EP2812559A1

EP2812559A1 - Fuel injection valve and device for injecting fuel

Info

Publication number: EP2812559A1
Application number: EP13702576.3A
Authority: EP
Inventors: Marco Ganser
Original assignee: Ganser Hydromag AG
Current assignee: Ganser Hydromag AG
Priority date: 2012-02-07
Filing date: 2013-02-01
Publication date: 2014-12-17
Anticipated expiration: 2033-02-01
Also published as: KR20140109470A; RU2607568C2; CN104093968B; KR101603029B1; RU2014136326A; JP6141328B2; US20140360469A1; WO2013117311A9; EP2812559B1; WO2013117311A1; JP2015506443A; US9587611B2; CN104093968A

Abstract

The fuel injection valve (1) for the intermittent injection of fuel into the combustion chamber of an internal combustion engine has a valve housing (12) that defines a longitudinal axis (14) and is provided with a high-pressure chamber (16). The connecting part (20) of the valve housing (12) has two identically formed high-pressure connections (22, 24) for high-pressure fuel lines. The two identically formed high-pressure connections (22, 24) are arranged in a common connecting face (30') in such a way that said high-pressure connections are oriented in the same direction and the connection axes (22', 24') thereof run parallel to each other. In the interior of the valve housing (12), the high-pressure connections (22, 24) are connected to each other and to the high-pressure chamber (16).

Description

Fuel injection valve and device for injecting fuel

The present invention relates to an injection valve for the intermittent injection of fuel into the combustion chamber of an internal combustion engine according to claim 1 and to an apparatus for the intermittent injection of fuel into a number of combustion chambers of an internal combustion engine according to claim 14.

A fuel injection valve is known from the document WO 2009/033304 AI. It has a longitudinal axis defining and a high-pressure chamber limiting valve housing, which carries at one end connected to the high-pressure chamber nozzle body. A housing body forming the valve housing is formed head-like thickened in its end region remote from the nozzle body and has two, with respect to the longitudinal axis diametrically opposite each other

High pressure connections on (Fig. 8). A bore extending in the direction of the longitudinal axis is closed by means of a sealing plug, which has a circumferential connecting groove, a radial bore opening into the bottom region thereof and a blind bore lying on the longitudinal axis. The two high-pressure connections are connected to one another via the connecting groove, and the high-pressure connections are connected to the high-pressure chamber via the radial bore and the blind bore.

CONFIRMATION COPY such fuel injection valves by means of

Combining fuel high-pressure connection lines with each other and a first of the series of fuel injection valves via a high-pressure fuel feed line with a

High-pressure pump to connect. Such a device for the intermittent injection of fuel into the combustion chambers of an internal combustion engine has the advantage that it is possible to dispense with bulky and expensive so-called common rails and still, with space-saving design, a reliable working of the injectors can be guaranteed. How this is made possible in a particularly simple manner is evident from the documents WO 2007/009279 A1 and WO 2009/033304 Al.

The document WO 2011/085058 Al discloses a fuel injection device, which has a

High-pressure input, a first fuel injection valve and at least one further fuel injection valve. Here, fuel is at least indirectly feasible via the high pressure input into a fuel space of the first fuel injection valve, wherein the further fuel injection valve is connected via a line to the first fuel injection valve and wherein via the fuel lines from the fuel space of the first fuel injection valve in a fuel space of the further fuel injection valve can be guided. To dampen pressure pulsations, the fuel chambers of the fuel injectors receive a total fuel volume that includes a partial volume for fuel injection and at least one additional fractional volume to facilitate damping. Next are in the lines or High pressure connections of the fuel injection valves

Built-in throttles.

It is an object of the present invention to provide a fuel injection valve for intermittent injection of fuel into the combustion chamber of an internal combustion engine and an apparatus for intermittent injection of fuel into a number of combustion chambers of an internal combustion engine such that high pressure fuel lines formed in a particularly simple manner and to the Fuel injection valve or the

Fuel injectors can be connected.

This object is achieved with a fuel injection valve having the features of claim 1, and a device having the features of claim 14.

The fuel injection valve according to the invention for the intermittent injection of fuel into the combustion chamber of an internal combustion engine has a preferably elongated and preferably at least approximately cylindrical valve housing which defines a longitudinal axis and in which a high-pressure space having a discrete storage chamber is arranged. This high-pressure chamber extends into the interior of a nozzle body, which is arranged at a longitudinal end of the valve housing and supported by this. In an end region of the valve housing facing away from the nozzle body, this has a connection part with two high-pressure connections. These each define their own Connection axis and are unthrottled with each other and flow associated with the high-pressure chamber.

According to the invention, the two high-pressure ports are arranged in a common connection surface of the connecting part, wherein they are the same direction and their connection axes parallel to each other.

In other words, high-pressure fuel lines can be connected to the two high-pressure ports from the same side. Preferably, a connecting line is present, which is formed in the valve housing and connects the high-pressure connections with each other and with the high-pressure chamber. A first section of the connecting line leads from the first high-pressure connection to the high-pressure chamber. A second section of the connecting line branches off from the first section and connects it to the second high-pressure connection. As a result, the high-pressure connections are connected to one another via a line and not via the high-pressure chamber. In a preferred embodiment, the connection surface is a connection plane. This allows a particularly simple design.

Particularly preferably, this connection plane extends at right angles to the longitudinal axis of the fuel injection valve. The high pressure connections are characterized - in the installed state - on a side facing away from the cylinder head of the internal combustion engine and thus freely accessible side of the

Fuel injection valve. Particularly preferably, the connection plane forms an end face of the valve housing. In a further preferred embodiment, the connection axes of the two high-pressure connections and the longitudinal axis of the valve housing are parallel to one another.

