, in einen allgemein bekannten Brennraum einer Verbrennungskraftmaschine intermittierend Brennstoff einzuspritzen. Es weist ein im Wesentlichen kreiszylinderförmiges, abgestuftes Gehäuse 10 auf, an dem stirnseitig - auf jener Seite mit dem geringerenA fuel injector shown in FIG. 1 is intended to inject fuel intermittently into a generally known combustion chamber of an internal combustion engine. It has a substantially circular cylindrical, stepped housing 10, on the front side - on that side with the lower
15 Aussendurchmesser - in bekannter Art und Weise ein15 outer diameter - in a known manner
Ventilsitzelement 12 mittels einer Ueberwurfmutter 14 befestigt ist. Die Achse des Gehäuses 10, desValve seat member 12 is fixed by means of a cap nut 14. The axis of the housing 10, the
Ventilsitzelements 12 und der ueberwurfmutter 14 fallen im vorliegenden Beispiel zusammen und ist mit 16 bezeichnet. 0 Die Achse des Gehäuses, des Ventilsitzelements und derValve seat member 12 and the cap nut 14 coincide in the present example and is designated 16. 0 The axis of the housing, the valve seat element and the
Ueberwurfmutter könnten auch desaxiert oder in einemCap nut could also be desaxed or in one
Winkel zueinander verlaufen.Angle to each other.
In einem dem Ventilsitzelement 12 abgewandten Endbereich des Gehäuses 10 ist in einer Ausnehmung 18 eineIn a valve seat element 12 facing away from the end portion of the housing 10 is in a recess 18 a
25 Aktuatoranordnung 20 angeordnet. Ein piezoelektrischer Aktuator 22 der Aktuatoranordnung 20 ist dazu bestimmt, ein Steuerventil 24 anzusteuern. Dieses verbindet in Offenstellung einen Steuerdruckeinlass 26 für den Brennstoff am Gehäuse 10 mit der Steuerdruckseite eines25 actuator assembly 20 is arranged. A piezoelectric actuator 22 of the actuator assembly 20 is intended to drive a control valve 24. This connects in open position a control pressure inlet 26 for the fuel on the housing 10 with the control pressure side of
30. als Differenzialkolben ausgebildeten Verstärkerkolbens 28. Die Hochdruckseite des Verstärkerkolbens 28 ist mit einem im Ventilsitzelement 12 angeordneten Brennstoffhochdruckraum 30 verbunden, der an einen am Ventilsitzelement 12 ausgebildeten, kegelmantelartig geformten Einspritzventilsitz 32 angrenzt. Im Brennstoffhochdruckraum 30 ist zentrisch zur Achse 16 und in Richtung dieser Achse 16 längsbewegbar ein nadelartiges Einspritzventilglied 34 angeordnet, das einerseits dazu bestimmt ist, mit dem Einspritzventilsitz 32 zusammen zu wirken, und das andererseits kolbenartig einen mit dem Steuerdruckeinlass 26 verbundenen Zylinderraum 36 begrenzt. Der Steuerdruck - oder auch Speisedruck - liegt bei ca. 200 - 1600 bar.30. As a differential piston formed booster piston 28. The high pressure side of the booster piston 28 is provided with a in the valve seat member 12 arranged high-pressure fuel chamber 30 is connected, which adjoins a formed on the valve seat member 12, a cone-shaped like injection valve seat 32. In the high-pressure fuel chamber 30, a needle-like injection valve member 34 is arranged centrally movable relative to the axis 16 and in the direction of this axis 16, which is intended on the one hand to cooperate with the injection valve seat 32, and the other piston-like limits a cylinder chamber 36 connected to the control pressure inlet 26. The control pressure - or feed pressure - is about 200 - 1600 bar.
Das Steuerventil 24, der Verstärkerkolben 28 und alle notwendigen Verbindungsdurchlässe sind im Gehäuse 10 angeordnet, bzw. an diesem ausgebildet. Der besseren üebersichtlichkeit halber ist das Gehäuse 10 einstückig dargestellt; es kann jedoch aus mehreren Teilen zusammengesetzt sein, um die notwendigen Ausnehmungen und Verbindungsdurchlässe bei der Herstellung einfach ausbilden zu können.The control valve 24, the booster piston 28 and all necessary connection passages are arranged in the housing 10, or formed thereon. For better clarity, the housing 10 is shown in one piece; However, it may be composed of several parts in order to easily form the necessary recesses and connecting passages in the production can.
Der piezoelektrische Aktuator 22 ist in einem Aktuatorgehäuse 38 aufgenommen, welches einerseits an einer Schulter 40 der Ausnehmung 18 am Gehäuse 10 anliegt und andererseits mittels einer hülsenförmigen Befestigungsschraube 42, welche in das Gehäuse 10 eingewindet ist und sich an einer Stützschulter 44 des Aktuatorgehäuses 38 abstützt, in Anlage an der Schulter 40 gehalten ist. Elektrische Steuerleitungen, über welche der Aktuator 22 in bekannter Art und Weise von einer Steuerung her angesteuert wird, sind mit 46 bezeichnet. Der Aktuator 22 weist einen Äktuatorschaft 48 auf, welcher bei Erregung bzw. Entregung des Aktuators 22 in Richtung der Achse 16 um einen Hub von ca. 0,02 - 0,1 mm in der einen bzw. entgegengesetzten Richtung bewegt wird.The piezoelectric actuator 22 is accommodated in an actuator housing 38, which rests on the one hand on a shoulder 40 of the recess 18 on the housing 10 and on the other hand by means of a sleeve-shaped fastening screw 42, which is threaded into the housing 10 and is supported on a support shoulder 44 of the actuator 38, held in abutment against the shoulder 40. Electrical control lines, via which the actuator 22 is driven in a known manner by a controller forth, are designated 46. The actuator 22 has an actuator shaft 48, which upon excitation or de-excitation of the actuator 22 in the direction of the axis 16 about a stroke of about 0.02 - 0.1 mm in the one or the opposite direction is moved.
Die Ausnehmung 18 weist angrenzend an dieThe recess 18 has adjacent to the
Aktuatoranordnung 20 einen Niederdruckraum 50 auf, welcher über einen, in radialer Richtung durch das Gehäuse 10 verlaufenden Niederdruckdurchlass 52 mit einemActuator 20 to a low pressure chamber 50, which via a, extending in the radial direction through the housing 10 low-pressure passage 52 with a
Niederdruckauslassanschluss 54 am Gehäuse 10 verbunden ist, von welchem durch Leckage oder die . Steuerung verursachter Verlust von Brennstoff in einen Brennstoffvorratstank geleitet wird.Low pressure outlet port 54 is connected to the housing 10, of which by leakage or the. Control caused loss of fuel is directed into a fuel storage tank.
Das Steuerventil 24 und die Druckverstärkungseinrichtung mit dem Verstärkerkolben 28 wird unter Beizug der Figur 2 näher beschrieben. Am Gehäuse 10 ist ein kreiszylinderförmiger Steuerventilraum 56 zentrisch zur Achse 16 ausgenommen, in welchem ein scheibenförmiges Steuerventilglied 58 in Richtung der Achse 16 bewegbar aufgenommen ist. Vom Steuerventilraum 56 zum Niederdruckraum 50 verläuft ein Führungsdurchlass 60, welcher in enger Gleitpassung von einem Betätigungsschaft 62 durchgriffen ist, der einerseits am Steuerventilglied 58 und andererseits am freien Ende des Aktuatorschafts 48 anliegt. Weiter ist der Steuerventilraum 56 mit dem Niederdruckraum 50 über einen Drosselkanal 64 verbunden.The control valve 24 and the pressure boosting device with the booster piston 28 will be described in detail with reference to FIG. On the housing 10 is a circular cylindrical control valve chamber 56 is recessed centrally to the axis 16, in which a disc-shaped control valve member 58 is movably received in the direction of the axis 16. From the control valve chamber 56 to the low pressure chamber 50 extends a guide passage 60 which is penetrated in close sliding fit by an actuating shaft 62 which rests on the one hand on the control valve member 58 and on the other hand at the free end of the Aktuatorschafts 48. Further, the control valve chamber 56 is connected to the low pressure chamber 50 via a throttle channel 64.
