EP2961977B1 - Apparatus to inject fuel in the combusion chamber of a combustion engine - Google Patents

Description

The present invention relates to a device for the intermittent injection of high-pressure fuel into the combustion chamber of an internal combustion engine according to claim 1.

A device with injectors for injecting fuel into the combustion chamber of an internal combustion engine is in the earlier international application WO 2013/117311 A disclosed. The injection valves of the device have a valve housing with a connection body, a memory body adjoining this with a discrete storage chamber, an intermediate body adjoining this, in which an electrically actuated actuator arrangement is accommodated, and a valve body adjoining the intermediate body. The valve body carries at its free end a nozzle body with an injection valve seat and nozzle openings for injecting the fuel into the combustion chamber of the internal combustion engine. With the injection valve seat, a needle-shaped injection valve member cooperates, which is formed on the side facing away from the injector seat piston-shaped. On the injection valve member, a closing spring is supported, which acts on the injection valve member with a directed in the direction of the injection valve seat closing force. On the other hand, the closing spring is supported on a guide sleeve of a hydraulic control device. The piston and the guide sleeve limit a control space which is connected to a pilot valve operated by means of the actuator. To trigger an injection process, the pilot valve is opened, so that fuel can flow out of the control chamber and thereby the injection valve member is lifted against the force of the closing spring from the injector seat. To end the injection process, the pilot valve is closed by means of the actuator assembly, after which the control chamber is refilled with fuel, and the injection valve member comes to rest on the injection valve seat.

On the connection body there are two identically formed high-pressure connections connected to one another in terms of flow, one of which serves to be connected to a supply line for supplying the injection valve with fuel. A connecting line can be connected to the other high-pressure connection in order to supply fuel to another injection valve.

The storage body has a larger diameter bore to form the discrete storage chamber. In an end portion facing the connector body, the blind bore has a larger diameter to form a shoulder for supporting a valve carrier of a check valve. The check valve seat is formed on the connection body, and with it a platelet-shaped check valve body cooperates, which has a continuous throttle bore in the center. The non-return valve body is acted upon by means of a closing spring designed as a compression spring, which is supported on the other end of the valve carrier, with a directed in the closed position of the check valve closing force.

Centrally through the valve carrier passes through a passage, and the valve carrier closes the storage chamber in the axial direction from the connection body out. The check valve forming a throttle device allows the flow of fuel from the high pressure ports into the storage chamber at least approximately unhindered and throttles the flow in the opposite direction. Next, the valve carrier carries a cup-shaped hole filter, which protrudes from the valve carrier into the interior of the storage chamber and in which the passage opens through the valve carrier.

Another device for the intermittent injection of high-pressure fuel into the combustion chamber of an internal combustion engine is from the document WO 2007/009279 A known. Each injection valve of this device is associated with a discrete storage chamber, wherein between the feed line and the storage chamber, a check valve with parallel throttle acts. If a plurality of such fuel injection valves or a plurality of injection valves, as disclosed in the above-mentioned CH and WO patent application, connected to each other and to a high-pressure fuel pump, the throttling action of the check valve is designed such that each fuel injection valve during an injection process high-pressure fuel from the discrete storage chambers other fuel injectors, from the high-pressure fuel lines and from the high-pressure fuel pump feeds. This functionality is in the document WO 2007/009279 A in detail and also in the document WO 2009/033304 A described.

In the context of the present invention, reference is expressly made to the above-mentioned documents with regard to the dimensioning of the storage chamber, the action of the check valves and the throttling action.

Moreover, devices for injecting fuel into the combustion chamber of internal combustion engines are known from the documents EP 2 188 516 B1 and CH 702 496 B1 known.

It is an object of the present invention to further develop the apparatus for intermittently injecting high pressure fuel into the combustion chamber of an internal combustion engine so that it can be more easily manufactured and assembled.

This object is achieved with a device having the features of claim 1.

The apparatus comprises a fuel injector, preferably a plurality of identically formed fuel injectors, having a housing with a high pressure inlet, a recess, and a high pressure chamber connected to the high pressure inlet. Preferably, the recess forms at least a part of the high-pressure chamber. The fuel injection valve is associated with a valve carrier having a fuel passage and a check valve. Vorzugseise the check valve is arranged in the valve carrier. A feed line for supplying fuel to the fuel injection valve is tensioned by means of a fastening element in the direction of the high-pressure inlet and fluidly connected thereto.

The high-pressure inlet has a conical sealing surface that widens from the interior of the housing in the direction toward the outside. This forms, in other words, an inner cone. The valve carrier has, on an outer circumferential surface, a conical outer sealing surface, which bears sealingly against the conical sealing surface of the high-pressure inlet. The fastener presses the feed line to the valve carrier, and this to the high pressure inlet.

The valve carrier preferably further has an inner cone on an input-side front side, which also forms a sealing surface. In its end region facing the fuel valve, the feed line has an outer cone forming a sealing surface, which sealingly bears against the inner cone of the valve carrier.

The valve carrier is held quasi clamped between the feed line and the housing. The high-pressure sealing concerns on the one hand of the valve carrier on the housing and on the other hand, the feed line on the valve carrier is achieved in that the fastener, such as a union nut, the supply line tensioned in the direction against the high pressure inlet.

If the supply line is connected to the fuel injection valve on site, it may be advantageous to fix the valve carrier to the housing. However, this fixation need not - but can - apply such a force that the valve carrier sealingly abuts the conical sealing surface of the high pressure inlet.

Preferably, the valve carrier has a funnel-shaped end flange on which both the conical outer sealing surface and the inner cone are formed. This leads to a space-saving embodiment and allows in the funnel-shaped end flange an optimal pressure or stress distribution between the outer cone of the feed line and the conical sealing surface of the high pressure inlet, so that in a simple manner a secure high-pressure seal can be achieved.

Further, in a preferred manner, the conical sealing surface of the high pressure inlet on the housing itself - as a portion of the recess - formed. This leads to a particularly simple and space-saving embodiment.

The sealing effect between on the one hand the conical sealing surface of the high-pressure inlet and the conical outer sealing surface of the valve carrier and on the other hand between the inner cone of the valve carrier and the outer cone of the feed line can be achieved particularly well, if in each case a cone angle difference of 0.5 ° to 2 ° is present, i. the two cooperating cones enclose a corresponding angle, which opens in the radial direction to the outside. As a result, sealing annular surfaces are formed at the respective smallest diameter of the interaction of the corresponding cones.

Preferably, the valve carrier is formed together with the check valve and attached to the valve carrier, preferably a further fuel passage having retaining element as a cartridge-like, self-contained unit. This preassembled unit can then as such in the recess or the high-pressure chamber of the housing Fuel injector are used, or is used as such.

This makes it easier to form the housing and in particular the - pre-assemble the entire fuel injector - except for the unit and only then to assemble the unit to the housing.

This further has the advantage that the assembly as such can be tested separately and, moreover, a simple replacement of the check valve is possible.

In a preferred embodiment, the assembly comprises a filter for the fuel, which is preferably carried by the holding member and secured thereto.

In this case, the assembly of the valve carrier, the check valve, the holding element and the filter is formed.

In a preferred embodiment, the filter has a cup-like filter body, with the further fuel passage opening into the cavity defined by the filter body.

In particular, the filter body is provided with a large number, for example at least 2,000, microholes.

Preferably, an annular check valve seat is formed on the valve carrier, which cooperates with a check valve member which is arranged between the valve carrier and the holding element.

More preferably, the check valve member is formed as a valve plate, and this is preferably provided centrally with a throttle passage. This is even with closed check valve with the fuel passage and thus the feed line fluidly connected.

More preferably acts between the valve plate and the holding element, a compression spring which acts on the valve plate with a force acting in the closed position force. However, this is low and only ensures that when pressure equalization, the valve plate rests against the check valve seat.