In a further preferred embodiment, the longitudinal axis and the connection axis lie in a common plane, with the longitudinal axis and one of the connection axes particularly preferably being aligned with one another.

A particularly simple embodiment of both the fuel injection valve and the high-pressure fuel lines results if the high-pressure connections are identical.

The high-pressure connections usually have, concentric with the connection axis, a high-pressure sealing surface, which preferably conically tapers toward the interior of the housing, for the high-pressure fuel lines.

In certain applications for inventive fuel injection valves, especially when used in marine engines, it may be necessary that leakage monitoring takes place. For this purpose, the high-pressure connections, in the radial direction outside the high-pressure sealing surfaces,

Leakage monitoring openings, which are fluidly connected to each other in the connection part. In these cases, the high-pressure fuel lines are double-walled, wherein the inner tube of the guide of the high-pressure fuel and the jacket space between the inner tube and the outer tube of the leakage monitoring is used. The shell space is then, in the mounted state, fluidly connected to the leakage monitoring openings and the Inner tube is then sealed with its sealing surface on the high-pressure sealing surface.

In a preferred embodiment of the

Fuel injector, the nozzle body to an injection valve seat, which is fluidly connected to the high-pressure chamber. Through the nozzle body passing nozzle openings are in a known manner in the region of the injection valve seat or centric of these in a nozzle tip. With the injection valve seat acts in particular a needle-shaped injection valve member, which is arranged adjustable in the valve housing in the direction of the longitudinal axis. A compression spring is supported on the injection valve member and acts on this with a directed in the direction of the injection valve seat closing force. On the other hand, the compression spring is supported on a guide sleeve and presses it against an intermediate plate sealingly. The guide sleeve together with a guided in the guide sleeve, formed on the injection valve member control piston defines a control chamber against the high-pressure chamber. A control device for controlling the axial movement of the injection valve member by changing the pressure in the control chamber has an intermediate valve, the intermediate valve member in the open position releases a high pressure passage connected to the high pressure chamber into the control chamber and in the closed position separates the control chamber from the high pressure passage. Further separates, preferably mushroom-shaped intermediate valve member continuously from the control chamber of a valve chamber, wherein the control chamber and the valve chamber are permanently interconnected solely via a throttle passage. By means of an electrically controlled actuator arrangement a pilot valve is actuated, which connects the valve chamber with a low-pressure fuel return or separates it from this.

The control device is designed in a preferred manner, as disclosed in the document WO 2007/098621 Al.

The actuator arrangement is preferably formed, as is known from the document WO 2008/046238 A2.

The relevant disclosure in these documents is hereby incorporated by reference in the present specification.

In a further preferred embodiment, the high-pressure chamber includes a discrete storage chamber. This makes it possible to keep the pressure drop in the injection processes within limits.

Furthermore, a throttle device is preferably provided which allows the flow of fuel from the high-pressure ports into the storage chamber at least approximately unhindered and throttles in the opposite direction. This allows high pressure fuel to be delivered to each fuel injector during its injection event both from the discrete storage chamber of another

Fuel injectors as well as from a high-pressure conveyor (high-pressure pump) ZufHessen can. In this regard, reference is expressly made to the document WO 2007/009279 AI, from which the structure and operation and dimensioning of such fuel injectors and discrete storage chambers (and their interaction with the High pressure fuel lines) is known. The disclosure in question is incorporated by reference in the present specification.

The throttle device is preferably designed as a check valve, the check valve member is provided with a throttle bore.

In a further preferred embodiment, the connection part has a connection body or is formed by it. The high-pressure connections and the connecting line are formed on the connection body, wherein the connecting line connects the high-pressure connections unthrottled with one another and with the discrete storage chamber, which is formed in a storage body of the valve housing adjacent to the connection body. Furthermore, a low-pressure fuel return connection-which is connected to the low-pressure fuel return-and an electrical connection which is connected to the actuator arrangement via an electrical connection line are preferably arranged on the connection body. An intermediate body, in which the actuator arrangement is arranged, is preferably located on the storage body. Moreover, a valve body of the valve housing preferably bears against the intermediate body, which carries the nozzle body on the side facing away from the intermediate body. In the valve housing, the injection valve member and the control device is arranged.

These bodies are preferably in succession in the direction of the longitudinal axis to each other and are preferably secured to each other by means of union nuts. Preferably, said bodies have an at least approximately circular cylindrical outer contour on, which may decrease (paragraph-like) from the intermediate body to the nozzle body in diameter.

Preferably, the valve housing, in particular the connecting body, at least one mounting flange,

5 which projects in the radial direction to the outside.

In particular, two diametrically opposite mounting flanges are provided. Preferably, the mounting flange, or are the

Mounting flanges, provided with a through hole. o To attach the fuel injector to the cylinder head of the internal combustion engine, the through hole is penetrated by a clamping screw, which is then supported with its head on the respective mounting flange and on the other hand in the

5 cylinder head is threaded.

Particularly preferred is the mounting flange, or are the mounting flanges, in the direction of the longitudinal axis, between the connecting part and the nozzle body, in particular on a running in the direction of the longitudinal axis o o of the connecting body.

The device according to the invention for the intermittent injection of fuel into a number of combustion chambers of an internal combustion engine has a fuel injection valve according to the invention per combustion chamber. The

5 fuel injection valves are identical in construction. To a first of the two high pressure ports of a first of these fuel injection valves is a first high pressure fuel line - a

Brennstoffhochdruckspeiseleitung - connected, which o for supplying the fuel injection valves with high-pressure fuel on the other hand with a High-pressure pump is connected. To a second of the two high-pressure connections of this first

Fuel injection valve is a second

High pressure fuel line connected, which on the other hand at the first high pressure port of the two high pressure ports of the next

Fuel injection valve is connected. This second Hochdruckbrennstof supply forms a

Fuel high-connection line. The fuel injection valves are unthrottled with each other and preferably also unthrottled with the

High pressure pump flow connected.