Auf der dem Betätigungsschaft 62 abgewandten Seite des Steuerventilglieds 58 ist der Steuerventilraum 56 von einem am Gehäuse 10 ausgebildeten, ebenen SteuerventilsitzOn the side facing away from the operating shaft 62 of the control valve member 58 of the control valve chamber 56 is formed by a formed on the housing 10, planar control valve seat
66 begrenzt. Mit diesem wirkt das tellerartige66 limited. With this acts the plate-like
Steuerventilglied 58 zusammen, welches auf der demControl valve member 58 together, which on the
Steuerventilventilsitz 66 zugewandten Seite ebenfalls mit hoher Präzision eben ausgebildet ist. In Fig. 2 befindet sich das Steuerventilglied 58 in einer vom Steuerventilsitz 66 beabstandeten Offenstellung, wogegen es in Fig. 1 in seiner am Steuerventilseitz 66 anliegenden Schliessstellung gezeigt ist.Control valve seat 66 facing side is also formed with high precision flat. In Fig. 2, the control valve member 58 is located in one of Control valve seat 66 spaced open position, whereas it is shown in Fig. 1 in its voltage applied to the control valve seat 66 closing position.
Im Bereich des Steuerventilsitzes 66 ist in dem Gehäuse 10 eine ringförmige, um die Achse 16 herumverlaufende Einlassnut 68 angeformt, die in Richtung gegen den Steuerventilraum 56 offen und bei geschlossenem Steuerventil 24 vom Steuerventilglied 58 verschlossen ist. Die Einlassnut 68 ist über einen Steuerdruckkanal 70 im Gehäuse 10 mit dem Steuerdruckeinlass 26 strömungsverbunden. Weiter ist sie mit möglichst grossem radialen Aussendurchmesser ausgebildet, so dass beim Oeffnen des Steuerventils 24 sehr rasch ein grosser Strömungsquerschnitt frei wird.In the area of the control valve seat 66, an annular inlet groove 68 extending around the axis 16 is formed in the housing 10 and is open in the direction of the control valve chamber 56 and closed by the control valve member 58 when the control valve 24 is closed. The inlet groove 68 is fluidly connected to the control pressure inlet 26 via a control pressure channel 70 in the housing 10. Further, it is formed with the largest possible radial outer diameter, so that when opening the control valve 24 very quickly a large flow cross section is free.
Im Gehäuse 10, bezüglich der Achse 16 zentrisch, ist ein kreiszylinderförmiger Kolbenführungsraum 74 ausgebildet, in welchem ein steuerdruckseitiger Kolbenteil 28' des Verstärkerkolbens 28 aufgenommen und in enger Gleitpassung in Richtung der Achse 16 hin und her verschiebbar geführt ist. Der Kolbenführungsraum 74 und der steuerdruckseitige Kolbenteil 28' begrenzen einen Kolbenantriebsraum 76, der über einen im Gehäuse 10 ausgeformten Verbindungskanal 78 mit dem Steuerventilraum 56 und somit durch den Drosselkanal 64 mit dem Niederdruckauslass 54 dauernd strömungsverbunden ist. Die freien Querschnitte des Steuerdruckkanals 70 und des Verbindungskanals 78 sind viel grösser als der engste Querschnitt des Drosselkanals 64. Weiter weist der Verstärkerkolben 28 an seiner steuerdruckseitigen Stirnseite eine vorstehende Anschlagnase 88 auf, die verhindert, dass sich der Verstärkerkolben 28 mit seiner diesseitigen Stirnseite ans Gehäuse 10 anlegen kann. Andererseits führt vom Kolbenteil 28' ein im Querschnitt kleinerer, ebenfalls kreiszylinderförmig ausgebildeter Kolbenteil 28' ' weg, welcher einen niederdruckseitigen Teil 82 des Kolbenführungsraums 74 durchgreift und an der Wand einer vom niederdruckseitigen Teil 82 weggehenden zylindrische Ausnehmung in enger Gleitpassung geführt ist. Mit seinem hochdruckseitigen Ende begrenzt der Kolbenteil 28" ' einen Kolbenabtriebsraum 84. Der niederdruckseitige Teil 82 des Kolbenführungsraumes 74 ist über einen in den Niederdruckdurchlass 52 führenden Niederdruckkanal 86 dauernd mit dem Niederdruckauslass 54 verbunden.In the housing 10, with respect to the axis 16 centric, a circular cylindrical piston guide chamber 74 is formed, in which a control pressure side piston part 28 'of the booster piston 28 is received and guided in close sliding fit in the direction of the axis 16 back and forth. The piston guide chamber 74 and the control-pressure-side piston part 28 'delimit a piston drive chamber 76, which is permanently connected to the flow through a connecting channel 78 formed in the housing 10 with the control valve chamber 56 and thus through the throttle channel 64 with the low-pressure outlet 54. The free cross sections of the control pressure channel 70 and the connecting channel 78 are much larger than the narrowest cross section of the throttle channel 64. Next, the booster piston 28 on its control-pressure side end a projecting stop lug 88, which prevents the booster piston 28 with its side face this side of the housing 10 can create. On the other hand leads from the piston part 28 'in cross-section smaller, also circular cylindrical trained piston part 28''away, which passes through a low-pressure side portion 82 of the piston guide chamber 74 and is guided on the wall of a low-pressure side portion 82 away cylindrical recess in close sliding fit. The low-pressure-side part 82 of the piston guide chamber 74 is permanently connected to the low-pressure outlet 54 via a low-pressure passage 86 leading into the low-pressure passage 52.
Vom Kolbenabtriebsraum 84 führt - siehe Figur 1 - eine im Gehäuse 10 ausgebildete Hochdruckleitung 88 zum stirnseitigen Ende des Gehäuses 10, wo sie in den Brennstoffhochdruckraum 30 mündet. Vom Steuerdruckkanal 70 zweigt eine Steuerdruckzweigleitung 90 ab, die einerseits über ein Rückschlagventil 92 in den Kolbenabtriebsraum 84 und andererseits am stirnseitigen Ende des Gehäuses 10 in den Zylinderraum 36 mündet. Das als federbelastetes Kugelventil ausgebildete Rückschlagventil 92 erlaubt Brennstoff vom Steuerdruckeinlass 26 her in den Kolbenabtriebsraum 84 einzuströmen, verhindert jedoch ein Ausströmen von Brennstoff aus dem Kolbenabtriebsraum 84 in die Steuerdruckzweigleitung 90.From Kolbenabtriebsraum 84 leads - see Figure 1 - formed in a housing 10 high-pressure line 88 to the front end of the housing 10, where it opens into the high-pressure fuel chamber 30. From the control pressure channel 70 branches off a control pressure branch line 90, which opens on the one hand via a check valve 92 in the Kolbenabtriebsraum 84 and on the other hand at the front end of the housing 10 in the cylinder chamber 36. The check valve 92 designed as a spring-loaded ball valve allows fuel to flow from the control pressure inlet 26 into the piston output space 84, but prevents fuel from flowing out of the piston output space 84 into the control pressure branch line 90.