Preferably, the valve plate has at least one in the direction of radially outwardly open and continuous in the direction of the longitudinal axis breakthrough - preferably three (or more) circumferentially distributed such breakthroughs - on. This allows a low-resistance, unthrottled flow through the fuel between the valve plate located in the open position and the surrounding valve carrier or holding element. The breakthrough is located or the openings are located radially outside the check valve seat.

Furthermore, the retaining element preferably has, in its end region facing the valve plate, at least one groove open in the direction of the valve plate and extending in the radial direction, preferably three such grooves (or more) distributed in the circumferential direction. This allows, with open check valve, as low as possible flow of the fuel.

In a particularly preferred manner, the high-pressure chamber of the injection valve has a discrete storage chamber for storing fuel. The interpretation of such discrete storage chambers and their interaction with the check valve and throttling is in document WO 2007/009297 A in detail and also in the document WO 2009/033304 A described. It is explicitly referred to these documents.

Preferably, the above-mentioned structural unit, in particular with the filter, projects into the discrete storage chamber.

In a preferred embodiment, the housing of the fuel injection valve carries a nozzle body, which is connected to the high-pressure chamber and on which an injection valve is formed. With the latter acts in the direction of the longitudinal axis adjustable arranged injection valve member together. A, preferably designed as a compression spring, closing spring is supported on the injection valve member and acts upon this with a directed in the direction against the injection valve seat closing force. Further, a hydraulically controlled control device is provided in the housing to lift the injection valve member against the closing force of the compression spring from the injection valve seat for injecting fuel. The hydraulic control device is controlled by means of a likewise arranged in the housing, electrically controlled actuator in a known manner.

The actuator and the hydraulic control device can be designed in any manner, in particular such as, for example, in the above-mentioned CH patent application no. 2012 0174/12 , in the pamphlets WO 2007/009279 . WO 2010/088781 A1 . WO 2008/046238 A . WO 2006/108309 A . WO 2006/058444 A . WO 2005/080785 A . WO 2005/019637 A . WO 2005/003550 A or WO 2004/099603 A disclosed.

In one embodiment, the housing has on the one hand a valve housing, which carries the nozzle body and in which the injection valve member, the closing spring, the actuator and the control device are arranged, and on which a conical pressing surface, which serves as a sealing surface is formed. From this sealing surface runs in the valve housing, the high-pressure chamber for the fuel. On the other hand, the housing has a discharge nozzle, at the nozzle housing of which the high-pressure inlet is formed and whose longitudinal axis extends transversely, preferably at right angles to the longitudinal axis of the valve housing. The pressure port has, in an end region facing away from the high-pressure inlet, a conical counter-contact surface, which likewise forms a sealing surface. The Gegenandrückfläche is sealingly against the Andrückfläche, and in the discharge nozzle, the discrete storage chamber or a portion of the discrete storage chamber is formed, if one is present. The fuel is supplied through the discharge nozzle to the high-pressure chamber.

In this embodiment too, the valve carrier with its conical outer sealing surface bears against the conical sealing surface, which is preferably integrally formed on the pressure nozzle housing. Further, the outer cone of the feed line preferably abuts against the inner cone of the valve carrier, and the feed line by means of the fastener is in the direction towards the high pressure inlet, i. clamped against the nozzle housing.

In connection with the embodiment of the injection valve with discharge nozzle is on the document WO 2009/033304 A directed.

Preferably, the housing or the nozzle housing has a high-pressure inlet which is arranged next to the high-pressure inlet and which is flow-connected to the high-pressure inlet, preferably without throttling and in order to supply a further injection valve with fuel via a high-pressure connection line connected to the high-pressure outlet. The operation of this embodiment is in the WO 2007/009279 A and also in the document WO 2009/033304 A described.

The high-pressure outlet preferably has an inner cone molded onto the housing or connecting piece housing, against which the outer cone of the connecting line rests sealingly.

Preferably, the valve carrier between the inner cone and the check valve on a radial outlet from the fuel passage, which is flow-connected via a connecting line in the housing or nozzle housing with the high pressure outlet. As a result, the supply line is connected to the connecting line low-resistance free throttling.

Preferably, the valve carrier, seen in the flow direction of the fuel in the injection valve, downstream of the radial outlet with the housing or nozzle housing defines a narrow gap. As a result, the high-pressure chamber or the discrete storage chamber is separated from the connecting line hydraulically, at least for transient processes.

Fig. 1

einen Längsschnitt durch eine erste Ausführungsform der erfindungsgemässen Vorrichtung zum intermittierenden Einspritzen von unter Hochdruck stehendem Brennstoff in den Brennraum einer Verbrennungskraftmaschine, wobei ein Einspritzventil und eine diesem zugeordnete Speiseleitung gezeigt ist; die Vorrichtung kann selbstverständlich mehrere Einspritzventile und jedes dieser Einspritzventile eine Speiseleitung aufweisen;

Fig. 2

gegenüber Fig. 1 vergrössert einen Teil der dort gezeigten Ausführungsform;

Fig. 3

gegenüber Fig. 2 vergrössert einen Teil der in den Fig. 1 und 2 gezeigten Vorrichtung;

Fig. 4

in perspektivischer Darstellung ein Halteelement und ein als Ventilplättchen ausgebildetes Rückschlagsventilglied, welche zusammen mit einem Ventilträger und gegebenenfalls einem Filter eine patronenartige, eigenständige Baueinheit bilden;

Fig. 5

eine weitere Ausführungsform der erfindungsgemässen Vorrichtung, wobei das Gehäuse einerseits ein Ventilgehäuse mit einer seitlichen konischen Andrückfläche und andererseits einen Druckstutzen aufweist, an welchem der Hochdruckeinlass ausgebildet ist;

Fig. 6

im Längsschnitt einen Teil des Druckstutzens und der an diesen angeschlossenen Speiseleitung;

Fig. 7

eine weitere Ausführungsform, bei welcher das Gehäuse des Einspritzventils bzw. des Druckstutzens neben dem Hochdruckeinlass mit einem Hochdruckauslass ausgestattet ist;

Fig. 8

gegenüber Fig. 7 vergrössert einen Teil der dort gezeigten Ausführungsform;

Fig. 9

in perspektivischer Darstellung die patronenartige, eigenständige Baueinheit mit dem Ventilträger, dem Halteelement und dem von diesem getragenen Filter, wobei im Ventilträger das Rückschlagventil angeordnet ist;

Fig. 10

in Ansicht das Halteelement und einen Stabfilter, wobei diese beiden Teile integral miteinander ausgebildet sind;

Fig. 11

das Halteelement und den Stabfilter in Seitenansicht in Richtung des Pfeiles XI der Fig. 10;

Fig. 12

das Halteelement und den Stabfilter in Seitenansicht in Richtung des Pfeiles XII der Fig. 10;

Fig. 13

im Längsschnitt entlang der Linie XIII - XIII der Fig. 11 das Halteelement mit dem Stabfilter gemäss Fig. 10;

Fig. 14

im Längsschnitt entsprechend Fig. 6 eine Ausführungsform, bei welcher ein Anschlusszwischenstück einen Aussenkonus aufweist, welcher mit dem Innenkonus des Ventilträgers zusammenwirkt; und

Fig. 15

ebenfalls im Längsschnitt entsprechend Fig. 6 eine Ausführungsform mit einem Anschlusszwischenstück, welches jedoch kürzer ausgebildet ist.

