FUEL INJECTION VALVE FOR INTERNAL COMBUSTION ENGINES

Abstract

The fuel injection valve has a hydraulic control device for controlling the axial movement of the injection valve member. The stem of the intermediate valve member of mushroom-shaped configuration of the intermediate valve is guided in the guide recess of the intermediate part. In the open position, the intermediate valve member opens up a second connection between a high-pressure fuel inlet and a valve chamber and, in the closed position, the intermediate valve member shuts off the second connection between the high-pressure fuel inlet and the valve chamber. In the closed position of the intermediate valve member, the head of the intermediate valve member lies with a side facing toward the intermediate part against the intermediate valve seat via a first sealing surface, which runs around the stem or the guide recess at a first radial spacing so as to form a first annular sealing surface which is continuous in the circumferential direction.

Claims

1. A fuel injection valve (10) for intermittently injecting fuel into the combustion chamber of an internal combustion engine, having a housing (12') which defines a longitudinal axis (L) and has a high-pressure fuel inlet (24') and an injection valve seat (18'); a high-pressure chamber (26) which is disposed in the housing (12') and runs from the high-pressure fuel inlet (24') to the injection valve seat (18'); an injection valve member (56) which is disposed in the housing (12') so as to be adjustable in the direction of the longitudinal axis (L) and interacts with the injection valve seat (18'); a compression spring (62') which impinges the injection valve member (56) with a closing force directed in the direction towards the injection valve seat (18'); a guide part (64) in which a control piston (68) of the injection valve member (56) is guided in a sliding fit; an intermediate part (66) which, together with the guide part (64) and the control piston (68), delimits a control chamber (70); a hydraulic control device (72) for controlling the axial movement of the injection valve member (56) by modifying the pressure in the control chamber (70), having an intermediate valve (83) comprising an intermediate valve member (78) which is configured in the shape of a mushroom and has a shaft (76), guided in a guiding recess (74) of the intermediate part (66), and a head (80), and an intermediate valve seat (82) which is configured on a side of the intermediate part (66) that faces the head (80) and which interacts with the head (80), wherein the intermediate valve member (78) in an open position releases a first connection between a high-pressure fuel supply port (86), connected to the high-pressure chamber (26), and the control chamber (70), and in a shut position interrupts the first connection between the high-pressure fuel supply port (86) and the control chamber (70) as well as, with the exception of a throttle passage (90), separates the control chamber (70) from a valve chamber (44); an electrically operatable actuator assembly (38) for connecting the valve chamber (44) to and separating the valve chamber (44) from a low-pressure fuel return (46); wherein the intermediate valve member (78) in the open position releases a second connection (118, 117, 96, 74, 126, 119, 108, 441, 441.1, 441.2) between the high-pressure fuel supply port (86) and the valve chamber (44), and in the shut position interrupts the second connection (118, 117, 96, 74, 126, 119, 108, 441, 441.1, 441.2) between the high-pressure fuel supply port (86) and the valve chamber (44).

2. The fuel injection valve (10) as claimed in claim 1, wherein the second connection (118, 117, 96, 108, 441, 441.1, 441.2) runs between the high-pressure fuel supply port (86) and a bore (92) which is part of the valve chamber (44) and runs through the shaft (76) of the intermediate valve member (78).

3. The fuel injection valve (10) as claimed in claim 1, wherein the head (80) in the shut position of the intermediate valve member (78), by way of a side that faces the intermediate part (66), across a first sealing face (111.2) that runs at a first radial spacing (r1) about the shaft (76) or the guiding recess (74), while forming a first annular sealing face (121) inherently closed in the encircling direction, and across a second sealing face (112.2) that runs at a second radial spacing (r2) about the shaft (76) or the guiding recess (74), while forming a second annular sealing face (122) inherently closed in the encircling direction, bears on the intermediate valve seat (82), wherein the first radial spacing (r1) is larger than the second radial spacing (r2).

4. The fuel injection valve (10) as claimed in claim 3, wherein a first annular sealing bead (111), having a first end face (111.1) which forms the first sealing face (111.2), is configured on that side of the head (80) that faces the intermediate part (66) or on that side of the intermediate part (66) that faces the head (80).

5. The fuel injection valve (10) as claimed in claim 3, wherein a second annular sealing bead (112), having a second end face (112.1) which forms the second sealing face (112.2), is configured on that side of the head (80) that faces the intermediate part (66) or on that side of the intermediate part (66) that faces the head (80).

6. The fuel injection valve (10) as claimed in claim 3, wherein the intermediate part (66) on the side that faces the head (80) has at least one gradation (125), and the head (80) on the side that faces the intermediate part (66) has at least one gradation (127), wherein in the shut position of the intermediate valve member (78) mutually offset edges (125.1, 127.1) of the gradations (125, 127) of the intermediate part (66) and of the head (80) radially delimit in each case the first and/or the second annular sealing face (121, 122).

7. The fuel injection valve (10) as claimed in claim 6, wherein a gradation (125) of the intermediate part (66) forms an inner annular chamber (126) which in the shut position of the intermediate valve member (78) is delimited by the intermediate part (66), the shaft (76) and the head (80).

8. The fuel injection valve (10) as claimed in claim 3, wherein the high-pressure fuel supply port (86) in the intermediate part (66) runs in such a manner that the high-pressure fuel supply port (86) in the shut position of the intermediate valve member (78) opens into an annular gap space (118) which in the shut position of the intermediate valve member (78) is configured between the intermediate part (66) and the head (80) and is radially delimited by the first and the second annular sealing face (121, 122).