Wie aus Fig. 1 und insbesondere Fig. 3 hervorgeht, ist der durch eine Ausnehmung im Ventilsitzelement 12 gebildete Brennstoffhochdruckraum 30 zur Achse 16 abgestuft kreiszylinderförmig ausgebildet und einerseits durch den Einspritzventilsitz 32 und andererseits durch die Stirnseite des Gehäuses 10 begrenzt. Im Brennstoffhochdruckraum 30 ist ein hülsenartig ausgebildetes Nadelführungselement 94 angeordnet, das einerseits über drei in radialer Richtung nach aussen vorstehende Rippen 94' am Ventilsitzeleiαent 12 zentrierend abgestützt ist und indem andererseits radial innen der diesseitige Endbereich des Einspritzventilgliedes 34 in dichter Gleitpassung geführt ist. Alternativ können die Rippen 94' auch weggelassen werden (Führung des Nadelführungselements 94 würde von Rippen 100 übernommen, siehe weiter unten) . Das Nadelführungselement 94 begrenzt umfangsseitig den Zylinderraum 36 und liegt unter der Kraft einer Schliessfeder 96 dichtend an der Stirnseite des Gehäuses 10 an. Die Schliessfeder 96 stützt sich einerseits am freien Ende des Nadelführungselements 94 und andererseits über eine Ringscheibe 98 und ein Abstützelement 98 ' in bekannter Art und Weise am Einspritzventilglied 34 ab. Die Schliessfeder 96 drückt das Brennstoffeinspritzventilglied 34 in Richtung gegen den Einspritzventilsitz 32. Zwischen dem Ventilsitzelement 12 und dem Nadelführungselement 94, der Schliessfeder 96 und dem Einspritzventilglied 34 bleibt ein grosser Strömungsquerschnitt für den Brennstoff frei.As is apparent from Fig. 1 and in particular Fig. 3, the formed by a recess in the valve seat member 12 fuel high-pressure space 30 to the axis 16 is stepped circular cylindrical and limited on the one hand by the injection valve seat 32 and on the other hand by the end face of the housing 10. In the high-pressure fuel chamber 30, a sleeve-like design needle guide element 94 is arranged, the on the one hand via three radially outwardly projecting ribs 94 'on Ventililsitzeleiαent 12 is centered supported and on the other hand radially inwardly the this side end portion of the injection valve member 34 is guided in tight sliding fit. Alternatively, the ribs 94 'may also be omitted (guidance of the needle guide element 94 would be assumed by ribs 100, see below). The needle guide element 94 circumferentially bounded the cylinder chamber 36 and is under the force of a closing spring 96 sealingly against the end face of the housing 10. The closing spring 96 is supported on the one hand at the free end of the needle guide element 94 and on the other hand via an annular disc 98 and a support element 98 'in a known manner on the injection valve member 34 from. The closing spring 96 presses the fuel injection valve member 34 in the direction against the injection valve seat 32. Between the valve seat member 12 and the needle guide member 94, the closing spring 96 and the injection valve member 34 remains a large flow area for the fuel free.
Das Einspritzventilglied 34 weist in radialer Richtung drei vorstehende Führungsrippen 100 auf, über welche es am Ventilsitzelement 12, im Bereich des im Querschnitt engeren Teils des Brennstoffhochdruckraums 30, in axialer Richtung verschiebbar geführt ist. Im Bereich zwischen den drei Führungsrippen 100 ist ein grosser Strömungsquerschnitt vorhanden, so dass Brennstoff ungehindert zum Einspritzventilsitz 32 strömen kann.The injection valve member 34 has in the radial direction three projecting guide ribs 100, via which it is guided on the valve seat member 12, in the region of the narrower in cross section part of the high-pressure fuel chamber 30, in the axial direction. In the region between the three guide ribs 100, a large flow cross-section is present so that fuel can flow unhindered to the injection valve seat 32.
Der Vollständigkeit halber sei erwähnt, dass stromabwärts des Einspritzventilsitzes am Ventilsitzelement 12For completeness, it should be mentioned that downstream of the injection valve seat on the valve seat member 12th
Düsendurchlässe 102 ausgenommen sind, durch welche bei einer Einspritzung der Brennstoff unter sehr hohem Druck in den Brennraum eingespritzt wird.Nozzle passages 102 are excluded, by which at an injection of the fuel is injected under very high pressure in the combustion chamber.
Bei der in den Fig. 1 bis 3 gezeigten Ausführungsform wirkt das als Flachsitzventil ausgebildete Steuerventil 34 als ein 2/2-Wege-Ventil.In the embodiment shown in FIGS. 1 to 3, the control valve 34 designed as a flat seat valve acts as a 2/2-way valve.
Bei der Beschreibung der in der Fig. 4 gezeigten Ausführungsform des erfindungsgemässenIn the description of the embodiment shown in FIG. 4 of the inventive
Brennstoffeinspritzventils werden für gleichwirkende beziehungsweise gleiche Teile dieselben Bezugszeichen verwendet, wie im Zusammenhang mit der in der Fig. 1 - 3 gezeigten Ausführungsform. Weiter wird im Folgenden nur noch auf die Unterschiede zur bereits beschriebenen Ausführungsform eingegangen.Fuel injection valve, the same reference numerals are used for equivalent or identical parts, as in connection with the embodiment shown in FIGS. 1-3. Furthermore, only the differences from the already described embodiment will be discussed below.
Am Gehäuse 10 ist im Bereich des Steuerventilsitzes 66, zentrisch zur Achse 16, eine kreiszylinderförmige Ausnehmung ausgebildet, welche eine mit Abstand von der Einlassnut 68 umgriffene Auslassöffnung 104 bildet. Diese ist über einen weiteren Verbindungskanal 78' mit dem Kolbenantriebsraum 76 strömungsverbunden. Durch die Parallelschaltung des Verbindungskanals 78 und des weiteren Verbindungskanals 78' ist zwischen dem Steuerventil 24 und dem Kolbenantriebsraum 76 ein, bezüglich der Ausführungsform gemäss den Fig. 1 - 3, beinahe verdoppelten Strömungsquerschnitt am Steuerventilsitz 66 vorhanden, wodurch der Hub des Steuerventilgliedes 58 verkleinert und/oder die Einspritzmenge vom Brennstoff pro Einspritzung grösser sein kann.On the housing 10, a circular cylindrical recess is formed in the region of the control valve seat 66, centric to the axis 16, which forms an outlet opening 104 encompassed by a distance from the inlet groove 68. This is flow-connected to the piston drive chamber 76 via a further connecting channel 78 '. Through the parallel connection of the connecting channel 78 and the further connecting channel 78 'is between the control valve 24 and the piston drive chamber 76, with respect to the embodiment of FIGS. 1-3, almost doubled flow cross-section at the control valve seat 66, whereby the stroke of the control valve member 58 is reduced and / or the injection quantity of fuel per injection may be greater.
Das Einspritzventilglied 34 ist wiederum teller- bzw. scheibenförmig ausgebildet, nun jedoch mit demThe injection valve member 34 is again plate-shaped or disk-shaped, but now with the
Betätigungsschaft 62 fest verbunden, vorzugsweise mit diesem einstückig ausgebildet. In Schliessstellung liegt das Steuerventilglied 58 einerseits an einer ringförmigen an die Einlassnut 68 radial aussen anschliessenden Dichtfläche des Steuerventilsitzes 66 und andererseits an einer ebenfalls ringförmigen, zwischen der Einlassnut 68 und der Auslassöffnung 104 angeordneten, weiteren Dichtfläche des Steuerventilsitzes 66 dichtend an. In in der Fig. 4 gezeigten Offenstellung des Steuerventils 34 gibt das Steuerventilglied 58 die Verbindung von der Einlassnut 68 zum Verbindungskanal 78 und weiteren Verbindungskanal 78' frei.Operating shaft 62 firmly connected, preferably with this integrally formed. In the closed position, the control valve member 58 bears sealingly against an annular sealing surface of the control valve seat 66 which adjoins the inlet groove 68 radially on the one hand, and against a further annular sealing face of the control valve seat 66 between the inlet groove 68 and the outlet opening 104. 4, the control valve member 58 releases the connection from the inlet groove 68 to the connection channel 78 and further connection channel 78 '.