The invention will be explained in more detail with reference to embodiments shown in the drawing. It shows purely schematically:

Fig. 1

a longitudinal section through a first embodiment of the inventive device for the intermittent injection of high-pressure fuel into the combustion chamber of an internal combustion engine, wherein an injection valve and a feed line associated therewith is shown; the device may, of course, comprise a plurality of injectors and each of these injectors having a feed line;

Fig. 2

across from Fig. 1 enlarges a part of the embodiment shown there;

Fig. 3

across from Fig. 2 enlarges a part of in the Fig. 1 and 2 shown device;

Fig. 4

in perspective view a holding element and a valve plate designed as a check valve member, which together with a valve carrier and optionally a filter form a cartridge-like, self-contained unit;

Fig. 5

a further embodiment of the inventive device, wherein the housing on the one hand has a valve housing with a lateral conical pressing surface and on the other hand, a pressure port on which the high-pressure inlet is formed;

Fig. 6

in longitudinal section a part of the pressure port and connected to this feed line;

Fig. 7

a further embodiment in which the housing of the injection valve or the pressure port is provided next to the high pressure inlet with a high pressure outlet;

Fig. 8

across from Fig. 7 enlarges a part of the embodiment shown there;

Fig. 9

in a perspective view of the cartridge-like, self-contained unit with the valve carrier, the support member and the filter carried by this, wherein in the valve carrier, the check valve is arranged;

Fig. 10

in view of the holding element and a rod filter, wherein these two parts are integrally formed with each other;

Fig. 11

the holding element and the rod filter in side view in the direction of arrow XI the Fig. 10 ;

Fig. 12

the holding element and the rod filter in side view in the direction of arrow XII the Fig. 10 ;

Fig. 13

in longitudinal section along the line XIII - XIII of Fig. 11 the holding element with the rod filter according to Fig. 10 ;

Fig. 14

in longitudinal section accordingly Fig. 6 an embodiment in which a connection intermediate piece an outer cone having, which cooperates with the inner cone of the valve carrier; and

Fig. 15

also in longitudinal section accordingly Fig. 6 an embodiment with a connection piece, which is shorter, however.

In all figures, the same reference numerals are used for corresponding parts.

The FIGS. 1 to 3 show a fuel injection valve 10 for the intermittent injection of fuel under high pressure into the combustion chamber 12 of an internal combustion engine 14 and connected to the fuel injection valve 10 feed line 16 of a first embodiment of the inventive device. Of course, this device may have a plurality of fuel injection valves 10 with feed lines 16 associated therewith.

On the other hand, the feed line 16 with a high-pressure conveyor, in particular a high-pressure pump, connected, as for example from WO 2007/009279 A is known. In this regard, reference is expressly made to the disclosure in this document.

The fuel injector 10 includes a housing 18 having a storage body 20 on which is integral, i. in one piece, a connection section 22 and storage section 24 are formed.

Further, the housing 18 has an intermediate body 26, which on the connecting portion 22, in the direction seen a longitudinal axis 28 of the fuel injection valve 10, the opposite side abuts the storage section 24.

Next, the housing 18 carries a nozzle body 30, which abuts against the storage body 20 side facing away from the intermediate body 26 and is secured by means of a union nut 32 on the housing 18. In the illustrated embodiment, the intermediate body 26 is disposed inside the union nut 32, and this is screwed to the storage body 22 such that the nozzle body 30 sealingly abut the intermediate body 26 and the latter on the storage body 20.

A high-pressure inlet 34 is formed in the connection portion 22 on the housing 18, and this is connected to a high-pressure chamber 36 of the fuel injection valve 10.

This high-pressure chamber 36 has a discrete storage chamber 38 in the storage body 20. The design and operation of such a storage chamber 38 is from the document WO 2007/009279 A known, the disclosure of which is incorporated by reference in this specification.

From the connection-side end face of the storage body 20 extends in this one to the longitudinal axis 28 rotationally symmetrical, in the direction of the longitudinal axis 28 long, blind hole, the discrete storage chamber 38 limiting recess 40, from the bottom of a longitudinal axis 28 obliquely extending duct section 42 to the intermediate body 26, for the supply of fuel to the nozzle body 30, runs.

The recess 40 is in the connection portion 22, seen in the direction of the longitudinal axis 28 against the free end of the storage body 20 out, widening, so that a conical sealing surface 44 (see Fig. 2 ) of the high pressure inlet 34 is formed. The opening angle α (see Figure 3 ) of this conical sealing surface 44 has approximately 60 ° in the exemplary embodiment shown. The conical sealing surface 44 forms an inner cone on the storage body 20 and thus on the housing 18th

Furthermore, the fuel injection valve 18 has a valve carrier 46 and a non-return valve 48 arranged therein. On the valve carrier 46, a holding element 50 is fixed, which in turn carries a filter 52 for the fuel, which is formed in the present case as a cup-shaped filter body 52 'with microholes 54. Preferably, at least 2,000 of such micro-holes 54 are present with a diameter of 20 to 50 microns. However, the filter 52 may also be formed as a rod filter 53, as in the Fig. 10 to 13 shown and described below.

In the illustrated embodiment, the valve carrier 46 is formed together with the check valve 48, holding member 50 and filter 52 as a cartridge-like, self-contained unit 56, similar to those in Fig. 9 is shown.

The assembly 56 is inserted as such in the discrete storage chamber 38 limiting recess 40 and thus in the high-pressure chamber 36.

The rotationally symmetrical to the longitudinal axis 28 formed valve carrier 46 has on its outer lateral surface 58 a conical outer sealing surface 60, which in the embodiment shown on a Input side, funnel-shaped end flange 62 of the valve carrier 46 is formed. The valve carrier 46 lies with its outer sealing surface 60, which forms an outer cone, on the sealing surface 44 sealingly, wherein the angle ß of the conical outer sealing surface 60 is formed smaller than the angle α, preferably this cone angle difference is 0.5 ° to 2 °. As a result, a particularly good tightness is achieved because the common contact surface of the cones with the smallest diameter form an annular sealing surface 64 ( Fig. 3 ).

Next, the valve carrier 46 on an input side end face 66 on a sealing surface forming inner cone 68, which is also formed in the illustrated embodiment, the end flange 62. The opening angle of this inner cone 68 is again about 60 °.

In the present exemplary embodiment, the feed power 16 is double-walled for monitoring any possible leakage of fuel, as is frequently required, in particular for marine applications. An inner tube 70 is designed to guide the under very high pressure fuel. It has in its two end regions depending on a sealing surface forming outer cone 72, which tapers towards the end of the inner tube 70.

With its outer cone 72 of the fuel injection valve 10 facing end portion of the inner tube 70 is sealingly against the inner cone 68 of the valve carrier 46.

In the same manner as explained in connection with the conical sealing surface 44 and outer sealing surface 60, the angle of the outer cone 72 of the Inner tube 70 formed smaller than the angle of the inner cone 68 of the valve carrier 46, preferably by a cone angle difference of 0.5 ° to 2 °, in turn to form a ring sealing surface at the smallest diameter of the contact surface of the cone.

The feed line 16 is fastened to the storage body 20 by means of a fastening element 74 'designed as a fastening element 74, and in particular so that the inner tube 70 is stretched in the direction against the fuel injection valve 10. As a result, the inner tube 70 bears with its outer cone 72 on the inner cone 68 of the valve carrier 46, and with its outer sealing surface 60 sealingly against the sealing surface 44 of the fuel injection valve 10. The valve carrier 46 and thus the assembly 56 is thus kept clamped directly between the housing 18 of the fuel injection valve 10 and the feed line 16.

The at least approximately rotationally symmetrical to the longitudinal axis 28 formed valve carrier 46 has a fuel passage 76, which leads from the outer cone 72 centric to the longitudinal axis 28 in a check valve chamber 78. This is bounded on the one hand by the valve carrier 46 and on the other hand by the holding element 50, which is threaded from the inner cone 68 facing away from the end face of the valve carrier 46 forth in this.