9. The fuel injection valve (10) as claimed in claim 1, wherein the second connection (118, 117, 96) comprises a supply port (96) of the intermediate valve member (78) which by way of a first end opens into the valve chamber (44) and by way of a second end opens toward an external side of the intermediate valve member (78).

10. The fuel injection valve (10) as claimed in claim 8, wherein the supply port (96) by way of the second end opens toward the external side of the intermediate valve member (78) in such a manner that the second end in the shut position of the intermediate valve member (78) is disposed at a radially smaller spacing from the shaft (76) than the second annular sealing face (122).

11. The fuel injection valve (10) as claimed in claim 1, wherein the second connection (118, 117, 74, 126) comprises a passage which is formed by a clearance present in the radial direction between the shaft (76) and the guiding recess (74), said clearance being at least 10 .Math.m, preferably between 20 .Math.m and 50 .Math.m.

12. The fuel injection valve (10) as claimed in claim 1, wherein the shaft (76) has two annular protrusions (761, 762) that are mutually spaced apart in the longitudinal direction of the shaft (76).

13. The fuel injection valve (10) as claimed in claim 12, wherein the annular protrusions (761, 762) in the circumferential direction each have at least one chamfer (762.1, 762.2, 762.3), wherein the second connection (118, 117, 126, 74) comprises a passage which is formed by an intermediate space (119) between the at least one chamfer (762.1, 762.2, 762.3) and the guiding recess (74).

14. The fuel injection valve (10) as claimed in claim 13, wherein the annular protrusions (761, 76) in the circumferential direction each have two or three chamfers (762.1, 762.2, 762.3).

15. The fuel injection valve (10) as claimed in claim 1, wherein the shaft (76) in the circumferential direction has at least one chamfer, wherein the second connection comprises a passage which is formed by an intermediate space between the at least one chamfer and the guiding recess (74).

16. The fuel injection valve (10) as claimed in claim 1, wherein the second connection (118, 108, 441, 441.1, 441.2) comprises a bore (441, 441.1, 441.2) which runs through the head (80) of the intermediate valve member (78) and forms a valve chamber passage (441, 441.1, 441.2) connected to the valve chamber (44) and by way of one end opens out on a side of the head (80) that faces the intermediate part (66).

17. The fuel injection valve (10) as claimed in claim 3, wherein the valve chamber passage (441, 441.1, 441.2) in the intermediate valve member (78) runs in such a manner that the valve chamber passage (441, 441.1, 441.2) in the shut position of the intermediate valve member (78) opens into an annular gap space (118) which in the shut position of the intermediate valve member (78) is configured between the intermediate part (66) and the head (80) and is radially delimited by the first and the second annular sealing face (121, 122).

18. The fuel injection valve (10) as claimed in claim 16, wherein the fuel injection valve has an annular chamber (120) which in the shut position of the intermediate valve member (78) is delimited by the intermediate part (66), the shaft (76) and the head (80) and into which the high-pressure fuel supply port (86) opens.

19. A fuel injection valve (10) for intermittently injecting fuel into the combustion chamber of an internal combustion engine, having a housing (12') which defines a longitudinal axis (L) and has a high-pressure fuel inlet (24') and an injection valve seat (18'), a high-pressure chamber (26) which is disposed in the housing (12') and runs from the high-pressure fuel inlet (24') to the injection valve seat (18'), an injection valve member (56) which is disposed in the housing (12') so as to be adjustable in the direction of the longitudinal axis (L) and interacts with the injection valve seat (18'), a compression spring (62') which impinges the injection valve member (56) with a closing force directed in the direction towards the injection valve seat (18'), a guide part (64) in which a control piston (68) of the injection valve member (56) is guided in a sliding fit, an intermediate part (66) which, conjointly with the guide part (64) and the control piston (68), delimits a control chamber (70), a hydraulic control device (72) for controlling the axial movement of the injection valve member (56) by modifying the pressure in the control chamber (70), having an intermediate valve (83) comprising an intermediate valve member (78) which is configured in the shape of a mushroom and has a shaft (76), guided in a guiding recess (74) of the intermediate part (66), and a head (80), and an intermediate valve seat (82) which is configured on one side of the intermediate part (66) that faces the head (80) and which interacts with the head (80), wherein the intermediate valve member (78) in an open position releases a connection between a high-pressure fuel supply port (86) connected to the high-pressure chamber (26) and the control chamber (70), and in a shut position interrupts the connection between the high-pressure fuel supply port (86) and the control chamber (70) as well as, with the exception of a throttle passage (90), separates the control chamber (70) from a valve chamber (44), an electrically operatable actuator assembly (38) for connecting the valve chamber (44) to and separating the valve chamber (44) from a low-pressure fuel return (46), wherein the head (80) in the shut position of the intermediate valve member (78), by way of a side that faces the intermediate part (66), across a first sealing face (111.2) that runs at a first radial spacing (r1) about the shaft (76) or the guiding recess (74), while forming a first annular sealing face (121) closed in the encircling direction, and across a second sealing face (112.2) that runs at a second radial spacing (r2) about the shaft (76) or the guiding recess (74), while forming a second annular sealing face (122) closed in the encircling direction, bears on the intermediate valve seat (82), wherein the first radial spacing (r1) is larger than the second radial spacing (r2).

20. The fuel injection valve (10) as claimed in claim 19, wherein the high-pressure fuel supply port (86) in the intermediate part (66) runs in such a manner that the high-pressure fuel supply port (86) in the shut position of the intermediate valve member (78) opens into an annular gap space (118) which in the shut position of the intermediate valve member (78) is configured between the intermediate part (66) and the head (80) and is radially delimited by the first and the second annular sealing face (121, 122).