Das Steuerventilglied 58 weist auf der dem Steuerventilsitz 66 abgewandten Seite eine kreisringförmige Dichtschulter 106 auf, die bezüglich des daran anschliessenden Betätigungsschaft 62 in radialer Richtung und bezüglich des übrigen Teils des Steuerventilgliedes 58 in axialer Richtung vorsteht. Die Dichtschulter 106 liegt in Offenstellung des Steuerventils 24 dichtend am Gehäuse 10 an. Der Führungsdurchlass 60, in welchen der Betätigungsschaft 62 in Gleitpassung geführt ist, ist in seinem, dem Steuerventilraum 56 zugewandten Endbereich, zu einer umlaufenden Entlastungsnut 108 aufgeweitet, welche über einen Entlastungskanal 64' dauernd - und ohne Drossel - mit dem Niederdruckraum 50 und somit dem Niederdruckauslass 54 verbunden ist. Dadurch kann beim Schliessen des Steuerventils 24 Brennstoff aus dem Steuerventilraum 56 und somit dem Kolbenantriebsraum 76 schneller abfliessen, als bei der in den Fig. 1 - 3 gezeigten Ausführungsform, was beim Schliessen des Steuerventils 24 zu einer rascheren Beendigung des Einspritzvorgangs führt. Mehrfacheinspritzungen in sehr kurzen Zeitabständen sind dadurch ermöglicht. Bei den beiden in den Fig. 1 - 4 gezeigten Ausführungsformen des Brennstoffeinspritzventils muss der Aktuator 22 mit grosser Kraft das Steuerventil 24 schliessen und dann in Schliessstellung halten. Derartig grosse Kräfte, bei für Brennstoffeinspritzventilen typischen Druck- und Flächenverhältnissen, können in der Regel nur von piezoelektrischen Aktuatoren aufgebracht werden. Die Fig. 5 und 6 zeigen eine Ausführungsform eines erfindungsgemässen Brennstoffeinspritzventils, bei welchem dieses Problem behoben ist und welche das Steuern des Steuerventils 24 auch mittels eines elektromagnetischen Aktuators 22 ermöglicht; dies durch wenigstens teilweise Kompensation der durch die Druckdifferenzen verursachten Kräfte auf das Steuerventilglied 58.The control valve member 58 has on the side facing away from the control valve seat 66 an annular sealing shoulder 106 which protrudes in the axial direction with respect to the adjoining operating shaft 62 in the radial direction and with respect to the remaining part of the control valve member 58. The sealing shoulder 106 is in the open position of the control valve 24 sealingly on the housing 10. The guide passage 60, in which the operating shaft 62 is guided in sliding fit, is widened in its, the control valve chamber 56 facing end portion to a circumferential relief groove 108, which via a discharge channel 64 'permanently - and without throttle - with the low-pressure chamber 50 and thus the Low pressure outlet 54 is connected. As a result, when closing the control valve 24 fuel from the control valve chamber 56 and thus the piston drive chamber 76 flow faster than in the embodiment shown in FIGS. 1-3, which leads to a faster completion of the injection process when closing the control valve 24. Multiple injections in very short time intervals are made possible. In the two embodiments of the fuel injection valve shown in FIGS. 1 to 4, the actuator 22 has to close the control valve 24 with a large force and then hold it in the closed position. Such large forces, in typical for fuel injection valves pressure and area ratios, can be applied usually only by piezoelectric actuators. Figures 5 and 6 show an embodiment of a fuel injection valve according to the invention, in which this problem is solved and which also allows the control of the control valve 24 by means of an electromagnetic actuator 22; this by at least partial compensation of the forces caused by the pressure differences forces on the control valve member 58th
Die in den Fig. 5 und 6 gezeigte Ausführungsform ist jener der in Fig. 4 gezeigten Ausführungsform ähnlich. Es wird im Folgenden, nur noch auf die Unterschiede eingegangen.The embodiment shown in Figs. 5 and 6 is similar to that of the embodiment shown in Fig. 4. In the following, only the differences will be discussed.
Am scheibenartigen Steuerventilglied 58 ist auf der dem Betätigungsschaft 62 abgewandten Seite ein Schaft 62 ' , vorzugsweise einstückig angeordnet, welcher in einem Schaftdurchlass 110 im Gehäuse 10 in enger Gleitpassung geführt ist und in seinem freien Endbereich einen Kompensationskolben 112 trägt. Der Kompensationskolben 112 ist in einer Zylinderausnehmung 114, ebenfalls in enger Gleitpassung, geführt. Die Zylinderausnehmung 114 und der Kompensationskolben 112 begrenzen auf der dem Steuerventilglied 58 zugewandten Seite des Kompensationskolben 112 einen Kompensationsdruckraum 116, welcher mit dem Steuerdruckkanal 70 und somit dem Steuerdruckeinlass 26 strömungsverbunden ist. Ein ebenfalls von der Zylinderausnehmung 114 und dem Kompensationskolben 112 begrenzten Kompensationsniederdruckraum 118, auf der dem Steuerventilglied 58 abgewandten Seite des Kompensationskolbens 112, ist, wie dies insbesondere aus Fig. β hervorgeht, über einen Kompensationsniederdruckdurchlass 120 mit dem Niederdruckraum 50 strömungsverbunden.At the disk-like control valve member 58 is on the side facing away from the operating shaft 62, a shaft 62 ', preferably integrally arranged, which is guided in a shaft passage 110 in the housing 10 in close sliding fit and carries in its free end a compensating piston 112. The compensation piston 112 is guided in a cylinder recess 114, also in close sliding fit. The cylinder recess 114 and the compensating piston 112 delimit, on the side of the compensation piston 112 facing the control valve member 58, a compensation pressure chamber 116, which is flow-connected to the control pressure channel 70 and thus to the control pressure inlet 26. An also delimited by the cylinder recess 114 and the compensation piston 112 Compensating low-pressure chamber 118, on the side of the compensation piston 112 facing away from the control valve member 58, is flow-connected to the low-pressure chamber 50 via a compensation low-pressure passage 120, as can be seen in particular from FIG.
Weiter ist die umlaufende Einlassnut 68, im Vergleich zu den in den Fig. 1 - 4 gezeigten Ausführungsformen, in ihrer radialer Breite gemessen schmaler, d.h. schlitzartiger ausgebildet, wodurch die bei geschlossenem Steuerventil 24 auf das Steuerventilglied 58 wirkende Kraft reduziert ist. Die Einlassnut 68 wird jedoch über einen im Querschnitt grosseren Ringkanal 68' gespeist, welcher mit dem Steuerdruckkanal 70 kommuniziert.Further, the circumferential inlet groove 68 is narrower in its radial width, as compared to the embodiments shown in Figs. formed slit-like, whereby the force acting on the control valve member 58 is closed when the control valve 24 is closed. However, the inlet groove 68 is fed via a ring channel 68 'which is larger in cross section and which communicates with the control pressure channel 70.
Da der Schaft 62', der Kompensationsdruckraum 116 und der Kompensationskolben 112 zentrisch zur Achse 16 angeordnet sind, mündet der weitere Verbindungskanal 78' in radialer Richtung gegen aussen versetzt aus der Auslassöffnung 104 und führt in den Verbindungskanal 78.Since the shaft 62 ', the compensating pressure chamber 116 and the compensating piston 112 are arranged centrally relative to the axis 16, the further connecting channel 78' opens radially outward from the outlet opening 104 and leads into the connecting channel 78.
In Fig. 5 befindet sich das Steuerventil 24 in Offenstellung. Dabei wirkt auf das Steuerventilglied 58 eine, wie mit dem dicken Pfeil angedeutete, gegen den Aktuator 22 gerichtete Kraft, welche der Druckdifferenz zwischen dem Druck des Brennstoffs im mit dem Steuerdruckeinlass 26 verbundenen Steuerventilraum 56 sowie dem mit dem Niederdruckauslass 54 verbundenen Entlastungsnut 108, multipliziert mit der Differenz der Fläche des Kompensationskolbens 112 - Durchmesser D2 - und der Fläche der Dichtschulter 106 - Durchmesser Dl entspricht. Zum Schliessen des Steuerventils 104 muss der Aktuator 48 somit eine dieser Kraft entgegen gesetzte Antriebskraft aufbringen.In Fig. 5, the control valve 24 is in the open position. In this case acts on the control valve member 58, as indicated by the thick arrow directed against the actuator 22 force, which the pressure difference between the pressure of the fuel in the control pressure inlet 26 connected to the control valve chamber 56 and the low-pressure outlet 54 connected to the relief groove 108, multiplied by the difference of the area of the compensation piston 112 - diameter D2 - and the surface of the sealing shoulder 106 - diameter Dl corresponds. To close the control valve 104 of the Actuator 48 thus apply a force opposing this force.