If only two fuel injection valves are present, the second high-pressure port of the second fuel injection valve is closed by means of a plug.

Is at least one more

Fuel injection valve is present, then the second high pressure port of the second injection valve, a further second high pressure fuel line is connected, which in turn is connected at its other end to the first high pressure port of the subsequent injection valve. In this way, a number of fuel injectors can be fed unthrottled via the high-pressure fuel lines, wherein the last high of the series of injection valves, the second high-pressure port is closed by a plug.

In such a device, on the one hand all fuel injectors can be designed to be identical and these are in a simple manner with high pressure stagnant fuel unthrottled available. It can be dispensed with a large storage volume, as it is known as "common rail". For this purpose, each fuel injection valve preferably has a discrete storage chamber and a throttle device, as described above. The mode of operation, design possibilities and dimensioning are disclosed in the document WO 2007/009279 Al, in order to enable optimal injection processes under all operating conditions.

In a particularly preferred embodiment, the second high-pressure fuel line or the second high-pressure fuel lines are provided with in-plane curvatures - that is to say that the center line of the second high-pressure fuel line lies in the plane. Such high-pressure fuel lines can be produced in a simple manner, and this is made possible by the fact that the identically designed injection valves are arranged parallel to each other and their high-pressure connections in the common pad, preferably in the connection plane lie.

In a particularly preferred embodiment, all the second high pressure fuel lines - that is, their centerlines - lie in a single plane, and more preferably, the longitudinal axes of the fuel injectors and their connection axes lie in the same single plane as the second

High-pressure fuel lines. Are the

Fuel injection valves arranged equidistantly, all second high pressure fuel lines can be made identical. The present invention will be explained in more detail with reference to an embodiment shown in the drawing. It shows purely schematically:

Fig. 1 in view of an inventive

Fuel injector; the injection valve according to Figure 1 in a section along the line II-II of Figure 1; in the same representation as Figure 2, but enlarged, a first portion of the fuel injection valve; in the same representation as Figure 2, but enlarged, a second portion of the fuel injection valve; in plan view, a common two combustion chambers of an internal combustion engine

Cylinder head, in which per combustion chamber a shown in Figures 1 to 4 injection valve is mounted, and

High-pressure fuel lines; in view of the fuel injection valves and the high pressure fuel lines according to Figure 5, without the cylinder head;

Fig. 7 is a plan view of a high pressure fuel line;

Fig. 8 in a section along the line VIII -VIII of

FIG. 7 shows the one shown there

High-pressure fuel line; FIG. 9 shows a connection section of the high-pressure fuel lines shown in FIGS. 5 to 8; and

Fig. 10 in perspective view a

Mounting sleeve for the

High pressure fuel lines.

The illustrated in the drawing

Fuel injection valve and the device shown with such injectors are intended for an ignition system for large reciprocating engines, which are operated with gas and / or diesel, also called "dual fuel" engines. Since these are very high power engines, the injectors can have a large overall length, as shown in the drawing. The injection valves serve, so to speak, as a pilot valve for igniting the main charge of fuel. Injectors and devices of the inventive type, however, can also be used - for engines of lower power - for injecting the main charge.

As can be seen in FIGS. 1 and 2, the fuel injection valve 10 according to the invention for the intermittent injection of fuel under very high pressure into the combustion chamber of an internal combustion engine has a valve housing 12 which defines a longitudinal axis 14 and in which a high-pressure space 16 is present.

The valve housing 12 carries at its injection-side end a nozzle body 18 which defines a nozzle chamber connected to the high-pressure chamber 16. In the end region facing away from the nozzle body 18 in the direction of the longitudinal axis 14, the valve housing 12 has a connection part 20, which forms a connection head 20 'of the fuel injection valve 10. In the exemplary embodiment shown, the connection part 20 is formed by a connection body 20 '.

At the connection part 20 or connection head 20 ', two identically formed high-pressure connections 22, 24 are formed, which each define a connection axis 22' or 24 '. The two

High-pressure ports 22, 24 are the same direction and their connection axes 22 ', 24' are parallel to each other.

In the illustrated embodiment, the connection axis 22 'of the first high pressure port 22 is aligned with the longitudinal axis 14; the latter and the two connection axes 22 'and 24' lie in a common plane 26 which coincides with the sectional plane II-II of FIG. 1 and the plane of the drawing of FIG.

The two high-pressure connections 22, 24 are unthrottled to one another and connected to the high-pressure chamber 16 by a connection line 28, in particular in the connection head 20 ', formed on the connection part 20.

A first section 28 'of the connecting line 28 connects the first high-pressure port 22 to the high-pressure chamber 16. A second section 28 "of the connecting line branches off from this first section 28' and leads to the second high-pressure port 24. The connecting line 28 has no throttles; as well are the high pressure ports 22, 24 formed without throttles.

The two high-pressure ports 22 and 24 are formed in a, in the present case, a connecting plane 30 forming connecting surface 30 ', which, seen in the direction of the longitudinal axis 14, the end face of the valve housing 12 forms. In the exemplary embodiment shown, the connection plane 30 extends at right angles to the longitudinal axis 14 and thus also at right angles to the connection axes 22 ', 24'. In the exemplary embodiment shown, the connection body 20 'forming the connection part 20 is L-shaped, the leg 32 extending in the direction of the longitudinal axis 14 having a circular cross-section and the connection leg 34 extending at right angles to it being parallelepiped-shaped; the latter forms the connection head 20 '.