21. The fuel injection valve (10) as claimed in claim 20, wherein the shaft (76) is guided in a sliding fit in the guiding recess (74) of the intermediate part (66), wherein a clearance of at least 10 .Math.m, preferably between 20 .Math.m and 50 .Math.m, is present in the radial direction between the shaft (76) and the guiding recess (74).

22. The fuel injection valve (10) as claimed in claim 20, wherein the intermediate valve member (78) has a supply port (96) which by way of a first end opens into the valve chamber (44) and by way of a second end opens toward an external side of the intermediate valve member (78) in such a manner that the second end in the shut position of the intermediate valve member (78) is disposed at a radially smaller spacing from the shaft (76) than the second annular sealing face (122).

23. The fuel injection valve (10) as claimed in claim 20, wherein the shaft (76) has at least one encircling annular protrusion (761), the shaft (76) being guided in the guiding recess (74) by way of said at least one encircling annular protrusion (761).

24. The fuel injection valve (10) as claimed in claim 23, wherein the shaft (76) has two annular protrusions (761, 762) that are mutually spaced apart in the longitudinal direction of the shaft (76).

25. The fuel injection valve (10) as claimed in claim 24, wherein the shaft (76) is guided in the guiding recess (74) of the intermediate part (66) in such a manner that a clearance of at least 50 .Math.m, preferably between 70 .Math.m and 100 .Math.m, is present in the radial direction between the shaft (76) and the guiding recess (74).

26. The fuel injection valve (10) as claimed in claim 19, wherein the intermediate valve member (78) has a valve chamber passage (441) which is connected to the valve chamber (44) and in the intermediate valve member (78) runs in such a manner that the valve chamber passage (441) in the shut position of the intermediate valve member (78) opens into an annular gap space (118) which in the shut position of the intermediate valve member (78) is configured between the intermediate part (66) and the head (80) and is radially delimited by the first and the second annular sealing face (121, 122).

27. The fuel injection valve (10) as claimed in claim 26, wherein the fuel injection valve has an annular chamber (120) which in the shut position of the intermediate valve member (78) is delimited by the intermediate part (66), the shaft (76) and the head (80) and into which the high-pressure fuel supply port (86) opens.

28. The fuel injection valve (10) as claimed in claim 26, wherein the valve chamber passage (441) in the head (80) has a bore (441.1) which is parallel to the longitudinal axis (L) or inclined in relation to the longitudinal axis (L) and in the shut position of the intermediate valve member (78) opens into the annular gap space (118).

29. The fuel injection valve (10) as claimed in claim 19, wherein a first annular sealing bead (111), having a first end face (111.1) which forms the first sealing face (111.2), is configured on that side of the head (80) that faces the intermediate part (66) or on that side of the intermediate part (66) that faces the head (80).

30. The fuel injection valve (10) as claimed in claim 19, wherein a second annular sealing bead (112), having a second end face (112.1) which forms the second sealing face (112.2), is configured on that side of the head (80) that faces the intermediate part (66) or on that side of the intermediate part (66) that faces the head (80).

31. The fuel injection valve (10) as claimed in claim 19, wherein the intermediate part (66) on the side that faces the head (80) has at least one gradation (125), and the head (80) on the side that faces the intermediate part (66) has at least one gradation (127), wherein in the shut position of the intermediate valve member (78) mutually offset edges (125.1, 127.1) of the gradations (125, 127) of the intermediate part (66) and of the head (80) radially delimit in each case the first and/or the second annular sealing face (121, 122).

32. The fuel injection valve (10) as claimed in claim 31, wherein a gradation (125) of the intermediate part (66) forms an inner annular chamber (126) which in the shut position of the intermediate valve member (78) is delimited by the intermediate part (66), the shaft (76) and the head (80).

33. The fuel injection valve (10) as claimed in claim 1, wherein the shaft (76) is permanently guided in the guiding recess (74) of the intermediate part (66).

Description

LIST OF THE FIGURES

[0098] Embodiments of the invention will be explained in more detail by means of the following figures and the associated description. In the schematic figures:

[0099] FIG. 1 shows an illustration of a fuel injection valve from the prior art in a longitudinal section;

[0100] FIG. 2 shows the part of the fuel injection valve from the prior art that in FIG. 1 is bordered by a rectangle denoted with II, so as to be enlarged in comparison to FIG. 1;

[0101] FIG. 3 shows a fragment of a first embodiment of a fuel injection valve according to the invention in a longitudinal section, wherein the fragment represents a region of the fuel injection valve that corresponds to the rectangle denoted with III in FIG. 2;

[0102] FIG. 4 shows a fragment of a second embodiment of a fuel injection valve according to the invention in a longitudinal section, wherein the fragment represents a region of the fuel injection valve that corresponds to the rectangle denoted with III in FIG. 2;

[0103] FIG. 5a shows a fragment of a third embodiment of a fuel injection valve according to the invention in a longitudinal section, wherein the fragment represents a region of the fuel injection valve that corresponds to the rectangle denoted with III in FIG. 2;

[0104] FIG. 5b shows a fragment of a horizontal sectional illustration of a further embodiment of a fuel injection valve according to the invention;

[0105] FIG. 6 shows a fragment of a fourth embodiment of a fuel injection valve according to the invention in a longitudinal section, wherein the fragment represents a region of the fuel injection valve that corresponds to the rectangle denoted with III in FIG. 2; and

[0106] FIG. 7 shows a fragment of a fifth embodiment of a fuel injection valve according to the invention in a longitudinal section, wherein the fragment represents a region of the fuel injection valve that corresponds to the rectangle denoted with III in FIG. 2.

DESCRIPTION OF EXEMPLARY EMBODIMENTS

[0107] The same reference signs are used for equivalent parts of the embodiments in the description of the figures.