In der Fig. 6 befindet sich das Steuerventil 24 in Schliessstellung, wobei das Steuerventilglied 58 am Steuerventilsitz 66 anliegt und die Einlassnut 68 abdichtet. Mit D3 ist in Fig. 6 der Durchmesser der Auslassöffnung 104 gekennzeichnet. Mit D4 . ist der Durchmesser des Steuerventilgliedes 58 angedeutet, und D5 bezeichnet den Durchmesser des Schaftes 62' . In Schliessstellung des Steuerventils 24 wirkt auf das Steuerventilglied 58 eine Kraft (entgegen der Richtung des dicken Pfeils), welche der Druckdifferenz- zwischen dem Druck des Brennstoffs in der mit dem Steuerdruckeinlass 26 verbundenen Einlassnut 68 und dem Druck des Brennstoffs im mit dem Niederdruckauslass 54 verbundenen Steuerventilraum 56, multipliziert mit der Ringfläche mit einem Aussendurchmesser von D4 und einem Innendurchmesser von D3 entspricht. Diese Kraft ist mindestens zum Teil kompensiert durch die vom Kompensationskolben 112 erzeugte Kraft, welche der Druckdifferenz des Brennstoffs im mit dem Hochdruckeinlass 26 verbundenen Kompensationsdruckraum 116 und dem mit dem Niederdruckauslass 54 verbundenen Kompensationsniederdruckraum 118, multipliziert mit der hydraulisch wirksamen Fläche des Kompensationskolbens 112 entspricht. Diese ist gegeben durch die Differenz von der Querschnittsfläche des Kompensationskolbens 112 - Durchmesser D2 in Fig. 5 - und dem Querschnitt des Schaftes 62' - Durchmesser D5 - in Fig. 6. Der Aktuator 22 muss somit, in Schliessstellung des Steuerventils, eine in Richtung des dicken Pfeils wirkende reduzierte Kraft aufbringen. Je nach Wahl der Abmessungen der Durchmesser Dl, D2, D3, D4 und D5 können die hydraulischen Kräfte auf das Steuerventil 58 in seiner Offen- bzw. Schliessstellung für eine optimale Funktion des Aktuators 22 ausgelegt werden.6, the control valve 24 is in the closed position, wherein the control valve member 58 rests against the control valve seat 66 and the inlet groove 68 seals. D3 in FIG. 6 designates the diameter of the outlet opening 104. With D4. the diameter of the control valve member 58 is indicated, and D5 denotes the diameter of the shaft 62 '. In the closed position of the control valve 24 acts on the control valve member 58, a force (opposite to the direction of the thick arrow), which the Druckdifferenz- between the pressure of the fuel in the connected to the control pressure inlet 26 inlet groove 68 and the pressure of the fuel in the low-pressure outlet 54 connected Control valve chamber 56 multiplied by the annular surface with an outer diameter of D4 and an inner diameter of D3 corresponds. This force is at least partially compensated by the force generated by the compensation piston 112, which corresponds to the pressure difference of the fuel in the compensation pressure chamber 116 connected to the high pressure inlet 26 and the compensation low pressure chamber 118 connected to the low pressure outlet 54 multiplied by the hydraulically effective area of the compensation piston 112. This is given by the difference of the cross-sectional area of the compensation piston 112 - diameter D2 in Fig. 5 - and the cross section of the shaft 62 '- diameter D5 - in Fig. 6. The actuator 22 thus, in the closed position of the control valve, in the direction Apply reduced force acting on the thick arrow. Depending on the choice of the dimensions of the diameter Dl, D2, D3, D4 and D5, the hydraulic forces on the control valve 58 in its open or closed position be designed for optimal operation of the actuator 22.
Fig. 7 zeigt eine weitere Ausführungsform des erfindungsgemässen Einspritzventils, welche bezüglich des Steuerventils 24 gleich ausgebildet ist wie jene gemäss Fig. 4. Der C-förmige Verbindungskanal mündet jedoch nicht direkt in den Kolbenantriebsraum 76, sondern in den konzentrisch zur Achse 16 angeordneten weiteren Verbindungskanal 78'.FIG. 7 shows a further embodiment of the injection valve according to the invention, which is of the same design as that of FIG. 4 with respect to the control valve 24. However, the C-shaped connection channel does not discharge directly into the piston drive chamber 76 but into the further connection channel arranged concentrically with the axis 16 78 '.
Im Gegensatz zur Ausführungsform gemäss Fig. 4 ist der steuerdruckseitige Kolbenteil 28' des Verstärkerkolbens 28 stufenartig ausgebildet. Er weist auf seiner dem Kolbenantriebsraum 76 zugewandten Seite einen kreiszylinderförmigen, zur Achse 16 zentrischen Kolbenvorsprung 122 auf, dessen mit Da bezeichneter Durchmesser etwas grösser ist als' der mit Db bezeichnete Durchmesser des hochdruckseitigen Kolbenteils 28' '.In contrast to the embodiment according to FIG. 4, the control-pressure-side piston part 28 'of the booster piston 28 is formed stepwise. He has on its the piston drive chamber 76 side facing a circular cylindrical, central axis 16 to the piston projection 122 whose designated Da diameter is slightly larger than 'designated by Db diameter of the high-pressure side piston member 28' '.
Entsprechend weist der Kolbenführungsraum 74 eine Verlängerung 124 auf, in welche der Kolbenvorsprung 122 um die mit L bezeichnete Länge eingetaucht ist, wenn der Verstärkerkolben 28 sich in der in der Fig. 7 gezeigten Ruhestellung befindet. In dieser liegen die Anschlagnasen 80 am Boden der Verlängerung 124 an.Accordingly, the piston guide space 74 has an extension 124 into which the piston projection 122 is immersed by the length designated L when the booster piston 28 is in the rest position shown in FIG. In this stop the lugs 80 at the bottom of the extension 124 at.
Beim Oeffnen des Steuerventils 24 wird zuerst nur der Kolbenvorsprung 122 mit Steuerdruck beaufschlagt. Es findet somit vorerst eine geringe Druckverstärkung statt, da der Durchmesser Da kleiner als der Durchmesser desWhen opening the control valve 24, only the piston projection 122 is first subjected to control pressure. Thus, for the time being, a slight pressure increase takes place, since the diameter Da is smaller than the diameter of the
Kolbenteils 28' ist. Hat sich jedoch der VerstärkerkolbenPiston part 28 'is. However, the amplifier piston has
28 um den Hub L in Richtung zum Kolbenabtriebsraum 84 - vergleiche Fig. 1 - zu bewegt, wird der gesamte Kolbenteil 28' mit Steuerdruck beaufschlagt, wodurch die volle Druckverstärkung erfolgt.28 to the stroke L in the direction of Kolbenabtriebsraum 84 - see Fig. 1 - moves to, the entire piston part 28 'applied with control pressure, whereby the full pressure amplification takes place.
Es ist auch möglich, wie in Fig. 7 gestrichelt angedeutet, am Kolbenvorsprung 122, umfangsseitig verteilt, in Richtung zum freien Ende des Kolbenvorsprungs 122 hin sich in Querschnitt vergrössernde Verbindungsnuten 126 auszubilden. Dadurch kann der Uebergang von geringer Druckverstärkung auf die volle Druckverstärkung kontinuierlich gestaltet werden. Ein Drosseldurchlass zwischen der Verlängerung 124 und dem Antriebsraum 76 hätte eine ähnliche Wirkung (in Fig. 7 nicht gezeigt) .It is also possible, as indicated by dashed lines in FIG. 7, on the piston projection 122, circumferentially distributed, in the direction of the free end of the piston projection 122, connecting grooves 126 which increase in cross section are formed. As a result, the transition from low pressure boost to full pressure boost can be made continuous. A throttle passage between the extension 124 and the drive space 76 would have a similar effect (not shown in FIG. 7).