At the mouth of the fuel passage 76 into the check valve space 78, a flat, annular check valve seat 80 is formed on the valve carrier 46, which surrounds the mouth of the fuel passage 76. Further In the embodiment shown, the valve carrier 46 has a circumferential undercut 82 which surrounds the check valve seat 80.

Next, the check valve 48 has a check valve member 84 (see Fig. 4 ), which is arranged in the check valve chamber 78 and in the embodiment shown as a valve plate 84 'is formed. When the check valve 48 is closed, the check valve member 84 or the valve plate 84 'is sealingly against the check valve seat 80.

The check valve member 84 is provided with a throttle passage 86, which is formed in the embodiment shown as a central through hole through the valve plate 84 '. By means of this restrictor passage 86, the high-pressure chamber 36 or the discrete storage chamber 38 is also flow-connected to the high-pressure inlet 34 (throttled) even when the check valve 48 is closed.

On the side facing away from the fuel passage 76 of the check valve member 84 is supported on this a compression spring 88 from one end, which is supported at its other end on the support member 50. The compression spring 88 acts as a closing spring for the check valve 48 and ensures that the check valve member 84 rests against the check valve seat 80 when the compensation pressure.

The holding element 50 has centric to the longitudinal axis 28 to a further fuel passage 90, which leads from the check valve chamber 78 to the free end of the retaining element 50. The cross section of this further Fuel passage 90 is equal to or greater than the cross section of the fuel passage 76.

In the end region facing the check valve chamber 78, the further fuel passage 90 has a step-like widening, into which the pressure spring 88 engages, and at whose step the compression spring 88 is supported on this side.

Further, the check valve-side end of the holding member 50 is spaced from the check valve seat 80 so that the holding member 50 for the valve plate 84 'in the open position forms a stop and while the non-return valve seat 80 and valve plate 84' limited flow cross section is at least as large, preferably larger than the cross section of the fuel passage 76.

In order to ensure a low-loss as possible flow of the fuel from the high-pressure inlet 74 into the high pressure chamber 36 in space-saving design, the valve plate 84 'in the illustrated embodiment 3 - see also Fig. 4 - Distributed uniformly in the circumferential direction and in the direction of radially outwardly open, in the direction of the longitudinal axis 28 through openings 92. Between the openings 92 of the radially outer edge of the valve plate 84 'to the longitudinal axis 28 is circular. It is thus a sufficiently large passage between the valve plate 84 'and the wall of the holding member 50, regardless of the rotational position and the lateral position of the valve plate 84' created.

How this continues to be particularly good FIG. 4 can be removed, has the holding element 50 in a subsequent to the thread 94, the check valve chamber 78 facing End region to a reduced outer diameter, to form between it and the wall of the support member 50 has a sufficiently large annular fluid space. Next, the holding element 50 in this area three, distributed in the circumferential direction, in the radial direction continuous and in the direction of the valve plate 84 'open grooves 96. These ensure, regardless of the rotational position and lateral position of the valve plate 84 ', a sufficiently large flow cross-section of the check valve chamber 78 in the other fuel passage 90 sure.

Only for the sake of completeness it should be mentioned that the holding element 50 is formed between the thread 94, with which it is threaded into a corresponding internal thread of the valve carrier 46, and a free end portion as a polygonal, in particular hexagon, by means of a tool, the holding member 50 on the valve carrier 46 to be able to tighten. A step 98 between the thread 94 and the polygon serves as a stop on the valve carrier 46 and determines the mutual axial position in the mounted state.

On the cylindrical free end portion of the holding member 50, the filter 52 is placed. This has a cup-shaped filter body 52 'with the microholes 54 on. Preferably, the filter body 52 'is welded to the holding element 50.

The valve carrier 46 then has radially outward to the end flange 62 to the holding element 50 facing the end of a circular cylindrical shape, with approximately in the middle of a step. The outer diameter in the section adjacent to the end flange 62 up to the step is smaller than in FIG. seen in the direction of the interior of the fuel injection valve 10, the stage following section, a guide portion 100. Between this and the housing 18 and the storage body 20, a narrow gap 102 is present. The guide portion 100 facilitates during assembly the insertion of the assembly 56 in the high pressure chamber 36 and the recess 40 and the storage chamber 38 and aligns the unit. The guide section 100 could also be dispensed with here.

For the sake of completeness, it should be mentioned that in the housing 18 eingindete screws 104 hold with its head the assembly 56 on the housing 18 in place when the feed line 16 is not connected to the fuel injection valve 10.

Like this one FIG. 1 can be removed, the fuel injection valve 10 is held by means of a claw 106 in a known manner to the cylinder head of the internal combustion engine 14.

Further, the housing 18, in the illustrated embodiment, the storage body 20, an electrical connection 108 is arranged, from which by the storage chamber 38 bounding wall parallel to the longitudinal axis 28, a channel 110 extends to the intermediate body 26 facing end side. From the electrical connection 108, a control line 112 is guided through the channel 110, which carries connection contacts 114 at the other end.

For the sake of completeness, it should be mentioned that the storage body 20 on this side has an opening, which is open toward the intermediate body 26, in the form of a center hole-like recess, in which a compression spring 116 is arranged. This serves the holding of an electrically controlled, connected to the terminal contacts 114 actuator assembly 118 which is received in a corresponding recess in the intermediate body 26.

Such actuator assemblies 118 are well known, and in the present case, they are configured as in FIG FIG. 5 of the document WO 2008/046238 A shown and described in detail. With regard to structure and operation, reference is expressly made to this document. However, differently configured actuator arrangements can be used.

In addition to the recess for the Aktuatoranodnung 118 parallel to the longitudinal axis 28 through the intermediate body 26 passes through a further duct section 42 ', which is fluidly connected to the duct section 42 and on the other hand opens into the limited part of the nozzle body 30 of the high-pressure chamber 36.

In this a needle-like trained injection valve member 120 is slidably disposed in the direction of the longitudinal axis 28, which cooperates with an integrally formed on the nozzle body 30 in a known manner injection valve seat 122. In the idle state, the injection valve member 120 abuts against the injection valve seat 122 and thus prevents the escape of fuel from the high pressure chamber 36 into the combustion chamber 12. For injection, the injection valve member 120 is briefly lifted from the injection valve seat 122, whereby fuel through the nozzle body 30 in a known manner and Way trained injectors is injected into the combustion chamber 12.

In its end region facing away from the injection valve seat 122, the injection valve member 120 forms a piston 124, which is guided in a guide sleeve 126 in close sliding fit. On the guide sleeve 126 is formed as a compression spring closing spring 128, which at the other end is supported on the injection valve member 120 and this is acted upon by a directed toward the injection valve seat 122 spring force.

On the other hand, by means of the closing spring 128, the guide sleeve 126 is pressed sealingly against an intermediate plate. The piston 124, the guide sleeve 126 and the intermediate plate define a control chamber 130th

To control the movement of the injection valve member 120 in the axial direction, the pressure in the control chamber is changed by means of a hydraulic control device 132. For this purpose, the control device 132 has an intermediate valve 134 with an intermediate valve member, which in the open position releases a high-pressure passage formed on the intermediate plate which leads from the high-pressure chamber 36 into the control chamber 130 and closes in the closed position in order to separate the control chamber 130 from the high-pressure chamber 36.

Furthermore, the intermediate valve member permanently separates the control chamber 130 from a valve chamber 136, with the exception of a throttle passage, via which the control chamber 130 is permanently connected to the valve chamber 136 via a small flow cross section.

The actuator assembly 118 has an electromagnet 138 connected to the control line 112, which actuates a control shaft 140. At rest closes the control shaft 140 a low-pressure outlet from the valve chamber 136. In the activated state of the solenoid 138, that is, for an injection, the control shaft 140 releases the low-pressure outlet; the fuel leaving the valve space 136 through this fuel is passed through a low pressure return line in a known manner to a low pressure fuel tank.