[0108] FIG. 1 shows a fuel injection valve 10' according to WO 2016/041739 A1 for intermittently injecting fuel into a combustion chamber of an internal combustion engine. The fuel here is highly pressurized, for example to a pressure of up to 2000 bar or more.

[0109] The fuel injection valve 10' has a housing 12' which defines a longitudinal axis L and has a housing body 14', a nozzle body 16' on which an injection valve seat 18' is configured, and an actuator receptacle body 20' which is disposed between the housing body 14' and the nozzle body 16'. A union nut 22' that is supported on the nozzle body 16' receives the actuator receptacle body 20' and by way of a thread is fitted to the housing body 14'. The housing body 14' and the actuator receptacle body 20', as well as the latter and the nozzle body 16', bear on one another on the end sides, are mutually compressed in a sealing manner by means of the union nut 22', and are aligned to one another in the direction of the longitudinal axis L.

[0110] The external shape of the housing 12', in a manner known, is at least approximately circular-cylindrical.

[0111] A high-pressure fuel inlet 24' is disposed on the end side of the housing body 14' that faces away from the nozzle body 16', a high-pressure chamber 26' from the high-pressure fuel inlet 24' running in the interior of the housing 12' - through the housing body 14', the actuator receptacle body 20' and the nozzle body 16' -up to the injection valve seat 18'. The high-pressure fuel inlet 24' is formed by a valve carrier 28' which carries a check valve 30' and a basket-type perforated filter 32' for retaining potential foreign particles in the fuel. The disk-shaped valve member of the check valve 30', which interacts with a valve seat configured on the valve carrier 28', has a bypass bore.

[0112] The check valve 30', in a manner known, allows fuel supplied by way of a high-pressure supply line to flow practically unimpeded into the high-pressure chamber 26' , but does prevent the outflow of fuel from the high-pressure chamber 26' into the high-pressure supply line, with the exception of the path by way of the bypass.

[0113] The construction and the functional mode of the module configured as a cartridge, having the valve carrier 28', the check valve 30' and the perforated filter 32', are disclosed in document WO 2014/131497 A1. The high-pressure fuel inlet 24' and the valve carrier 28' having the check valve 30' and the perforated filter 32' can also be configured as disclosed in document WO 2013/117311 A1. A potential embodiment of the high-pressure fuel inlet 24' and of the check valve 30', as well as a tubular filter instead of the perforated filter 32', is known from document WO 2009/033304 A1. The corresponding disclosure of the documents mentioned above is considered to be incorporated in the present disclosure by reference.

[0114] Adjoining the valve carrier 28', the high-pressure chamber 26' has a discrete storage chamber 34' which is configured on the housing body 14' and at the other side is connected to the injection valve seat 18' by way of a flow duct 36' of the high-pressure chamber 26'.

[0115] The dimensions and the functional mode of the discrete storage chamber 34', conjointly with the check valve 30' having the bypass, are disclosed in document WO 2007/009279 A1; the corresponding disclosure is considered to be incorporated in the present disclosure by reference.

[0116] Instead of the check valve 30', a stationary, immovable throttle may also be provided in specific embodiments.

[0117] An electrically activated actuator assembly 38' is received in a manner known in a recess of the actuator receptacle body 20', said actuator assembly 38' which by way of the tappet 40' thereof that is spring-loaded in one direction and in the other direction is movable by means of a solenoid of the actuator assembly 38' is specified for closing a low-pressure outlet 42', so as to separate a valve chamber 44' from a low-pressure fuel return 46' (see FIG. 2), and for releasing the low-pressure outlet 42', so as to connect the valve chamber 44' and the low-pressure fuel return 46' to one another. The longitudinal axis, denoted with 48', of the tappet 40' and thus of the actuator assembly 38' runs so as to be parallel and eccentric to the longitudinal axis L.

[0118] A duct 52' in which the electric control line for controlling the actuator assembly 38' is received runs from an electric connector 50' through the housing body 14' to the actuator assembly 38', said duct 52' running so as to be parallel to the discrete storage chamber 34' disposed so as to be eccentric in terms of the longitudinal axis L of the housing 12' and thus of the fuel injection valve 10'.

[0119] The tappet 40' penetrates the base of the cup-shaped actuator receptacle body 20' that forms a guide element for the tappet 40'. The tappet 40' has guide wings which project in the radial direction and by way of which said tappet 40' is guided so as to be displaceable in a sliding manner, parallel to the longitudinal direction L, on the guide element. The guide wings form passages running in the longitudinal direction L, by way of which passages the fuel can flow from the low-pressure outlet 42' to the low-pressure fuel return 46'.

[0120] FIG. 2 shows an enlarged fragment of the fuel injection valve of FIG. 1 in the region of the rectangle denoted with II.

[0121] The conical injection valve seat 18', which by way of the flow duct 36' is connected directly to the storage chamber 34' and thus to the high-pressure fuel inlet 24', is integrally molded on the nozzle body 16'.

[0122] When viewed in the flow direction of the fuel, injection openings 54', by way of which, in the event of an injection valve member 56' being lifted from the injection valve seat 18', the very highly pressurized fuel is injected into the combustion chamber of the internal combustion engine, are configured in a manner known in a semi-spherical free end region of the nozzle body 16' downstream of the injection valve seat 18'.

[0123] The injection valve member 56' is configured in the shape of a needle and interacts with the injection valve seat 18'. The injection valve member 56' is guided so as to be movable in the direction of the longitudinal axis L in a guide bore 57' in the nozzle body, said guide bore 57' being concentric with the longitudinal axis L and associated with the high-pressure chamber 26', wherein the flow of fuel to the injection valve seat 18' and to the injection openings 54' with minor losses is made possible by recesses on the injection valve member 56', said recesses running in the longitudinal direction and in the radial direction being open toward the outside.