Die Fig. 8 und 9 zeigen eine Ausführungsform mit Druckkompensation, welche jener in den Fig. 5 und 6 gezeigten Ausführungsform sehr ähnlich ist. Der konstruktive Aufbau ist jedoch mit mehr Details gezeigt.Figs. 8 and 9 show an embodiment with pressure compensation, which is very similar to that shown in Figs. 5 and 6 embodiment. The structural design is shown with more details.
In einer zur Achse 16 zentrischen abgestuft ausgebildeten Gehäuseausnehmung 128 - diese schliesst an die Ausnehmung 18 an - ist ein pillenartiger Steuerventilsitzkörper 130 eingesetzt. Mit der einen Stirnseite liegt dieser dichtend am Boden der Gehäuseausnehmung 128 an und an der anderen Stirnseite sind der Steuerventilsitz 66, die Einlassnut 68 und die Auslassöffnung 104 ausgebildet. Eine parallel zur Achse 16 durch den Steuerventilsitzkörper 130 hindurchgehende Bohrung bildet einen Teil des Verbindungskanals 78, welcher beim Boden der Gehäuseausnehmung 128 mit einem am Gehäuse 10 ausgebildeten, zum Kolbenantriebsraum 76 führenden weiteren Teil des Verbindungskanals 78 strömungsverbunden ist.In a graduated recess 16 to the axis of the housing recess 128 - this connects to the recess 18 - a pill-like control valve seat body 130 is inserted. With one end face of this sealingly against the bottom of the housing recess 128 and at the other end face of the control valve seat 66, the inlet groove 68 and the outlet opening 104 are formed. A bore passing through the control valve seat body 130 parallel to the axis 16 forms part of the connection channel 78 which is fluidly connected to the bottom of the housing recess 128 with a further part of the connection channel 78 formed on the housing 10 leading to the piston drive chamber 76.
Der die Einlassnut 68 mit Brennstoff speisende Ringkanal 68 ' erstreckt sich von der bodenseitigen Stirnfläche des Steuerventilkörpers 130 bis zur Einlassnut 68, wobei der Ringkanal 68' jedoch durch drei umfangsseitig verteilte Stege 132, in der der Einlassnut 68 zugewandten Hälfte des Steuerventilsitzkörpers 130, unterteilt ist. Diese Stege 132 verbinden den bezüglich des Ringkanals 68' radial innen liegenden Teil des Steuerventilsitzkörpers 130 mit dem radialen aussen liegenden Teil; siehe insbesondere Fig. 9. In einem dieser Stege 132 verläuft eine, den weiteren Verbindungskanal 78' bildende Schrägbohrung von der Auslassöffnung 104 zum Verbindungskanal 78. Durch einen weiteren Steg 132 hindurch verläuft der Kompensationsniederdruckdurchlass 120. Dieser mündet aus der Zylinderausnehmung 114, welche sacklochartig am Steuerventilsitzkörper 130 ausgenommen und andererseits vom Boden der Gehäuseausnehmung 128 verschlossen ist.The inlet groove 68 with fuel feeding annular channel 68 'extending from the bottom end face of the Control valve body 130 to the inlet groove 68, wherein the annular channel 68 ', however, by three circumferentially distributed webs 132, in which the inlet groove 68 facing half of the control valve seat body 130, is divided. These webs 132 connect with respect to the annular channel 68 'radially inner part of the control valve seat body 130 with the radially outer part; see in particular Fig. 9. In one of these webs 132, a, the further connecting channel 78 'forming inclined bore extends from the outlet opening 104 to the connecting channel 78. Through a further web 132 passes through the Kompensationsniederdruckdurchlass 120. This opens out of the cylinder recess 114, which blind hole on Control valve seat body 130 except and on the other hand closed from the bottom of the housing recess 128.
In der Zylinderausnehmung 114 ist der hohlzylinderförmig ausgebildete Kompensationskolben 112 in enger Gleitpassung aufgenommen, welcher auf dem diesseitigen Endbereich des einstückig mit dem Betätigungsschaft 62 ausgebildeten Schafts 62' fest sitzt. Der Kompensationsdruckraum 116 ist über einen in radialer Richtung verlaufenden Durchlass mit dem Ringkanal 68 ' verbunden, welcher seinerseits beim Boden der Gehäuseausnehmung 128 mit dem am Gehäuse 10 ausgenommenen Steuerdruckkanal 70 strömungsverbunden ist.In the cylinder recess 114 of the hollow cylindrical compensating piston 112 is received in close sliding fit, which sits firmly on the this side end portion of the integrally formed with the operating shaft 62 shaft 62 '. The compensation pressure chamber 116 is connected via a radially extending passage with the annular channel 68 ', which in turn at the bottom of the housing recess 128 with the recessed on the housing 10 control pressure channel 70 is fluidly connected.
Weiter sind in den Steuerventilsitzkörper 130 zwei Positionierungsstifte 134 eingelassen, welche in entsprechende Sacklöcher im Boden der Gehäuseausnehmung 128 zur Festlegung der Drehlage des Steuerventilsitzkörpers 130 bezüglich des Gehäuses 10 eingreifen. Auf der dem Boden der Gehäuseausnehmung 128 abgewandten Stirnseite des Steuerventilsitzkörpers 130 sitzt eine Ringscheibe 136, welche den Steuerventilraum 56 umfangsseitig begrenzt und deren Innendurchmesser derart gewählt ist, dass der Verbindungskanal 78 mit dem Steuerventilraum 56 strömungsverbunden ist.Further, in the control valve seat body 130, two positioning pins 134 are inserted, which engage in corresponding blind holes in the bottom of the housing recess 128 for fixing the rotational position of the control valve seat body 130 with respect to the housing 10. On the bottom of the housing recess 128 facing away from the end face of the control valve seat body 130 sits an annular disc 136, which limits the control valve chamber 56 circumferentially and the inner diameter is selected such that the connecting channel 78 is fluidly connected to the control valve chamber 56.
Auf der dem Steuerventilsitzkörper 130 abgewandten Seite ist der Steuerventilraum 56 durch eine Scheibe 138 begrenzt, welche auf der Ringscheibe 136 anliegt und mit einer zentralen Bohrung 140 versehen ist, welche vom Betätigungsschaft 62 mit radialem Spiel durchgriffen ist. Der Ringspalt zwischen dem Betätigungsschaft 62 und der Scheibe 138 bildet den Entlastungskanal 64' . Im Steuerventilraum 56 sitzt das scheibenartig ausgebildete Steuerventilglied 58 auf dem Betätigungsschaft 62.On the side facing away from the control valve seat body 130, the control valve chamber 56 is delimited by a disc 138, which rests on the annular disc 136 and is provided with a central bore 140 which is penetrated by the operating shaft 62 with radial play. The annular gap between the operating shaft 62 and the disc 138 forms the discharge channel 64 '. In the control valve chamber 56 sits the disk-like control valve member 58 on the operating shaft 62nd
Auf der dem Steuerventilraum 56 abgewandten Seite der Scheibe 138 ist eine ringartige, mit einem Innensechskant versehene Schraube 142 angeordnet, welche mit ihrem Aussengewinde in ein Innengewinde im Bereich der Gehäuseausnehmung 128 eingewindet ist. Diese beaufschlagt die Scheibe 138, die Ringscheibe 136 und den Steuerventilsitzkörper 130 mit einer axialen Kraft, so dass diese dichtend aneinander und der Steuerventilsitzkörper 130 dichtend am Boden der Gehäuseausnehmung 128 anliegen.On the side facing away from the control valve chamber 56 side of the disc 138, an annular, provided with a hexagon screw 142 is arranged, which is threaded with its external thread in an internal thread in the region of the housing recess 128. This acts on the disc 138, the washer 136 and the control valve seat body 130 with an axial force, so that these sealingly against each other and the control valve seat body 130 sealingly abut the bottom of the housing recess 128.