On a side surface of the connecting leg 34, a low-pressure fuel return port 36 is arranged, and at a side surface extending at right angles thereto, there is an electrical connection 38 designed in the manner of a socket.

From the leg 32 are diametrically opposite in the radial direction against the outside attachment flanges 40 from whose through holes 40 'are intended to be penetrated by clamping screws 40' ¹ , by means of which the fuel injection valve on a cylinder head 42 (see Figure 5) of

Internal combustion engine 44 is attached. At the high pressure ports 22, 24 facing away from the end face of the leg 32 and thus of the connecting body 22 is a circular cylindrical storage body 46, which is held by a first union nut 48 in close contact. The storage body 46 forms part of the valve housing 12.

At the connection body 20 'facing away from the end of the storage body 46 is located on this an intermediate body 50 of the valve housing 12 at. Its outer contour is circular cylindrical.

On the side facing away from the storage body 46 of the intermediate body 50 is located on these a valve body 52 at. At this attacks a second union nut 54, which comprises the intermediate body 50 and the other end is threaded into an external thread of the storage body 46. By means of the second union nut 54, the valve body 52 on the intermediate body 50, and the latter on the storage body 46, held in sealing engagement.

At the free end of the valve body 52 of the nozzle body 18 abuts, which in turn is sealed by a third union nut 56 on the valve body 52.

For the sake of completeness, it should be mentioned that the central axes of the storage body 46, the intermediate body 50, the valve body 52 and the nozzle body 18 lie in the longitudinal axis 14.

As can be seen in FIGS. 2 and 3, the two high pressure ports 22, 24 are in cross section circular recesses 58 in the connector body 20 ^Λ concentric with the respective connection axes 22 ', 24 ^Λ formed.

The high-pressure connections 22, 24, or the recesses 58 forming them, have a circular-cylindrical first section 60 adjoining the connection plane 30 after a chamfering. The jacket wall of this first section 60 serves as a low-pressure sealing surface 60 ', as will be explained later in connection with FIGS. 7 to 10.

The first section 60 is followed, in the direction towards the interior of the connection body 20 ', by a conically tapering shoulder, to which a circular cylindrical second section 62 adjoins. The jacket wall of this second section 62 is formed as an internal thread 62 ¹ .

The plane, perpendicular to the respective connection axis 22 ', 24' extending bottom of the recess 58 is designated 64. Furthermore, each of the two high-pressure ports 22, 24 has a conically tapering high-pressure sealing surface 66 which extends from the bottom 64 and whose axis coincides with the relevant connecting shaft 22 ', 24'. Of the high-pressure sealing surface 66 of the first high-pressure port 22 extends concentrically to the connection axis 22 'and longitudinal axis 14, a longitudinal bore 68 through the nozzle body 18 through to its, the high-pressure ports 22, 24 facing away from the front side. Of the high-pressure sealing surface 66 of the second high-pressure port 24 extends in the direction of the connection axis 24 ', a blind hole 70 which opens into a transverse bore 72, which in turn opens into the longitudinal bore 68.

The transverse bore 72 extends at right angles to the longitudinal axis 14 and the connection axes 22 ', 24' and in the plane 26. It is formed by the second high-pressure port 24 closer side surface 74 of the connecting leg 34 forth to the longitudinal bore 68, where they, in a the side surface 74 adjacent end portion has a larger cross section, and stepwise tapered, is formed. In the inner end of this end region, a sealing ball 76 is arranged, which is held by means of an indented and sealed in the end region Andrückstopfens 78 such that it seals the transverse bore 72 high pressure moderately. For this purpose, the transverse bore 72 can subsequently have a conically tapered sealing surface against the end region, against which the sealing ball 76 is pressed.

A section 68 'of the longitudinal bore 68 (corresponding to the first line section 28 ¹ ) leading from the high-pressure connection 22 to the high-pressure chamber 16, the blind bore 70 and the transverse bore 72 (corresponding to the second line section 28'') form the connection line 28 mentioned above.

From an annular space extending around the sealing ball 76, on the side facing the pressing plug 78, a leakage longitudinal bore 80 extends parallel to the connection axis 24 'to the bottom 64 of the second High-pressure port 24, where it, seen in the radial direction, outside the respective high-pressure sealing surface 66, opens into the recess 58 and forms there a leakage monitoring opening. Further extending from the bottom 64 of the recesses 58 of the two high pressure ports 22, 24 from the facing sides leakage bevels 82, which open into one another. For the sake of completeness, it should be mentioned that the high-pressure connection-side openings of the leakage orifices 82 lie in the radial direction outside the high-pressure sealing surfaces 66 and likewise form leakage monitoring openings.

At this point, it should be mentioned that leakage bores, such as the leakage longitudinal bore 80 and leakage orifices 82, are not necessary if leak monitoring is dispensed with. The operation of the leakage monitoring will be explained in more detail below in connection with FIGS. 7 to 10. The leakage longitudinal bore 80 in the exemplary embodiment shown serves to monitor the sealing of the connecting line 28 by means of the sealing ball 76.

The storage body 46 has a blind hole, which is produced from the end face facing the connection body 20 'in the mounted state, to the cross section of the connection line of larger diameter. In the illustrated embodiment, this diameter is about 1/3 of the outer diameter of the circular cylindrical storage body 46. The blind hole serves to form a discrete storage chamber 84 for the fuel under high pressure. From the terminal body 20 ^Λ facing away from the end of the storage body 46, with respect to the longitudinal axis 14 obliquely, a connecting bore 86 to the bottom of the storage chamber 84th

In an end section facing the connection body 20 ', the blind hole bore has a larger diameter,

5 to support a shoulder for supporting a valve carrier 88 of a check valve 90. Of the

Check valve seat 92 is formed by an annular, around the mouth of the connecting line 28 extending around part of the storage body 46 facing the end face of the o connection body 20 '. With the

Check valve seat 92 operates a plate-shaped check valve body 94 together, which has centrally, on the longitudinal axis 14, a continuous throttle bore 96.