[0124] The interior space 58' of the nozzle body 16', which is associated with the high-pressure chamber 26', is configured upstream of this guide bore 57', so as to widen twofold toward the actuator receptacle body 20', wherein the portion of the interior space 58' which, so as to be approximately longitudinally centric to the nozzle body 16', runs up to the end side of the latter that faces the actuator receptacle body 20' defines a portion 60' of the nozzle body 16' which has a constant cross section and is circular-cylindrical on the inside.

[0125] A support ring, on which a compression spring 62' by way of one end thereof is supported, is integrally molded on the injection valve member 56' between this portion 60' and the guide bore 57'. The compression spring 62', by way of the other end thereof, on the end side is supported on a guide sleeve 64'' that forms a guide part 64'. The compression spring 62' impinges the injection valve member 56' with a closing force acting in the direction toward the injection valve seat 18'. On the other hand, the compression spring 62' holds the guide part 64', or the guide sleeve 64'', respectively, by way of the end side thereof that faces away from the compression spring 62', so as to bear in a sealing manner on an intermediate part 66'. The guide part 64' can be configured in a form other than that of a sleeve, for example as a cuboid or an annular body.

[0126] A dual-action control piston 68', which is integrally molded on the injection valve member 56', is guided in a tight sliding fit of approx. 3 .Math.m to 5 .Math.m in the guide part 64', or in the guide sleeve 64'', respectively, so as to be displaceable in the direction of the longitudinal axis L. The control piston 68', the guide part 64', or the guide sleeve 64'', respectively, and the intermediate part 66' delimit a control chamber 70' in relation to the high-pressure chamber 26' . The intermediate part 66' is part of a hydraulic control device 72'.

[0127] FIG. 3 shows a fragment of a first embodiment of a fuel injection valve 10 according to the invention in a longitudinal section. The fragment represents a region of the fuel injection valve 10 that corresponds to the rectangle denoted with III in FIG. 2, wherein the specific design embodiment of this region of the first embodiment of the fuel injection valve 10 according to the invention differs from the fuel injection valve 10' according to WO 2016/041739 A1 shown in FIG. 2 in particular in terms of the hydraulic control device 72, this being described hereunder with reference to FIG. 3. The remaining region of the first embodiment of the fuel injection valve 10 outside the rectangle denoted with III corresponds substantially to the fuel injection valve 10' shown in FIGS. 1 and 2. This also applies in an analogous manner to the fragments of the further embodiments of the fuel injection valve 10 according to the invention, which are shown in FIGS. 4 to 7.

[0128] A circular-cylindrical guiding recess 74 runs through an intermediate part 66, from the planar end side that faces the control chamber 70 to the likewise planar end side that faces away from the control chamber 70. A shaft 76 of an intermediate valve member 78 which is configured in the shape of a mushroom is guided in said guiding recess 74. A head 80 of the intermediate valve member 78, which is configured so as to be integral to the shaft 76, is situated in the control chamber 70 and, by way of the side thereof that faces the intermediate part 66, interacts with the intermediate part 66, the planar end side thereof forming an annular intermediate valve seat 82.

[0129] The intermediate valve member 78, conjointly with the intermediate valve seat 82 configured on the intermediate part 66, forms an intermediate valve 83.

[0130] A first toroidal sealing bead 111 which has a first end face 111.1 that forms the first sealing face 111.2 and which runs at a first radial spacing r1 about the shaft 76 is configured on the side of the head 80 that faces the intermediate part 66. A second toroidal sealing bead 112 which has a second end face 112.1 that forms the second sealing face 112.2 and which runs at a second radial spacing r2 about the shaft 76 is furthermore configured on the side of the head 80 that faces the intermediate part 66. As is shown in FIG. 3, the intermediate valve member 78 is situated in the shut position in which the head 80, by way of the side thereof that faces the intermediate part 66, across the first sealing face 111.2, while forming a first annular sealing face 121 inherently closed in the encircling direction, and across the second sealing face 112.2, while forming a second annular sealing face 122 inherently closed in the encircling direction, bears on the intermediate valve seat 82. The first radial spacing r1 here is larger than the second radial spacing r2 from the shaft 76.

[0131] A high-pressure fuel supply port 86 which is connected to the high-pressure chamber 26 and comprises a horizontal bore 861 and a vertical bore 862 runs in the intermediate part 66. The vertical bore 862 in the shut position of the intermediate valve member 78 opens into an annular gap space 118 which is configured between the intermediate part 66 and the head 80 and is radially delimited by the first and the second annular sealing face 121, 122. As can be seen in FIG. 3, a plurality of high-pressure fuel supply ports 86 can be provided. A second, optional high-pressure fuel supply port 86 is thus shown with dashed lines in the region of the intermediate part 66 that is on the right in FIG. 3.

[0132] A clearance of preferably at least 10 .Math.m is present in the radial direction between the shaft 76 and the guiding recess 74. However, the clearance may also be smaller, for example between 3 and 10 .Math.m. In further embodiments, the clearance may in each case be larger and have a value of, for example, between 20 .Math.m and 50 .Math.m. The second radial spacing r2 of the second annular sealing face 122 from the shaft 76 here is larger than the clearance (for example several 1/10 mm larger). By virtue of the high-pressure fuel supply port 86 in the shut position of the intermediate valve member 78 being sealed by the annular sealing faces 121, 122, the possibility of additional leakages into the valve chamber 44, generated as a result of the clearance between the shaft 76 and the guiding recess 74, is minimized or negligible. Moreover, it is apparent that the shaft 76 for this reason can be configured so as to be shorter along the longitudinal axis L in comparison to the prior art such as, for example, in the fuel injection valve of WO 2016/041739 A1. Furthermore, the intermediate part 66 can also be designed so as to be shorter in the direction of the longitudinal axis L, so that a more compact construction mode is made possible.