Die Innensechskantschraube 142 begrenzt innen einen Teilraum der Gehäuseausnehmung 128, der sich dem Niederdruckraum 50 anschliesst. Der Niederdruckdurchlass 52 ist durch eine Radialbohrung im Gehäuse 10 gebildet. Auf dem diesseitigen Ende des Gehäuses 10 sitzt das Aktuatorgehäuse 38, welches zusammen mit dem darin eingesetzten Aktuator 22 den Niederdruckraum 50 begrenzt.The hexagon socket screw 142 bounded inside a partial space of the housing recess 128, which adjoins the low pressure chamber 50. The low pressure passage 52 is formed by a radial bore in the housing 10. The actuator housing 38, which together with the actuator 22 inserted therein defines the low-pressure space 50, sits on the downstream end of the housing 10.
Bei der in den Fig. 8 und 9 gezeigten Ausbildungsform ist der Betätigungsschaft 62 mit dem Aktuatorschaft 48 fest verbunden. Bei einer derartigen Ausbildungsform kann der Kompensationskolben 112 derart ausgebildet werden, dass er die auf das Steuerventilglied 58 wirkenden Kräfte vollständig kompensiert.In the embodiment shown in FIGS. 8 and 9, the operating shaft 62 is fixedly connected to the actuator shaft 48. In such an embodiment, the compensating piston 112 may be configured to fully compensate for the forces acting on the control valve member 58.
Der Vollständigkeit halber sei erwähnt, dass die Scheibe 138 auch den Sitz für die Dichtschulter 106 des Steuerventilgliedes 58 bildet, um bei geöffnetem Steuerventil 24 den Steuerventilraum 56 vom Niederdruckraum 50 abzutrennen.For the sake of completeness it should be mentioned that the disc 138 also forms the seat for the sealing shoulder 106 of the control valve member 58 in order to separate the control valve chamber 56 from the low-pressure chamber 50 when the control valve 24 is open.
Wird ein elektromagnetisch betätigter Aktuator 22 verwendet, bildet die Scheibe 138 in Zusammenwirkung mit dem Steuerventilglied 58 auch den Anschlag für den Aktuator bzw. dessen Anker. Weiter lassen sich bei dieser Ausführungsform durch die Wahl der Dicke der Ringscheibe 136 und der axialen Dimension des Steuerventilgliedes 58 der Hub des Aktuators 22 einstellen.If an electromagnetically actuated actuator 22 is used, the disc 138 in cooperation with the control valve member 58 also forms the stop for the actuator or its armature. Further, in this embodiment, by selecting the thickness of the washer 136 and the axial dimension of the control valve member 58, the stroke of the actuator 22 can be adjusted.
Bei den in den Fig. 4 - 9 gezeigten Ausbildungsformen wirkt das als Flachsitzventil ausgebildete Steuerventil 24 als 2/3-Wege-Ventil.In the embodiments shown in FIGS. 4 to 9, the control valve 24 designed as a flat seat valve acts as a 2/3-way valve.
Die in den Fig. 1 - 9 gezeigten Brennstoffeinspritzventile funktionieren wie folgt. Ausgehend von dem in den Fig. 1 und 6 gezeigten Zustand mit geschlossenem Steuerventil 24 und am Einspritzventilsitz 32 anliegenden Einspritzventilglied 34 wird für eine Brennstoffeinspritzung der Aktuator 22 derart angesteuert, dass sich der Aktuatorschaft 48 in Richtung von Steuerventilsitz 66 wegbewegt. Dadurch bewegt sich auch das Steuerventilglied 58 vom Steuerventilsitzglied 66 weg in die in den Fig. 2, 4, 5, 7 und 8 gezeigte Offenstellung, wodurch der Kolbenantriebsraum 76 mit Steuerdruck beaufschlagt wird. Dies führt zu einer Bewegung des Verstärkerkolbens 28 in Richtung zum Kolbenabtriebsraum 84 hin, wodurch diesseitig der Druck des Brennstoffs im Kolbenabtriebsraum 84, in der Hochdruckleitung 88 und im Brennstoffhochdruckraum 30 verstärkt wird. Dadurch nimmt die auf das Einspritzventil 34 wirkende hydraulische Kraft zu, so dass es, entgegen der Kraft der Schliessfeder 96 und die durch den Steuerdruck im Zylinderraum 36 erzeugten Kraft, vom Einspritzventilgliedsitz 32 abgehoben wird. Dadurch erfolgt eine Einspritzung von Brennstoff, welcher unter dem durch den Verstärkerkolben 28, gegenüber dem am Steuerdruckeinlass 26 anstehenden Steuerdruck, erhöhten Druck steht.The fuel injectors shown in Figs. 1-9 operate as follows. Starting from the state shown in FIGS. 1 and 6 with the control valve 24 closed and injection valve member 34 resting against the injection valve seat 32, the actuator 22 is actuated in such a way for fuel injection, the actuator shaft 48 moves away from the control valve seat 66. As a result, the control valve member 58 moves away from the control valve seat member 66 in the open position shown in Figs. 2, 4, 5, 7 and 8, whereby the piston drive chamber 76 is supplied with control pressure. This leads to a movement of the booster piston 28 in the direction of the piston output space 84, as a result of which the pressure of the fuel in the piston output space 84, in the high-pressure line 88 and in the high-pressure fuel chamber 30 is intensified on the side. As a result, the hydraulic force acting on the injection valve 34 increases, so that it is lifted off the injection valve member seat 32, counter to the force of the closing spring 96 and the force generated by the control pressure in the cylinder space 36. This results in an injection of fuel, which is below the pressure applied by the booster piston 28, compared to the control pressure applied to the control pressure inlet 26.
Zur Beendigung des Einspritzvorgangs wird der Aktuator 22 derart angesteuert, dass sich der Aktuatorschaft 48 in Richtung gegen den Steuerventilsitz 66 hin bewegt und dadurch das Steuerventil 24 geschlossen wird. Durch die Verbindung des Steuerventilraumes 56 und somit des Kolbenantriebsraumes 76 durch den Drosselkanal 64 bzw. Entlastungskanal 64' mit dem Niederdruckraum 50 bewegt sich der Differenzialkolben nun in entgegen gesetzter Richtung, wodurch sehr rasch der Druck des Brennstoffs im Brennstoffhochdruckraum 30 absinkt und sich das Einspritzventilglied 34 in Richtung zum Einspritzventilsitz 32 hin bewegt und dadurch den Einspritzvorgang beendet. Ist zwischen dem Steuerdruckeinlass 26 und dem Kolbenabtriebsraum 84 Druckausgleich gegeben, fliesst - indem das Rückschlagventil 92 öffnet - Brennstoff in den Kolbenabtriebsraum 84 nach, bis der Verstärkerkolben 28 mit seiner Anschlagnase 80 am Gehäuse 10 anliegt. Das Brennstoffeinspritzventil ist nun für einen weiteren Einspritzvorgang bereit. Bei Mehrfacheinspritzungen muss der Verstärkerkolben 28 in den kurzen Pausen zwischen den einzelnen Einspritzungen sich nicht zwangsläufig zurückbewegen oder gar den ganzen Weg in Richtung zum Ende des Kolbenantriebsraums 76 hin zurücklegen.To end the injection process, the actuator 22 is driven such that the actuator shaft 48 moves in the direction against the control valve seat 66 and thereby the control valve 24 is closed. By connecting the control valve chamber 56 and thus the piston drive chamber 76 through the throttle channel 64 and discharge channel 64 'with the low-pressure chamber 50, the differential piston now moves in the opposite direction, causing the pressure of the fuel in the high-pressure fuel chamber 30 drops rapidly and the injection valve member 34th moved toward the injection valve seat 32 and thereby terminates the injection process. Is between the control pressure inlet 26 and the Kolbenabtriebsraum 84th Given pressure equalization, flows - by the check valve 92 opens - fuel in the Kolbenabtriebsraum 84 until the booster piston 28 rests with its stop lug 80 on the housing 10. The fuel injection valve is now ready for another injection process. In multiple injections, the booster piston 28 need not necessarily move back or even all the way toward the end of the piston drive chamber 76 in the short pauses between each injection.