5 The check valve body 94 is acted upon by means of a closing spring 98 designed as a compression spring, which is supported at the other end on the valve carrier 88, with a closing force directed into the closed position of the check valve 90. o Centrally through the valve carrier 88 passes through a passage 100 at least approximately the same cross section as the connecting line 28. Incidentally, the valve carrier 88 closes the storage chamber 84 in the axial direction to the connecting body 20 'out from.

The check valve 90, which forms a throttle device, allows the flow of high pressure fuel from the high pressure ports 22, 24 into the storage chamber 84 at least approximately unhindered and throttles the flow in the opposite direction. If a plurality of fuel injection valves 10 are connected to each other and to a high-pressure fuel pump 166 by means of high-pressure fuel lines 164, 164 ', as is shown in FIGS. 5 and 6 and described in more detail below, the throttling action of the check valve 90 is designed such that each fuel injection valve 10 during a

Injection process high pressure fuel from the

Storage chambers 86 of other fuel injection valves 10, from the high-pressure fuel lines 164, 164 'and from the high-pressure conveyor 166 flows. These

Mode of operation is described in detail in document WO 2007/009279 AI and also in document WO 2009/033304 AI. It is explicitly referred to these documents.

On the valve carrier 88, a filter 102, in this case a cup-shaped hole filter, further attached, which protrudes from the valve carrier 88 into the interior of the storage chamber 84 and in which the passage 100 opens through the valve carrier 88. The filter 102 and the check valve 90 can be designed differently, preferred embodiments are shown in the document WO 2009/033304 Al.

The filter 102 prevents solid particles from entering the high-pressure chamber 16 and impairing the function of the fuel injection valve 10.

Furthermore, a channel 104 runs through the wall of the storage body 46 defining the storage chamber 84 in the longitudinal direction. A corresponding channel is also formed on the connection body 20 ', which communicates with the channel 104 is aligned and leads to the electrical connection 38. From this leads an electrical control line 106 through the channel 104 in the connector body 20 'and storage body 46 to terminal contacts 108, which protrude into the channel 104 in the assembled state.

Finally, the storage body 46 has a recess facing away from the connection body 20 'and facing the intermediate body 50 facing end face recess in which a compression spring 110 is arranged. This serves to hold an electrically controlled

Actuator 112, in a corresponding recess in the intermediate body 50. The actuator 112 is electrically connected to the terminals 108 and via this and the electrical control line 106 to the electrical connection 38.

Such actuator arrangements 112 are generally known and in the present case designed as shown and described in detail in FIG. 5 of the document WO 2008/046238 A2. The differently designed actuator arrangements, as disclosed in the cited document, can be found in the present

Fuel injector 10 are used. With regard to structure and mode of operation, reference is expressly made to the document WO 2008/046238 A. In the embodiment shown in Figures 2, 3 and 4, the actuator assembly 112 is in a

Aktuatoraufnahmeausnehmung 113 of the intermediate body 50 is received, which, with respect to the longitudinal axis 14, is laterally offset. This provides space for another connection bore 86 'which communicates with the Connecting bore 86 is fluidly connected and parallel to the longitudinal axis 14 through the intermediate body 50 extends therethrough.

The actuator assembly 112 has an actuating shaft 114, which is biased by means of an actuator spring 116 in the closing direction of a pilot valve 118 and against the force of the actuator spring 116 by means of an electromagnet 120 in the opening direction of the pilot valve 118 is movable. The solenoid 120 is driven by an electrical controller which supplies the control signals to the electrical connection 38.

From the bottom of the Aktuatoraufnahmeausnehmung 113 of the intermediate body 50 extends through this passage, in which a pilot valve member 122 is slidably received in the axial direction. This is actuated by means of the operating shaft 114.

From the bottom region of the Aktuatoraufnahmeausnehmung 113 passes through the intermediate body 50, then the accumulator body 46 and the connector body 20 ^Λ to low pressure fuel return port 36 a dashed line indicated low pressure fuel return 123. The flowing at open pilot valve 118 fuel is thus guided to a fuel recirculation header, as is well known. As shown in particular in Figure 4, the valve body 52 has a circular cross-section, multi-stepped, continuous in the axial direction and concentric to this

Valve body recess 124, in which a needle-shaped injection valve member 126 slidably in the axial direction and a hydraulic control device 128 are included for controlling the movement of the injection valve member 126 in a known manner. The injection valve member 126 protrudes into the cup-shaped nozzle body 18 and acts there in a known manner with an injection valve seat 130 together to connect through nozzle openings 132 with the high-pressure chamber 16 and separate from it. For the sake of completeness, it should be mentioned that there is a gap between the injection valve member 126 and the valve body 52 and the nozzle body 18, so that the high-pressure fuel can feed the injection valve seat 130 and the nozzle openings 132 with little loss.

A compression spring 134 is supported on the one hand in a known manner on the injection valve member 126 and acts on this with a directed in the direction against the injection valve seat 130 closing force. On the other hand, the compression spring 134 is supported on a guide sleeve 136, which is thereby pressed sealingly against an intermediate plate 138.

In this side end region of the injection valve member is designed as a control piston 140 which is guided in the guide sleeve 136 in close sliding fit. The control piston, together with the guide sleeve, delimit a control arm 142 against the high-pressure chamber 16.