The detailed structure and operation of fuel injection valves 10 according to Fig. 1 is for example in the publications WO 2007/098621 A and WO 2008/046238 A described in detail. The other and further known embodiments disclosed in these documents can also be used in the present fuel injection valve 10.

The structure and operation of the double-walled feed line 16 corresponds to the prior art and is for example in the earlier international patent application WO 2013/117311 A shown and described in detail.

To monitor any leakage of fuel, the feed line 16 is double-walled. The inner tube 70 is intended to guide the under very high pressure fuel. It runs within a (thin-walled) outer tube 142, wherein between this and the inner tube 70, a leakage return gap 144 is present; see in particular Fig. 2 ,

The feed line 16 has at its two ends depending on a connecting nut 74 and 75, wherein the fuel injection valve side, the fastening element 74 forming the connecting nut 74 'has an internal thread for Screwing onto a corresponding external thread on the housing 18 or storage body 20 and the other connection nut 75 has an external thread for insertion into, for example, a distributor element or a distributor block, as is known from the document WO 2007/009279 A is known; one could therefore also speak of a connection screw 75.

Further, the fuel injection valve 10 associated with the connecting nut 74 'has a radially inwardly open circumferential groove into which an O-ring 146 is inserted, which cooperates in the mounted state with a corresponding sealing surface on the housing 18 and the storage body 20 to the leakage to avoid fuel through the thread. Accordingly, the other connection nut 75 has an outwardly open circumferential groove with an O-ring 146 'inserted therein.

Through the connecting nut 74 'passes through a nut passage 148, through which the inner tube 70, to form a gap extends. In its two-sided axial end portions of the mother passage 148 is formed larger in diameter. In the fuel injector 10 facing away from the end portion of the nut passage 148 engages the outer tube 142, wherein between the connecting nut 74 'and the outer tube 142 acting further O-ring 146 "prevents leakage of fuel from the mother passage 148 to the environment; Fig. 2 ,

An end region of the inner tube 70 which adjoins the outer cone 72 is provided with an end region of the mother passage 148 facing the fuel injection valve 10 Attachment sleeve 150 threaded with its center section. In its end region facing away from the free end of the feed line 16, the fastening sleeve 150 has four cross-shaped, groove-shaped leakage recesses 152 running through in the radial direction. Here, the fastening sleeve 150 is provided on the outside with a conical taper, which cooperates with a corresponding conical surface on the connecting nut 74 '.

In the assembled state, the outer cone 72 of the inner tube 70 on the inner cone 68 of the valve carrier 46 and the outer sealing surface 60 on the conical sealing surface 44 of the housing 18 or its storage body 20 are held in tight contact by means of the connecting nut 74 'on the mounting sleeve 150. Should one or both of these gaskets leak, the leakage fuel will flow through the mother passage 148 into the leakage return gap 144, and from there in a known manner back to a leakage monitoring sensor, preferably in the low pressure fuel tank.

Another embodiment of the inventive device is in the Figures 5 and 6 shown, wherein the housing 18 of the fuel injection valve 10, a valve housing 154 and a nozzle housing 156 of a pressure port 158 has. A fuel injector 10 with such a valve housing 154 and a discharge nozzle 158 is from the document WO 2009/033304 A known. The structure and operation of the fuel injection valve 10 are disclosed in detail in that document, and the disclosure of which is incorporated by reference into the present specification.

Compared with in the FIGS. 1 to 3 shown and described above embodiment, the nozzle housing 156 is formed by the storage body 20 with the discrete storage chamber 38, but without the electrical connection 108, channel 110, control line 112, connection contacts 114 and recess for a compression spring 116 in the present case.

Accordingly, the valve housing 154 in the embodiment according to the Figures 5 and 6 instead of the storage body 20 on a connection body 160, at whose the nozzle body 30 facing end face (as in FIG. 1 shown) abuts the intermediate body 26 with the actuator assembly 118 received therein. This is arranged in the interior of the union nut 32, which on the one hand is supported on the nozzle body 30 and on the other hand is threaded onto the connection body 160, analogously as in FIG. 1 shown and described above.

Furthermore, the electrical connection 108 is attached to the connection body 160. Incidentally, the interior of the in Fig. 5 shown valve housing 154 analog Fig. 1 be educated.

Next, a lateral, designed as a sealing surface, conical pressing surface 162 is integrally formed on the connecting body 160. The high-pressure hydraulic connection from the feed line 16 to the valve housing 154 is realized via the pressure port 158.

The longitudinal axis 158 'of the pressure port 158 extends at right angles to the longitudinal axis 28 of the valve housing 154. The longitudinal axis 158' also forms the axis of rotation for the pressure surface 162.

The nozzle housing 156 is formed at its end region facing the valve housing 154 as a conical abutment surface 164, which also acts as a sealing surface and bears sealingly against the pressure surface 162.

In the interior of the nozzle housing 156, the recess 40 is formed with the discrete storage chamber 38 or at least a portion of the discrete storage chamber 38, from which or from which to the free end a duct section extends and is connected there to the high-pressure chamber inside the valve housing 154. Analogous to the execution according to Fig. 1 may be present in the valve housing 154, a second part of the discrete storage chamber 38.

For the sake of completeness, it should be mentioned that a mounting flange 166 protrudes from the nozzle housing 156, which has two through-holes 168. These are intended to be penetrated by clamping screws, which are supported with their head on the mounting flange 166 and are threaded into the cylinder head to hold the discharge nozzle 158 in close contact with the valve housing 154.

According to Fig. 6 and analogously to the embodiment according to the FIGS. 1 to 3 , see in particular FIG. 3 , has in the direction of the longitudinal axis 158 'extending recess 40 of the nozzle housing 156, which also forms at least a portion of the discrete storage chamber 38, the connection side in the connection section 22, the conical sealing surface 44. Accordingly, in the recess 40, the independent assembly 56 is used, which is exactly the same design and sealing, as described above and in the Fig. 1 to 3 shown. The valve carrier 46 is located with its outer sealing surface 60 on the conical sealing surface 44 at. In the assembled state also engages the inner tube 70 of the feed line 16 with its outer cone 72 in the inner cone 68 of the valve carrier 46 and is located on this sealingly.

In order to hold the valve carrier 46 and thus the assembly 56 even when the supply line 16 is not connected to the nozzle housing 156, the screws 104 are threaded into this, which pull a retaining ring 170 against the nozzle housing 156 and which is supported on the end face of the valve carrier 46. This solution can be used in all embodiments.

In the connection region of the feed line 16 to the nozzle housing 156 is the difference from the embodiment according to the FIGS. 1 to 3 only in that at the nozzle housing 156 in a connection recess, an internal thread is formed, in which, instead of the connection nut 74 ', a, otherwise the same as the connection nut 74' formed, the fastening element 74 forming connection screw 74 "is threaded with its external thread Words, the terminal portion of the feed line 16 is formed as the terminal portion in the fuel injection valve 10 remote from the end of the feed line 16 according to the embodiment according to the FIGS. 1 to 3 ,

The FIGS. 7 and 8th show the connecting portion 22 of the housing 18, or the storage body 20 or the nozzle housing 156 of a further embodiment of the inventive device, wherein the fuel injection valve 10 - with the exception in the connection portion 22 - may be formed as in the FIGS. 1 to 3 respectively 5 and 6 are shown and described accordingly.

Centric to the longitudinal axis 28 - or 158 '- the high pressure inlet 34 is formed on the housing 18, exactly the same as in the FIG. 6 shown and described above. In the present embodiment, however, the valve carrier 46 in the recess 40, with not connected feed line 16, by means of the head of a screw 104 - held without retaining ring 170.