Flachsitzventile haben, wie anhand der gezeigten Ausführungsbeispiele dargelegt, die Eigenschaft, bereits bei sehr geringem Oeffnungshub einen sehr grossen Strömungsquerschnitt freizugeben.Flat seat valves have, as explained with reference to the exemplary embodiments shown, the property of releasing a very large flow cross-section even at a very small opening stroke.
Wie bereits weiter oben erwähnt, eignet sich das erfindungsgemässe Brennstoffeinspritzventil auch für Mehrfacheinspritzungen. As already mentioned above, the fuel injection valve according to the invention is also suitable for multiple injections.

Claims

Patentansprüche claims
1. Brennstoffeinspritzventil zur intermittierenden Brennstoffeinspritzung in den Brennraum einer Verbrennungskraftmaschine, mit einem an einen Brennstoffhochdruckraum (30) angrenzenden Einspritzventilsitz (32), einem nadeiförmigen Einspritzventilglied (34), das einerseits mit dem Einspritzventilsitz (32) zusammenwirkt und andererseits kolbenartig einen mit einem Steuerdruckeinlass (26) für den Brennstoff verbundenen Zylinderraum (36) begrenzt, einem als Differentialkolben wirkenden Verstärkerkolben (28), der steuerdruckseitig einen über ein mittels eines elektrisch angesteuerten Aktuators (22) gesteuertes Steuerventil (24) mit .. dem Steuerdruckeinlass (26) verbindbaren und von diesem abtrennbaren Kolbenantriebsraum (76) und hochdruckseitig einen mit dem Brennstoffhochdruckraum (30) verbundenen Kolbenabtriebsraum (84) begrenzt, wobei das Steuerventil (24) als Flachsitzventil ausgebildet istA fuel injector for intermittent fuel injection into the combustion chamber of an internal combustion engine having an injection valve seat (32) adjacent to a fuel high pressure space (30), a needle-shaped injection valve member (34) cooperating with the injector seat (32) on the one hand and a piston having a control pressure inlet (FIG. 26) for the fuel-connected cylinder chamber (36) limited, acting as a differential piston booster piston (28), the control pressure side via a means of an electrically controlled actuator (22) controlled control valve (24) with .. the control pressure inlet (26) connectable and this detachable piston drive chamber (76) and the high pressure side, a piston output space (84) connected to the high-pressure fuel chamber (30) is limited, wherein the control valve (24) is designed as a flat seat valve
2. Brennstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass das Flachsitzventil ein scheibenartig ausgebildetes Steuerventilglied (58) und einen mit diesem zusammenwirkenden Steuerventilsitz (66) aufweist, in dessen Bereich eine mit dem Steuerdruckeinlass (26) verbundene, wenigstens annähernd kreisringförmige Einlassnut (68) angeordnet ist.2. Fuel injection valve according to claim 1, characterized in that the flat seat valve has a disc-like design control valve member (58) and a cooperating with this control valve seat (66), in the region of which connected to the control pressure inlet (26), at least approximately annular inlet groove (68) is arranged.
3. Brennstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, dass im Bereich des Steuerventilsitzes3. Fuel injection valve according to claim 2, characterized in that in the region of the control valve seat
(66), zentrisch und in einem Abstand zur Einlassnut (68) eine mit dem Kolbenantriebsraum (76) verbundene Auslassöffnung (104) angeordnet ist(66), centric and at a distance from the inlet groove (68) disposed with the piston drive chamber (76) outlet opening (104) is arranged
4. Brennstoffeinspritzventil nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass das Steuerventilglied (58) an einem mit dem Aktuator (22) zusammenwirkenden, in einer Gleitpassung geführten Betätigungsschaft (62) angeordnet ist.4. Fuel injection valve according to claim 2 or 3, characterized in that the control valve member (58) on one with the actuator (22) cooperating, guided in a sliding fit operating shaft (62) is arranged.
5. Brennstoffeinspritzventil nach einem der Ansprüche 2 bis 4, dadurch gekennzeichnet, dass das Steuerventilglied (58) mit einem, einen mit dem5. Fuel injection valve according to one of claims 2 to 4, characterized in that the control valve member (58) with one, one with the
Hochdruckeinlass (26) verbundenenHigh pressure inlet (26) connected
Kompensationsdruckraum (116) begrenzendenCompensating pressure chamber (116) limiting
Kompensationskolben (28) verbunden ist.Compensating piston (28) is connected.
6. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass der6. Fuel injection valve according to one of claims 1 to 5, characterized in that the
Kolbenabtriebsraum (84) über ein Rückschlagventil (92) mit dem Hochdruckeinlass (26) verbunden ist.Kolbenabtriebsraum (84) via a check valve (92) to the high pressure inlet (26) is connected.
7. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass der Kolbenantriebsraum (76) über einen Drosseldurchlass (64) mit einem Niederdruckauslass (54) verbunden ist.7. Fuel injection valve according to one of claims 1 to 6, characterized in that the piston drive chamber (76) via a throttle passage (64) with a low-pressure outlet (54) is connected.
8. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass der Kolbenantriebsraum (76) über einen Durchlass (64') mit einem Niederdruckauslass (54) verbunden ist und der Niederdruckauslass (54) bei geöffnetem Steuerventil (24) , vorzugsweise durch das Steuerventilglied (58), verschlossen ist. 8. Fuel injection valve according to one of claims 1 to 6, characterized in that the piston drive chamber (76) via a passage (64 ') with a low pressure outlet (54) is connected and the low pressure outlet (54) with open control valve (24), preferably by the control valve member (58) is closed.
9. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass der Verstärkerkolben (28) niederdruckseitig abgestuft ausgebildet ist und der Kolbenantriebsraum (76) wenigstens annähernd gegengleich abgestuft begrenzt ist.9. Fuel injection valve according to one of claims 1 to 8, characterized in that the booster piston (28) is designed stepped down low pressure side and the piston drive chamber (76) is at least approximately stepped counterparts limited.
10. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass der Aktuator (22). als Piezoaktuator ausgebildet ist.10. Fuel injection valve according to one of claims 1 to 9, characterized in that the actuator (22). is designed as a piezo actuator.
11. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, dass das Steuerventil11. Fuel injection valve according to one of claims 1 to 10, characterized in that the control valve
(24) einen an einer Stirnseite eines(24) one at a front side of a
Steuerventilsitzkörpers • (130) ausgebildetenControl valve seat body trained (130)
Steuerventilsitz (66) aufweist und zwischen dem Aktuator (22) und dem Steuerventilsitzkörper (130) eine Ringscheibe (136) wählbarer Dicke angeordnet ist. Control valve seat (66) and between the actuator (22) and the control valve seat body (130) an annular disc (136) of selectable thickness is arranged.
EP05798800A 2004-12-03 2005-11-08 Fuel injection valve with pressure gain Not-in-force EP1836385B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH20062004 2004-12-03
PCT/CH2005/000656 WO2006058444A1 (en) 2004-12-03 2005-11-08 Fuel injection valve with pressure gain

Publications (2)

Publication Number Publication Date
EP1836385A1 true EP1836385A1 (en) 2007-09-26
EP1836385B1 EP1836385B1 (en) 2010-12-29

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Application Number Title Priority Date Filing Date
EP05798800A Not-in-force EP1836385B1 (en) 2004-12-03 2005-11-08 Fuel injection valve with pressure gain

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US (1) US7513241B2 (en)
EP (1) EP1836385B1 (en)
AT (1) ATE493577T1 (en)
DE (1) DE502005010779D1 (en)
WO (1) WO2006058444A1 (en)

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Also Published As

Publication number Publication date
DE502005010779D1 (en) 2011-02-10
WO2006058444A1 (en) 2006-06-08
US20080115765A1 (en) 2008-05-22
EP1836385B1 (en) 2010-12-29
US7513241B2 (en) 2009-04-07
ATE493577T1 (en) 2011-01-15

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