In the illustrated embodiment, the needle-shaped injection valve member 122 on the one hand on the guide sleeve 136 and on the other hand guided in radially projecting guide lips on the nozzle body 18.

To control the movement of the injection valve member 126 in the axial direction, the pressure in the control chamber 142 is changed by means of a hydraulic control device 128.

The control device 128 has an intermediate valve 145 with an intermediate valve member 146 which, in the open position, releases a high-pressure passage 148 which leads from the high-pressure chamber 16 into the control chamber 142 and closes it in the closed position in order to separate the control chamber 142 from the high-pressure chamber 116 ,

Furthermore, the intermediate valve member 146 permanently separates the control chamber 142 from a valve chamber 150, with the exception of a throttle passage 152, via which the control chamber 142 with the valve chamber 150 are permanently connected to one another via a small flow cross section.

In the embodiment shown, the intermediate valve member 146 is mushroom-shaped, wherein the

Stem in sliding fit into a Durchläse the

Intermediate plate 138 is guided and arranged in the control chamber 142 mushroom head in the closed position against the intermediate plate 138 to close the arranged in this area the mouth of the high-pressure passage 148. Is the mushroom head lifted from the intermediate plate 138, the fuel between this and the

Guide sleeve 136 into the control chamber 142. On the side facing away from the control chamber 142, the intermediate plate 138 sealingly abuts against a further intermediate plate 154, which is held in a predefined rotational position in the valve housing 112 by means of a positioning pin 156 and which, together with the intermediate plate 138 and the intermediate valve member 146 or the mushroom trunk thereof Valve space 150 limited.

In alignment with the axis of the actuator assembly 112, the further intermediate plate 154 has an outlet passage 158, which is tapered in a stepwise manner from the valve space 150 in the direction of the actuator arrangement 112.

The outlet passage 158 is closable by means of the pilot valve member 122 controlled by the actuator arrangement 112 or to

Low pressure fuel return 123 can be opened. The further intermediate plate 154 forms a pilot valve seat of the pilot valve 118 which cooperates with the pilot valve member 122, with an annular region extending around the mouth of the outlet passage 158.

The detailed structure and operation of fuel injection valves 10 with such a control device 128, with the pilot valve 118 and the actuator assembly 112, is described in detail in the publications WO 2007/098621 A and WO 2008/046238 A. The other embodiments disclosed in these documents can also be used in the fuel injection valve 10 according to the invention. FIG. 5 shows part of a device for the intermittent injection of fuel into a number of combustion chambers of an internal combustion engine 44. Only one cylinder head 42 assigned to two combustion chambers is shown in FIG. In a known manner, the cylinder head 42 per combustion chamber on a fuel injection valve receiving passage, in each of which a fuel injection valve 10, as shown in Figures 1 to 4 and described above, is used.

By means of clamping screws 40 '', the injection valves 10 are fixed to the cylinder head 42.

With their connection part 20 or connection body 20 ', the injection valves 10 project beyond the cylinder head 42 and the high-pressure connections 22, 24 are located on the connection plane 30 facing away from the cylinder head 42 and are thus freely accessible.

A first high-pressure fuel line 164 forms a high-pressure fuel feed line and is connected, on the one hand, to a high-pressure feed pump 166 and, on the other hand, to the first high-pressure port 22 of a first injection valve 10 of the series of injection valves.

At the second high pressure port 24 of this fuel injection valve 10, a second high pressure fuel line 164 'is connected, which on the other hand is connected to the first high pressure port 22 of the next following fuel injection valve 10. FIGS. 5 and 6 show a further second high-pressure fuel line 164 ', which has the second high-pressure port 24 of the second

Fuel injection valve 10 with the first high-pressure port 22 of a not shown, the next following fuel injection valve 10 connects.

Form the second high-pressure fuel lines

Fuel high-pressure connection lines.

In the last of the series of injection valves 130, the second high pressure port 24 is closed by a plug.

FIG. 6 shows the same arrangement of FIG

Fuel injection valves 10 and

High-pressure fuel lines 164, 164 ', as Figure 5, but without the cylinder head 42nd

Preferably, as in the illustrated embodiment, the longitudinal axes 14 of the fuel injectors 10 of the series of fuel injectors 10, as well as their connection axes 22 ', 24' of the high pressure ports 22, 24 in the common plane 26th

Further, in the illustrated embodiment, the centerlines 168 of the second high pressure fuel lines 164 'forming fuel high pressure communication lines are also in the same plane 26. In the illustrated embodiment, this also applies to the first high pressure fuel line 164. The connection levels 30 of all interconnected fuel injection valves 10 are also in one plane.

The advantage of this arrangement is that the second high-pressure fuel lines 164 ', and in the present case also the first high-pressure fuel line 164, only have to have two 90 ° bends lying in the plane 26 and can be assembled and disassembled in a simple manner. In the present exemplary embodiment, the high-pressure fuel lines 164, 164 'have a double-walled design for monitoring any leakage, as can be seen from FIGS. 7 and 8. An inner tube 170 is designed to guide the under very high pressure fuel. It has at both ends a conically tapering towards the free end, in the radial direction outside lying high pressure sealing surface 172, which is intended in the assembled state to cooperate with the high pressure sealing surface 66 of the respective high pressure port 22, 24.

The inner tube 170 extends within a (thin-walled) outer tube 174, wherein between the outer tube 174 and the inner tube 170, a leakage return gap 176 is present. At their two ends, the

High pressure fuel lines 164, 164 'a

Connection nut 178 on; In this regard, reference is also made to FIGS. 9 and 10. The terminal nut 178 is in a free end of the high pressure fuel line 164, 164 'facing

End region provided with an external thread 180, which is intended to be threaded into the internal thread 62 'of the second portion 62 of the respective high-pressure port 22, 24.