Parallel to the high pressure inlet 34 and with respect to this laterally offset on the housing 18, or the accumulator body 20 or nozzle housing 156, a high pressure outlet 172 is formed. Accordingly, the housing 18 is formed head-like in the connection portion 22 and it has a lateral extension.

The geometry of the high pressure outlet 172 is analogous to that of the high pressure inlet 34. From the bottom of the high pressure outlet 172 is a conical, tapered sealing surface 174 of which has the same geometry as the inner cone 68 on the valve carrier 46. It cooperates with an outer cone 72 at one , same as the feed line 16 formed connecting line 176. This serves to feed a further fuel injection valve 10 and is only indicated schematically.

From the sealing surface 174 extends in the housing 18, a hydraulic connection 177 to the recess 40. The junction is in the recess 40, seen in the direction of the longitudinal axis 28 and 158 ', the valve carrier 46, at its reduced outside diameter, that is, between the end flange 62nd or the outer sealing surface 60 and the guide portion 100; see also Figure 3 ,

In the exemplary embodiment shown, the connection 177 consists of a radial bore 178 opening into the recess 40 and a longitudinal bore 178 'extending from the latter and extending to the connection axis 172' of the high-pressure outlet 172, starting from the end of the conical sealing surface 174. The transverse bore 178 has a larger cross-section in an end region adjoining the lateral outer surface of the housing 18 and, in this region, has a step-like tapering inwards. In the inner end of this end region, a sealing ball 180 is arranged, which is held by means of an indented and sealed in the end region Andrückstopfens 182 such that the radial bore 178 seals high pressure moderately. For this purpose, the radial bore 178 may have, subsequent to the end region, a conically tapered sealing surface against which the sealing ball 180 is pressed.

From an annular space extending around the sealing ball 180 on the side facing the Andrückstopfen 182 runs parallel to the connection axis 172 ', a Leckagelängsbohrung 184 to the bottom of the high pressure outlet 172, where they, viewed in the radial direction, outside the sealing surface 174 in the recess in the housing 18 for the high pressure outlet 172 opens and forms there a leakage monitoring opening.

Further extending from the bottom of the high pressure inlet 34 and the high pressure outlet 172 forming recesses in the housing 18 from the facing sides leakage bevels 186, which open into one another. Of the For completeness, it should be mentioned that the openings of the Leckageeschrägbohrungen 186 lie in the radial direction outside the sealing surface 174 and the conical sealing surface 44 and also form leakage monitoring openings.

Of course, leakage bores, such as the leakage longitudinal bore 184 and Leckescheschägbohrungen 186, not necessary if a leakage monitoring is omitted. In this case, the feed line 16 and connecting line 176 must not be double-walled; it then has no outer tube 142.

Should any seal or inner tube 70 leak, the leakage fuel is directed through the leakage return gap 144 to a leakage monitor. In this regard, the disclosure in the international patent application WO 2013/117311 A directed.

Unlike the ones in the FIGS. 1 to 6 In the present embodiment, the illustrated embodiments of the valve carrier 46, in the direction of the longitudinal axis 28 between on the one hand the end flange 62 and the outer sealing surface 60 and inner cone 68 and on the other hand the guide portion 100 (FIG. Fig. 8 ) is at least one radial outlet 190, in the embodiment shown four cross-like extending radial outlets 190. This is or these are thus also disposed between the inner cone 68 and the check valve 48 and a preferably throttle-free connection between the fuel passage 76 and thus the feed line 16 and the high pressure outlet 172 and the connecting line 176 is possible.

In this embodiment, preferably in the flow direction in the fuel valve 10 in the downstream of the radial outlet 190 existing guide portion 100 of the valve carrier 46 is formed longer than in the embodiments shown above, and the gap 102 has a smaller width. By these measures, both a trouble-free mounting of the valve carrier 46 and the assembly 56 and a hydraulic separation between the discrete storage chamber 38 and the connecting line 176 in a simple manner, at least for transient processes, allows.

Incidentally, the unit 56 is formed exactly the same as in the other embodiments of the fuel injection valve 10th

The FIG. 9 shows the assembly 56 of the embodiment according to the FIGS. 7 and 8th in perspective view. As described above, this consists of the valve carrier 46, the non-return valve 48 present in it, the holding element 50 which is inserted in the valve carrier 46 and the filter 52 carried by the holding element 50.

In the region of the guide section 100, two opposite chamfers 192 are integrally formed on the valve carrier 46, which serve to attack a fork wrench in order to be able to tighten the holding element 50.

The assembly 56 in the embodiments according to the FIGS. 1 to 6 is exactly the same, but with the valve carrier 46 has no radial outlet 190 and the length of the guide portion 100 may be less.

This preassembled, self-contained unit 56 can be easily inserted into the recess 40 until it rests with the outer sealing surface 60 of the valve carrier 46 on the conical sealing surface 44 of the housing 18.

Instead of the filter body 52 'with the microholes 54 may be provided as a filter 52 of the rod filter 53 - also in the other embodiments. In the in the FIGS. 10 to 13 In the embodiment shown, the rod filter 53 and the holding element 50 are integrally formed, ie integrally, with one another. As a result, the rod filter 53 is also part of the assembly 56 and can accordingly be inserted into the recess 40 from the high-pressure inlet 34 together with the valve carrier 36 and the check valve 48. However, it should also be mentioned the possibility to form the rod filter 53 as an independent component and to hold by means of a press fit in the recess 40, as in the document EP 2 188 516 described and there in FIG. 7 is shown (see reference numerals 72 and 72 '). In this case, the assembly 56 comprises the valve carrier 46, the check valve 48 and the holding member 50 with a further fuel passage 90th

In the in the FIGS. 10 to 13 In the embodiment shown, the holding element 50 with its further fuel passage 90, the thread 94, the open grooves 96 and the step 98 with the polygon is the same, as in connection with FIGS FIGS. 1 to 3 and particularly FIGS. 4 to 7 shown and described. At the end described there closes now integrally Bar filter 53, which closes the further fuel passage 90 in the axial direction blind hole. For this run from the other fuel passage 90, inclined in the flow direction of the fuel, here three radial passages 194 in the annular space between the support member 50 and the housing 18 and the storage body 20 or nozzle housing 156th

It should be noted that in FIG. 13 the indicated there housing 18 or the accumulator body 20 or the nozzle housing 156 - for greater clarity - at a greater distance from the rod filter 53 is shown as this is effectively the case.

The rod filter 53 is cylindrical and has at its circumference, distributed in the circumferential direction, longitudinal grooves 196, 196 'which alternately open to the high-pressure chamber 36 and the radial passages 194 out, on the other hand, however, are almost closed and each other, measured in the axial direction over overlap a substantial part of the length of the rod filter 53. In the region of this overlap, the outer diameter of the rod filter 53 is formed slightly smaller than in the two axial end portions 198 and 198 ', which close the longitudinal grooves 196 and 196' almost. The reduced diameter in the overlap region, together with the housing 18 or accumulator body 20 or stub housing 156, defines filter gaps 200 which allow the fuel to flow from the longitudinal grooves 196 'into the longitudinal grooves 196, but retain solid particles.

In the two end regions 198 and 198 ', the distance A between the rod filter 53 and the housing 18 or accumulator body 20 or stub housing 156 - Outside the range of each there open longitudinal grooves 196, 196'- about 5 to 10 microns. The width of the filter gaps 200 between the rod filter 53 and the housing 18 or storage body 20 or nozzle housing 156 is preferably about 30 to 40 micrometers, in particular about 35 micrometers.

It is also possible, the feed line 16 and the inner tube 70 with respect to the in the FIGS. 1 to 3 and 6 to 8 shown embodiments of smaller outer diameter and, if required by the pressure conditions (which is practically always the case), even smaller inner diameter form; see also Fig. 15 , 16 and 17. Preferably, in this case, the volume of the discrete storage chamber 38 is formed correspondingly large or larger.