[0133] Despite the reliable sealing of the high-pressure fuel supply port 86 in the shut position of the intermediate valve member 78, the adhesion between the head 80 and the intermediate part 66 remains minor thanks to the sealing of the intermediate valve member 78 implemented by the two annular sealing faces 121, 122.

[0134] An intermediate element 98, through which an outlet bore 102 that tapers in a staged manner and at the one side by way of one end is connected to the guiding recess 74 and by way of another end forms the low-pressure outlet 42, is disposed above and adjoining the intermediate part 66 in FIG. 3. The outlet bore 102 is disposed so as to be eccentric in terms of the longitudinal axis L. In specific embodiments, the intermediate element 98 is configured so as to be integral to the intermediate part 66, i.e. as a single-piece intermediate part, in which the guiding recess is configured as a blind bore (see FIG. 5a, for example).

[0135] The length of the shaft 76 in the direction of the longitudinal axis L is sized in such a manner in comparison to the guiding recess 74 that a flow gap 100 between the end side of the shaft 76 that faces the outlet bore 102 and the intermediate element 98 remains in the shut position of the intermediate valve member 78.

[0136] The intermediate valve member 78 has a supply port 96 which by way of a first end opens into a blind bore 92 that runs through the shaft 76 and is part of the valve chamber 44, and by way of a second end at the external side of the intermediate valve member 78 opens toward a line on which the shaft 76 adjoins the head 80.

[0137] In the shut position of the intermediate valve member 78, an inner annular chamber 117 is configured between the intermediate part 66 and the head 80, which inner annular chamber 117 is adjacent to the shaft 76 and the second annular sealing face 122, wherein the supply port 96 in the shut position of the intermediate valve member 78 connects the inner annular chamber 117 to the blind bore 92, or to the valve chamber 44, respectively.

[0138] The blind bore 92 runs through the shaft 76 and protrudes into the head 80. The supply port 96 is configured as a bore which is inclined in relation to the longitudinal axis L. However, in further embodiments, the supply port 96 can also be configured as a horizontal bore.

[0139] A throttle passage 90, which runs from the end side of the head 80 that faces the control piston 68 to the blind bore 92 and connects the valve chamber 44 to the control chamber 70 is configured on the head 80. The supply port 96 has a diameter which is larger than that of the throttle passage 90. While not shown in this way in the schematic FIG. 3, the diameter of the supply port 96 can also be larger than the smallest diameter of the graduated outlet bore 102.

[0140] The intermediate valve member 78 in the open position, by way of the supply port 96, releases a second connection between the high-pressure fuel supply port 86 and the valve chamber 44, so that the valve chamber 44, or the blind bore 92, respectively, can be flooded with fuel. Already in the event of a small movement of the intermediate valve member 78 away from the intermediate part 66, fuel from the high-pressure fuel supply port 86 can flow through the supply port 96 into the blind bore 92 by way of the annular gap space 118 and the inner annular chamber 117, thus supporting the opening movement of the intermediate valve member 78. In the shut position of the intermediate valve member 78, the second connection between the high-pressure fuel supply port 86 and the valve chamber 44, or the blind bore 92, respectively, is interrupted by virtue of the second sealing bead 112, or the second sealing face 112.2, respectively.

[0141] The second connection is particularly advantageous for the intermediate valve member according to the invention, which is configured in the shape of a mushroom, because the above-described rapid filling of the blind bore of the intermediate valve member for a rapid opening movement of the intermediate valve member can be achieved therewith.

[0142] The control piston 68 on the side thereof that faces the head 80 has a cam-type protrusion 561 which has a preferably circular cross section and serves as a stroke delimitation for the stroke of the injection valve member 56 and can thereby bear on the intermediate valve member 78. The cam-type protrusion 561 has a recess 5611 which extends perpendicularly to the drawing plane and by way of which fuel from the control chamber 70 can flow into the valve chamber 44, or into the blind bore 92, respectively, by way of the throttle passage 90, even when the cam-type protrusion 561 bears on the intermediate valve member 78. Therefore, the recess 5611 is configured so as to be open in the radial direction (or as shown in FIG. 3 in the direction perpendicular to the drawing plane), toward the control chamber 70.

[0143] A detent shoulder 84, which delimits the opening stroke of the intermediate valve member 78, is configured on the guide sleeve 641 so as to be spaced apart from the intermediate part 66, said guide sleeve 641 forming the guide part 64. In order to enable the fuel to flow with ideally minor losses from a high-pressure fuel supply port 86 into the control chamber 70, a sufficiently large gap is present radially on the outside, between the head 80 and the guide sleeve 641, and the head 80 on the side thereof that faces the detent shoulder 84 has wedge-type flow grooves which, when the intermediate valve member 78 is situated in the open position and the head 80 bears on the detent shoulder 84, allow the fuel to flow from the gap to the control piston 68 with minor losses. In specific embodiments, the guide part 64, or the guide sleeve 641, respectively, can be configured so as to be integral to the intermediate part 66, i.e. as a single-piece component.

[0144] The intermediate valve 83 in the shut position of the intermediate valve member 78 has the task of separating the high-pressure fuel supply port 86 from the control chamber 70 and from the valve chamber 44 and, in the open position of the intermediate valve member 78, i.e. when the head 80 is lifted from the intermediate valve seat 82, of releasing the connection between the high-pressure fuel supply port 86 and the control chamber 70 and the valve chamber 44.