Further, the connection nut 178 has a radially outwardly open circumferential groove into which an O-ring 182 is inserted, which in the assembled state with the sealing surface 60 'in the first section 60 of the respective high-pressure port 22, 24 cooperates to the interior of the recess 58 to seal against the environment.

Further, the terminal nut 178 has a nut passage 184 extending therethrough in the axial direction, through which the inner tube 170 passes to form a gap 186. In its two-sided end portions of the mother passage 184 is formed larger in diameter. In the external thread 180 facing away from the first end portion 190 engages the outer tube 174, on the outside of another O-ring 182 'sealingly applied, which on the other hand is received in an inner circumferential groove of the connecting nut 178. In the free end of the high pressure fuel line 64, 64 'facing the second end portion 190' is a mounting sleeve 192 is arranged, the structure of which is particularly well apparent from Figure 10. It has in the axial direction in a central portion of an internal thread 194, by means of which they on a corresponding external thread of the Inner tube 170 is threaded. In its end region facing away from the free end of the high-pressure fuel line 164, 164 ', the fastening sleeve 194 has four cross-shaped, groove-shaped leakage recesses 196 extending in the radial direction. Here, the fastening sleeve 192 is provided on the outside with a cone taper 198, which cooperates with a corresponding cone support surface 200 on the utterdurchlass 184. In the assembled state, the high pressure sealing surface 172 of the inner tube 170 by means of the connection nut 178 via the mounting sleeve 192 in close contact with the high pressure sealing surface 66 of the respective

High pressure port 22, 24 held. Should the seal formed by the two sealing surfaces 66 and 172 leak, the leakage fuel can pass through the leakage recesses 196 into the gap 186 defined radially from the connecting nut 178. This is fluidly connected to the leakage return gap 176 between the inner tube 170 and the outer tube 174. If the inner tube 170 licks itself, the leakage fuel in question is caught in the outer tube 174.

Furthermore, in the connection parts 20, the gaps 186 and thus the leakage return gaps 176 of the high-pressure fuel lines 164, 164 'are flow-connected to one another by means of the leakage bevel bores 182. In this connection also leads the Leckagelängsbohrung 80, which can be determined by a simple manner a possible leakage of fuel. A single leakage sensor, which is preferably arranged at the beginning or at the end of the line system, is sufficient thus, to monitor the entire device for leakage.

In a known manner, the fuel injection valves 10 are sequentially controlled in a predetermined order for injection of very high pressure fuel. In the idle state, the pilot valve 180 in the closing and the intermediate valve 145 in the open position and the injection valve member 126 sealingly against the injection valve 130 at.

To trigger an injection process, the actuator assembly 112 of the relevant

Fuel injector 10 is electrically energized, whereby the pilot valve member 122 is released. As a result of the pressure in the valve chamber 150 high pressure, the pilot valve member 122 is lifted from its attachment to the further intermediate plate 154, after which fuel from the valve chamber 150 into the low-pressure fuel return 123 flows. As a result of the resulting pressure difference between the pressure in the control chamber 142 and in the valve chamber 150, the intermediate valve 145 is closed, so that in the control chamber 142 can not nachfHessen high-pressure fuel from the high-pressure chamber 16. Due to the outflow of fuel from the control chamber through the throttle bore 96 into the valve chamber, the pressure in the control chamber 142 decreases, which leads to the lifting of the injection valve member 126 from the injection valve seat 130. As a result, high-pressure fuel is injected through the nozzle openings 132 into the combustion chamber. To end the injection process, the actuator assembly 112 is de-energized, resulting in the closure of the pilot valve 118. As a result, the pressure in the valve chamber 150 increases by allowing fuel to flow through the throttle bore 96 out of the control chamber 142. As a result of this pressure increase, the intermediate valve 145 opens and the subsequent flow of high-pressure fuel from the high-pressure chamber 16 into the control chamber 142 is released. This leads to a rapid pressure increase in the control chamber 142, which leads to the movement of the injection valve member 162 to the injection valve seat 130 and the termination of the injection process.

During the injection process, the pressure in the high-pressure chamber 16 decreases. As a result of the discrete memory chambers 84 and the check valve 90 provided with the throttle bore 96, fuel can now be injected from the high-pressure delivery pump 166, the high-pressure fuel lines 164, 164 'and further fuel injection valves 10 into the injecting fuel injection valve during an injection process 10 refill. This ensures optimum injection processes with smaller discrete storage chambers 46 and thus less space consuming fuel injectors 10, without a large storage chamber in the form of a "common rail" is present.

In contrast to the embodiment shown in FIGS. 2, 3, 5 and 6, the high-pressure connections 22, 24 can also be arranged such that their connection axes 22 ', 24 * have an angle of 90 ° with a longitudinal direction defined by the longitudinal axis 14 or enclose an angle between 0 ° and 90 °.

Claims

claims

Fuel injection valve for the intermittent injection of fuel into the combustion chamber of an internal combustion engine, comprising a valve housing (12) having a high-pressure chamber (16) with a discrete storage chamber (84) and defining a longitudinal axis (14), which on the one hand has a nozzle body connected to the high-pressure chamber (16) (18) carries and on the other hand a connecting part (20) with two, each a connection axis (22 ', 24') defining, with the high-pressure chamber (16) and unthrottled interconnected high-pressure connections (22, 24) for high-pressure fuel lines (164, 164 ') , wherein the high pressure connections (22, 24) in a common connection surface (30 ') of the

Connecting part (20) are arranged such that they are rectified and their connection axes (22 ', 24') parallel.