Also in this case, the feed line 16 and the inner tube 70 is pressed with its outer cone 72 by means of the fastener 74 sealingly against the inner cone 68 of the valve carrier 46 and its end flange 62. Thus, the valve carrier 46 and its end flange 62 is pressed with the conical outer sealing surface 60 on the conical sealing surface 44 of the housing 18.

However, since it is possible in this case that the feed line 16 and the inner tube 70 is too weak to the valve carrier 46 against the pressure in the storage chamber 38 reliably sealingly press on the housing 18, for example, in FIG. 6 shown holding ring 170 correspondingly more stable and correspondingly more stable attached to the housing 18, so that even with pressure surges between the Outer sealing surface 60 and the conical sealing surface 44 tightness is guaranteed.

The Fig. 14 and 15 show two embodiments in which the valve carrier 46 is pressed by means of a connecting piece 202 with its conical outer sealing surface 60 to the conical sealing surface 44 of the high pressure inlet 34 sealingly. These embodiments are preferably used when the (not double-walled) feed line 16 and the inner tube 70 of the double-walled feed line 16 are formed with relatively small diameters; compare in this regard the supply line 16 in the Fig. 1 to 3 and 6 to 8 with larger diameters. There, the outer diameter of the feed line 16 and the inner tube 70 is greater than the diameter of the recess 40 (outside the conical connecting portion) in the cylindrical region. Here, however, the outer diameter of the feed line 16 and the inner tube 70 is smaller than the diameter of the recess 40 in the cylindrical region.

The fuel injection valve 10, in particular the assembly 56 with the valve carrier 46 is the same design as shown in the other figures and described above.

The recess 40 in the housing 18 or accumulator body 20 or nozzle housing 156 has in the connection section 22, the conical sealing surface 44, against which the valve carrier 46 sealingly abuts with its conical outer sealing surface 60; as described above.

Subsequent to the sealing surface 44, the housing or the accumulator body 20 or the stub housing 156 in the connection section 22 towards the free end on an internal thread into which the connection piece 202 is screwed with a corresponding external thread; at Fig. 14 analogous to the terminal screw 74 "in the embodiments in the Fig. 7 to 8 ,

In its the fuel injection valve 10 and thus the valve carrier 46 facing end portion of the outer adapter 72 is integrally formed on the connecting piece 202, which cooperates sealingly with the inner cone 68 of the valve carrier 46, as above, in particular in connection with the Fig. 1 to 3 and 6 to 8 , is disclosed. There, the corresponding outer cone 72 is formed on the feed line 16 and on the inner tube 70.

At its end facing away from the outer cone 72, an inner cone sealing surface 204 is integrally formed on the integrally formed connection piece 202, against which the inner tube 70 of the feed line 16 sealingly abuts with its outer cone 72.

Centrally to the longitudinal axis 28 and 158 'extends through the connecting piece 202 through a feed hole 208 to the fuel from the feed line 16 to the fuel injector 10, that is, the assembly 56, supply.

In the embodiment according to Fig. 14 the connection adapter 202 projects beyond the housing 18 or the accumulator body 20 or the stub housing 156. Same as in the Fig. 1 to 3 shown and described accordingly, the connecting nut 74 ', which presses the inner tube 70 sealingly against the inner cone sealing surface 204 via the fastening sleeve 150, is screwed onto a corresponding external thread of the connecting intermediate piece 202.

Between the housing 18 or accumulator body 20 or nozzle housing 156 and the connecting nut 74 ', an external bead 206 is integrally formed on the connecting intermediate piece 202 which, in the radial direction, protrudes beyond the connecting nut 76 and the downstream end region of the housing 18 and at which engaging surfaces for a tool, For example, a hexagon for the attack of a fork wrench are formed.

In this way, the connection adapter 202 can be sufficiently strongly threaded into the housing 18 or the accumulator body 20 or the stub housing 156 in a simple manner.

If the feed line 16 - for the return of leakage fuel - double-walled with a inner ear 70 and an outer tube 142, the connecting adapter 202 two in corresponding radially outwardly open circumferential grooves inserted O-rings 146 are provided which between the terminal adapter 202 and on the one hand the housing 18 or the storage body 20 or nozzle housing 156 and on the other hand, the connecting nut 74 'seal. In this case, a leakage bore 210 is formed on the connection intermediate piece 202, which has the leakage return gap 144, via the parent passage 148, with a housing 18 or storage body 20 or support housing 156, the valve carrier. 46 and the connecting piece 202 limited, gap-shaped leakage chamber 212 connects.

Any fuel escaping from the high-pressure space 36 on this side is thereby returned to the feed line 16 and through its leakage return gap 144, as described above.

In the embodiment according to Fig. 15 the terminal adapter 202 is shorter in the axial direction than in the embodiment according to FIG Fig. 14 and arranged in the interior of the housing 18 or storage body 20 or nozzle housing 156 in its connection portion 22.

Between the inner cone sealing surface 204 and the external thread of the connecting intermediate piece 202 whose end face is flat. Run from this end face, distributed in the circumferential direction and in the radial direction approximately centrally between the Innenkonusdichtfläche 204 and the external thread, three blind holes 214 parallel to the longitudinal axis 28 and 158 '. These serve the attack with a corresponding socket wrench, the pins can engage in the blind holes 214 to pull the connection piece 202 so tight that the outer cone 72 of the connection piece 202 sealingly against the inner cone 68 of the valve carrier 46 and this with its outer sealing surface 60 sealingly against the conical sealing surface 44 is present.

The fastener 74 is the same as in the embodiments according to the FIGS. 6 to 8 formed as a fastening screw 74 ", which via the mounting sleeve 150, the inner tube 70 of the feed line 16 with its outer cone 72 sealingly against the Inner cone sealing surface 204 of the terminal adapter 202 presses.

In the embodiments according to the Figures 14 and 15 the valve carrier 46 is provided with the radial outlets 190, as in connection with the FIGS. 7 and 8th is shown and explained to supply via a connecting line 176, another fuel injection valve 10 with fuel. However, if no other fuel injector 10 is to be supplied in this manner, the valve carrier 46 may be formed without the radial outlets 190 as shown in FIGS FIGS. 1 to 3 . 6 and 13 is shown.

For feeding a further fuel injection valve 10, the connection portion 22 of the housing 18 or storage body 20 or nozzle housing 156 may be formed the same as in Fig. 7 shown and described above, namely with a high pressure outlet 178th

The Figures 14 and 15 show an alternative solution for feeding a further fuel injection valve 10, this solution can also be used in the other embodiments.

Seen in the direction of the longitudinal axis 28 or 156 'at least approximately at the height of the radial passages 190 of the valve carrier 46, extends from the recess 40 through the wall of the housing 18 and the storage body 20 or nozzle housing 156, a hydraulic connection 177 forming radial bore 178. Your in Radial direction outer end portion is formed as a conical sealing surface 174, on which the Inner tube 70 of the connecting line 176 sealingly abuts with its outer cone 72.

The housing 18 or the storage body 20 or nozzle housing 156 is encompassed by a clamp 216, which is arranged such that its radial passage 218 is aligned with the radial bore 178.

The clamp 216 is provided in the region of the radial passage 218 with an internal thread into which the fastening element 74 designed as a connection screw 74 "is screwed in order to press the inner tube 70 sealingly against the housing 18 or the accumulator body 20 or stub housing 156.

In order to fix the clamp 216 additionally on the housing 18 or on the accumulator body 20 or stub housing 156, it may have, preferably on the side opposite the radial passage 218 side, a threaded hole into which a preferably sealing screw 220 is inserted, which with its blunt point engages at the free end of the shaft in a corresponding recess on the housing 18 or storage body 20 or nozzle housing 156.