[0145] The intermediate element 98 is disposed in the nozzle body 16 and by way of the planar end side thereof that faces away from the intermediate part 66 bears on the corresponding end side of the actuator receptacle body 20.

[0146] In order for the intermediate element 98 to be correctly positioned relative to the actuator receptacle body 20, and thus relative to the actuator assembly 38, the intermediate element 98 as well as the actuator receptacle body 20 have mutually aligned, mutually facing, positioning bores 106 in the manner of blind bores into which a common positioning pin 104 is inserted.

[0147] In order for the position of the intermediate part 66 in relation to the intermediate element 98 to be established, mutually aligned further positioning bores in the manner of blind bores are placed on these components, a positioning pin 1041 likewise being inserted into said positioning bores. These positioning bores lie outside the drawing plane of FIG. 3, the positioning pin 1041 for this reason being shown in dashed lines.

[0148] At least two positioning bores are typically placed on each component, said positioning bores aligning in each case in pairs with positioning bores of adjacent components so that two adjacent components are held in position relative to one another by at least two positioning pins.

[0149] FIG. 4 shows a fragment of a second embodiment of a fuel injection valve 10 according to the invention in a longitudinal section. The fragment represents a region of the fuel injection valve 10 which corresponds to the rectangle denoted with III in FIG. 2, wherein the specific design embodiment of this region of the second embodiment of the fuel injection valve 10 according to the invention differs from the fuel injection valve 10' according to WO 2016/041739 A1, shown in FIG. 2, in particular in terms of the hydraulic control device 72.

[0150] The second embodiment of the fuel injection valve according to the invention, shown in FIG. 4, corresponds substantially to the first embodiment shown in FIG. 3, with the difference that the first and the second sealing bead 111, 112 are not configured on the head 80 but on the intermediate part 66. The first toroidal sealing bead 111, which runs at a first radial spacing r1 about the guiding recess 74, is configured on the side of the intermediate part 66 that faces the head 80, having a first end face 111.1 which forms the first sealing face 111.2. The second toroidal sealing bead 112, which runs at a second radial spacing r2 about the guiding recess 74, is also configured on the side of the intermediate part 66 that faces the head 80, having a second end face 112.1 which forms the second sealing face 112.2. At the same time, the first and the second end face 111.1, 112.1 form the intermediate valve seat 82 which in the shut position of the intermediate valve member 78 interacts in a sealing manner with the planar face of the head 80 that lies opposite the first and the second sealing bead 111, 112. Therefore, the intermediate valve seat 82 comprises the first end face 111.1 of the first sealing bead 111 as well as the second end face 112.1 of the second sealing bead 112.

[0151] As shown in FIG. 4, the intermediate valve member 78 is situated in the shut position in which the head 80 by way of the side thereof that faces the intermediate part 66 across the first sealing face 111.2, while forming a first annular sealing face 121 inherently closed in the encircling direction, and across the second sealing face 112.2, while forming a second annular sealing face 122 inherently closed in the encircling direction, bears on the intermediate valve seat 82. The first radial spacing r1 here is again larger than the second radial spacing r2 from the guiding recess 74.

[0152] The features of the high-pressure fuel supply port 86 and the effects of the sealing of the high-pressure fuel supply port 86 described in FIG. 3, as well as the features pertaining to the clearance between the shaft 76 and the guiding recess 74, can be applied in an analogous manner to the second embodiment shown in FIG. 4. In particular, the high-pressure fuel supply port 86, which runs in the intermediate part 66 and is connected to the high-pressure chamber 26, in the shut position of the intermediate valve member 78 opens in an annular gap space 118 which is configured between the intermediate part 66 and the head 80 and is radially delimited by the first and the second annular sealing face 121, 122. As is apparent in FIG. 4, two diametrically opposite, mutually corresponding high-pressure fuel supply ports 86 are configured in the intermediate part 66. Further high-pressure fuel supply ports can be configured in the intermediate part 66, for example on a plane which is vertical to the drawing plane and runs through the longitudinal axis L.

[0153] As is apparent in FIG. 4, the shaft 76 has an undercut which adjoins the head 80 and forms an internal annular chamber 108 that runs about the shaft 76 and in the radial direction is delimited by the shaft 76 and the intermediate part 66. An inner annular chamber 117 adjoins the internal annular chamber 108, said inner annular chamber 117 being adjacent to the shaft 76 and the second annular sealing face 122. In one embodiment, a further supply port (not shown in FIG. 4), configured as a horizontal bore, for example, can be disposed in the shaft 76, said further supply port connecting the blind bore 92 to the internal annular chamber 108 and being conceived for facilitating the opening procedure of the intermediate valve member 78.

[0154] In the embodiment shown in FIG. 4, the clearance between the shaft 76 and the guiding recess 74 serves as the passage of the second connection, which between the high-pressure fuel supply port 86 and the valve chamber 44 is released by the intermediate valve member 78 in the open position. Should the intermediate valve member 78, as is shown in FIG. 4, not have any supply port as part of the second connection (as is the case in the supply port 96 in FIG. 3), the clearance between the shaft 76 and the guiding recess 74 is thus preferably larger than in an embodiment with a supply port, i.e. for example larger than the clearance between the shaft and the guiding recess in FIG. 3. In the shut position of the intermediate valve member 78, the second sealing bead 112, or the second annular sealing face 122, respectively, interrupts the second connection between the high-pressure fuel supply port 86 and the valve chamber 44.

[0155] It is obvious to the person skilled in the art that, alternatively or additionally to the supply port, the clearance between the shaft and the guiding recess also in FIG. 3 also can serve as part of the second connection. In an analogous manner, alternatively or additionally to the clearance between the shaft and the guiding recess, a supply port can also serve as part of the second connection in FIG. 4.