Fuel injection valve according to Claim 1, characterized by the high-pressure connections

(22, 24) with each other and with the high pressure chamber (16) connecting connecting line (28), one from the first high pressure port (22) to the high pressure chamber (16), in particular to the discrete storage chamber (84), leading first section

(28 ') and a branching off from this second portion (28 ¹ '), which leads to the second high pressure port (24). Fuel injection valve according to claim 1 or 2, characterized by a throttle device (90) which allows the flow of fuel from the high pressure ports (22, 24) in the discrete storage chamber (84) at least approximately unhindered and throttles in the opposite direction.

Fuel injection valve according to one of claims 1 to 3, characterized in that the valve housing (12) at least one, in the radial direction protruding outwards

Mounting flange (40), preferably diametrically projecting from the valve housing (12)

Mounting flanges (40), and preferably each mounting flange (40) is provided with a through hole (40 ') which is intended - for fastening the fuel injection valve to a cylinder head (42) of the internal combustion engine (44) - by a clamping screw (40'). ') to be penetrated.

Fuel injection valve according to claim 4, characterized in that the fastening flange (40) or the fastening bottle (40), in the direction of the longitudinal axis (14), between a connection head 20 'of the connecting part (20) and the nozzle body (18) is arranged or are.

6. Fuel injection valve according to one of claims 1 to 5, characterized in that the connection surface (30 ') is a connection plane (30).

7. Fuel injection valve according to claim 6, characterized in that the connection plane (30) extends at right angles to the longitudinal axis (14).

8. Fuel injection valve according to one of claims 1 to 7, characterized in that the

Connecting axes (22 ', 24') parallel to the longitudinal axis (14) extend.

9. Fuel injection valve according to claim 8, characterized in that the longitudinal axis (14) and the connection axes (22 ', 24') in a common

Level (26) run.

10. Fuel injection valve according to one of claims 1 to 9, characterized in that the high pressure ports (22, 24) are identical.

11. Fuel injection valve according to one of claims 1 to 10, characterized in that the high-pressure connections (22, 24) in the center a preferably conical connection sealing surface (66) for the high-pressure fuel lines (164, 164 ') and, in the radial direction outside the

Terminal sealing surfaces (66), interconnected leakage monitoring openings (82).

12. Fuel injection valve according to one of claims 1 to 11, characterized in that the nozzle body (18) having a high pressure chamber (16) connected to the injection valve seat (130), with which in the valve housing (12) in the direction of the longitudinal axis (14) adjustable arranged injection valve member (126) cooperates, a compression spring (134) on the one hand to injection valve member (126) is supported and this acted upon with a directed towards the injection valve seat (130) closing force and on the other hand on a guide sleeve (136) is supported while the guide sleeve (136) to an intermediate plate (138) presses sealingly, the guide sleeve (136) together with a guided in the guide sleeve (136) control piston (140) of the injection valve member (126) a control chamber (142) against the high-pressure chamber (16) delimits a control device (128) for control the axial movement of the

Injection valve member (126) by changing the pressure in the control chamber (142) has an intermediate valve (145), the intermediate valve member (146) in the open position with the high pressure chamber (16) connected high pressure passage (148) in the control chamber (142) releases and in the closed position the Control chamber (142) from the high pressure passage (148) separates and the control chamber (142) from a valve chamber (150) continuously - up to a throttle passage (152) - separated, and by means of an electrically actuated actuator assembly (112) of the valve chamber (150) with a

Low pressure fuel return (123) can be connected and disconnected from this.

Fuel injection valve according to claim 12, characterized in that the connecting part (20) has a connection body (20 ') to which the high-pressure connections (22, 24) and optionally the connecting line (28) are formed, the connecting line (28) unthrottled to the high-pressure connections (22, 24) and to the discrete storage chamber (84) formed in a storage body (46) of the valve housing (12) resting against the connecting body (20 '). connects, on the connection body (20 '), a low-pressure fuel return port (36) and a with the actuator assembly (112) connected to electrical connection (38) are arranged on the storage body (46) an intermediate body (50) of the valve housing (12) is present, in which the actuator assembly (112) is arranged, and on the intermediate body (50) a valve body (52) of the valve housing (12) is present, which on the other hand carries the nozzle body (18) and in which the injection valve member (126) and the

Control device (128) are arranged.

Apparatus for the intermittent injection of fuel into a number of combustion chambers of an internal combustion engine, with per combustion chamber a fuel injection valve (10) according to one of claims 1 to 13, wherein the

Fuel injection valves (10) are of identical construction, to a first of the two high pressure ports (22, 24) of a first of the fuel injection valves (10) a first high pressure fuel line (164) - a

Fuel high - pressure feed line - is connected, which for feeding the

Fuel injection valves (10) with fuel on the other hand with a high-pressure feed pump (166) is connected, and to each of the second of the both high pressure ports (22, 24) of the fuel injectors (10) have a second high pressure fuel line (164 ·) - one

High-pressure fuel line connection

on the other hand connected to a first high-pressure port (22) of a respective subsequent fuel injection valve (10), however, the last of the fuel injection valves (10) of the second high-pressure port (24) is closed by means of a plug and wherein the

Fuel injectors are connected to each other and preferably with the high pressure pump (166) unthrottled.

15. The apparatus according to claim 14, characterized in that the second high-pressure fuel line (164 ¹ ), or all the second high-pressure fuel lines (164 ¹ ), in a single plane (26) has or have curvatures lying.

16. The apparatus of claim 14 or 15, characterized in that the second high-pressure fuel lines (164 ') lie in a single plane (26).

17. Device according to one of claims 14 to 16, characterized in that the longitudinal axes (14) of the fuel injection valves (10) and their connection axes (22 ', 24') in the same plane (26) as the second high-pressure fuel lines (164 ') ,