In the case of the feed line 16 and the connecting line 176 are formed double-walled for returning any leakage fuel, seal O-rings 146 above and below the radial bore 178 and the radial passage 218 between the housing 18 or accumulator body 20 or nozzle housing 156 and the clamp 216 to the Avoid leakage of leakage fuel.

Next is in this case also in the embodiment according to Fig. 15 the connection adapter 202 with a leakage bore 210 and the housing 18 or the storage body 20 or the nozzle housing 156 provided with leakage passages, as already in Fig. 14 2, to establish a leakage connection between the connection line 176 via the leakage space 212 with the leakage return gap 144 of the feed line 16.

For completeness, it should be mentioned that in the embodiment according to Fig. 15 the connection piece 202 and the fastening element 74 of the feed line 16 designed as a terminal screw 74 "are threaded into the same thread in the connection section 22 of the housing 18 or storage body 20 or socket housing 156.

Claims (18)

1. Device for intermittently injecting high-pressure fuel into the combustion chamber of an internal combustion engine, having a fuel injection valve (10), which has a housing (18) that has a high-pressure inlet (34) with a conical sealing surface (44), a recess (40) and a high-pressure space (36), having a check valve (48), which allows flow of the fuel from the high-pressure inlet (34) through the fuel passage (76) into the high-pressure space (36) with as little hindrance as possible and at least restricts said flow in the opposite direction, having a feed line (16) for feeding fuel to the fuel injection valve (10), and having a fastening element (74), which loads the feed line (16) in a direction toward the high-pressure inlet (34), characterized by a valve carrier (46) which has a fuel passage (76), having a conical outer sealing surface (60) on an outer circumferential surface (58), which outer sealing surface rests sealingly on the conical sealing surface (44) of the high-pressure inlet (34), and the fastening element (74) presses the feed line (16) against the valve carrier (46), and presses the latter against the high-pressure inlet (34).
2. Device as claimed in claim 1, characterized in that the valve carrier (46) has an inner cone (68) at a front end (66) on the inlet side, which inner cone forms a sealing surface and is adjoined by the fuel passage (76), and the feed line (16) has an outer cone (72) in its end region facing the fuel injection valve (10), said outer cone forming a sealing surface which rests sealingly on the inner cone (68) of the valve carrier (46).
3. Device as claimed in claim 2, characterized in that the conical outer sealing surface (60) and the inner cone (68) are formed on a funnel-shaped end flange (62) of the valve carrier (46).
4. Device as claimed in claim 2 or 3, characterized in that there is a cone angle difference (α, β) of 0.5° to 2° between the conical sealing surface (44) of the high-pressure inlet (34) and the conical outer sealing surface (60) of the valve carrier (46), on the one hand, and between the inner cone (68) of the valve carrier (46) and the outer cone (72) of the feed line (16), on the other hand, with the result that an annular sealing surface (64) is formed in each case at the smallest diameter of the contact surface between the respective cones (44, 60; 68, 72).
5. Device as claimed in one of claims 1 to 3, characterized in that the conical sealing surface (44) of the high-pressure inlet (34) is formed on the housing (18).
6. Device as claimed in one of claims 1 to 5, characterized in that the valve carrier (46) is formed as a self-contained, cartridge-type modular unit (56) together with the check valve (48) and a holding element (50) fastened on the valve carrier (46) and is inserted as such into the recess (40) of the housing (18).
7. Device as claimed in claim 6, characterized in that the modular unit (56) is inserted into the recess (40) from the direction of the high-pressure inlet (34).
8. Device as claimed in claim 6 or 7, characterized in that the holding element (50) has a further fuel passage (90).
9. Device as claimed in one of claims 6 to 8, characterized in that the modular unit (56) has a filter (52) for the fuel, in particular a cup-shaped filter body (52') with microholes (54) or a rod-type filter (52"), which is carried by the holding element (50) and to which the fuel flows, if appropriate through the further fuel passage (90).
10. Device as claimed in one of claims 6 to 9, characterized in that the recess (40) forms at least part of the high-pressure space (36), and the modular unit (56) is inserted into the high-pressure space (36).
11. Device as claimed in one of claims 6 to 10, characterized in that an annular check valve seat (80) of the check valve (48) is formed on the valve carrier (46), and a check valve member (84) interacting with the check valve seat (48), preferably designed as a valve plate (84') and provided with a restrictor passage (86), is arranged between the valve carrier (46) and the holding element (50).
12. Device as claimed in claim 11, characterized in that the check valve member (84) designed as a valve plate (84') has at least one aperture (92) open in a direction radially toward the outside and passing through in the direction of the longitudinal axis (28) - preferably three such apertures (92) distributed in the circumferential direction - and the holding element (50) has, in its end region facing the valve plate (84'), at least one groove (96) open in a direction toward the valve plate (84') and passing through in a radial direction - preferably three such grooves (96) distributed in the circumferential direction - in order to allow flow of the fuel with as little hindrance as possible when the check valve (48) is open.
13. Device as claimed in one of claims 1 to 12, characterized in that the high-pressure space (36) has a discrete storage chamber (38) for storing fuel, and the modular unit (56) preferably projects into this storage chamber (38).
14. Device as claimed in one of claims 1 to 13, characterized in that the housing (18) of the fuel injection valve (10) carries a nozzle body (30) having an injection valve seat (122), which is connected to the high-pressure space (36) and with which an injection valve member (120) arranged in such a way as to be adjustable in the direction of the longitudinal axis (28) interacts, wherein a closing spring (128) is supported on the injection valve member (120) and subjects the latter to a closing force directed in a direction toward the injection valve seat (122), and there is in the housing (18) a hydraulic control device (132) controlled by means of an electrically controlled actuator (118) for the purpose of raising the injection valve member (120) from the injection valve seat (122) against the closing force of the closing spring (128) in order to inject fuel.
15. Device as claimed in claim 14, characterized in that the housing (18) has, on the one hand, a valve housing (154), which carries the nozzle body (30) and in which the injection valve member (120), the closing spring (128), the actuator (118) and the control device (132) are arranged and on which a conical contact pressure surface (162) acting as a sealing surface is formed, and, on the other hand, has a pressure connection piece (158), on the connection piece housing (156) of which the high-pressure inlet (34) is formed and the longitudinal axis (158') of which extends transversely, preferably at right angles, to the longitudinal axis (28) of the valve housing (154), wherein the connection piece housing (156) has, in an end region facing away from the high-pressure inlet (34), a conical mating contact pressure surface (164), which rests sealingly on the contact pressure surface (162), and, if appropriate, the modular unit (56) is inserted into the connection piece housing (156) and, if appropriate, the discrete storage chamber (20) is formed at least partially in the connection piece housing (156).
16. Device as claimed in one of claims 1 to 15, characterized in that the housing (18) or the connection piece housing (156) has a high-pressure outlet (172), which is arranged next to the high-pressure inlet (34) and is fluidically connected, preferably without restriction, to the high-pressure inlet (34) in order to supply a further injection valve (10) with fuel via a high-pressure connecting line (176) connected to the high-pressure outlet (172).
17. Device as claimed in claim 2 and 16, characterized in that the valve carrier (46) has, between the inner cone (68) and the check valve (48), a radial outlet (190), which starts from the fuel passage (76) and which is fluidically connected to the high-pressure outlet (172) via a connecting line (176) in the housing (18) or the connection piece housing (156).
18. Device as claimed in claim 17, characterized in that the valve carrier (46) together with the housing (18) or the connection piece housing (156) delimits a narrow gap (102), in a direction toward the high-pressure space (36) downstream of the radial outlet (190), in order to hydraulically separate the high-pressure space (36) or, if appropriate, the discrete storage chamber (38) from the connecting line (176), at least for transient processes.

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