[0156] Furthermore, a compression spring 63 is disposed between the control piston 68 and the head 80 so as to be centered about the longitudinal axis L. The compression spring 63 serves for keeping the intermediate valve member 78 in the shut position when the low-pressure outlet 42 is released by the lifted tappet 40, in that the head 80 is pressed against the intermediate part 66, this being particularly effective at the low system pressure of approx. 200 to 300 bar when the engine is idling.

[0157] FIG. 5a shows a fragment of a third embodiment of an fuel injection valve 10 according to the invention in a longitudinal section. The fragment represents a region of the fuel injection valve 10 that corresponds to the rectangle denoted with III in FIG. 2, wherein the specific design embodiment of this region of the third embodiment of the fuel injection valve 10 according to the invention differs from the fuel injection valve 10' according to WO 2016/041739 A1, shown in FIG. 2, in particular in terms of the hydraulic control device 72.

[0158] In a manner similar to the embodiment of the fuel injection valve shown in FIG. 3, the head 80 of the intermediate valve member 78 on the side of the head 80 that faces the intermediate part 66 has a first sealing bead 111 which at a first radial spacing r1 runs about the shaft 76, having a first end face 111.1 which forms the first sealing face 111.2.

[0159] As opposed to the embodiments of the fuel injection valve shown in FIGS. 3 and 4 however, the second sealing face is not formed by a sealing bead but by a gradation 127 on the side of the head 80 that in the direction of the longitudinal axis L faces the intermediate part 66, said gradation 127 running about the shaft 76 at a second radial spacing r2. The intermediate part 66 on the side that faces the head 80 likewise has a gradation 125 which encircles the guiding recess 74, wherein the mutually offset edges 125.1 and 127.1 of the gradations 125 and 127 in the shut position of the intermediate valve member 78 shown radially delimit the second annular sealing face 122.

[0160] The gradation 127 of the head 80 is formed by an undercut which at the same time configures the annular gap space 118 into which the high-pressure fuel supply port 86 opens. The gradation 127 has a horizontal face which forms the second sealing face 112.2 and in the shut position of the intermediate valve member 78, while forming the second annular sealing face 122 inherently closed in the encircling direction, bears in a sealing manner on a face 781 of the intermediate part 66 that in the direction of the longitudinal axis L faces the head 80. The face 781 of the intermediate part 66 that in that in the direction of the longitudinal axis L faces the head 80, therefore forms the intermediate valve seat 82 on which, in the shut position of the intermediate valve member 78, the first sealing face 111.2 of the first sealing bead 111, while forming a first annular sealing face 121 inherently closed in the encircling direction, also bears in a sealing manner.

[0161] The gradation 125 of the intermediate part 66 is formed by an annular recess 126 which in the encircling direction has a rectangular cross-sectional profile. In further variants, the annular recess 126 in the encircling direction can have a chamfered cross-sectional profile or a curved cross-sectional profile. The annular recess 126 forms an inner annular chamber which in the shut position of the intermediate valve member 78 is delimited by the intermediate part 66, the shaft 76 and the head 80.

[0162] It can furthermore be seen in FIG. 5a that the outlet bore 102 runs in the intermediate part 66. The intermediate part 66 is received in a receptacle recess 151 in the manner of a blind bore of an intermediate body 15, the latter serving as an actuator receptacle body 20 of the actuator assembly 38. As opposed to the embodiments of FIGS. 3 and 4, a separate intermediate part and a separate intermediate element are therefore not provided, but these two components are integrally configured as a single-piece intermediate part 66. The outlet bore 102 has an inclined bore portion which connects a guiding recess 74 in the manner of a blind bore of the intermediate part 66 to the eccentrically disposed low-pressure outlet 42.

[0163] The shaft 76 as well as the head 80 are able to be received in the guiding recess 74 in the manner of a blind bore of the intermediate part 66. The guiding recess 74 in the region thereof that faces the control piston 68 is extended into a head space 128 in which the head 80 is able to be received. The end side 84 of the guide sleeve 641 that faces the intermediate part 66 and adjoins the latter serves as a detent shoulder for the head 80 in the open position of the intermediate valve member 78.

[0164] As in FIGS. 3 or 4, a separate intermediate element and a separate intermediate part could however also be provided instead of the single-piece intermediate part 66. It is also conceivable for the intermediate part and the guide sleeve to be configured as a single piece. Furthermore, it is also conceivable for the intermediate element and the intermediate part, shown in FIGS. 3 or 4, to be configured integrally as a single-piece component.

[0165] The shaft 76 has two annular protrusions 761 and 762 which are mutually spaced apart in the longitudinal direction L of the shaft 76 and encircle the shaft 76 (in part highlighted as dashed lines in FIG. 5a), by way of which the shaft 76 is guided in the guiding recess 74. Two throttle pathways which are disposed in series along the longitudinal axis L and encircle the shaft 76 in the longitudinal direction L are configured by the annular protrusions 761 and 762. As a result, the formation of turbulences and a turbulent flow of the fluid flowing through the intermediate space between the shaft 76 and the guiding recess 74 is promoted. A clearance of at least 50 .Math.m is present in the radial direction between the shaft 76 and the guiding recess 74. In further embodiments, the clearance can in each case have a value between 70 .Math.m and 100 .Math.m. By virtue of the radial clearance, the radial extent of the second annular sealing face 122 can vary depending on the current radial position of the shaft 76 in the guiding recess 74. In order for the sealing function of the intermediate valve to be guaranteed, the maximum radial extent of the second annular sealing face 122 here is larger than the clearance.

[0166] In the embodiment shown in FIG. 5a, the clearance between the shaft 76 and the guiding recess 74 serves as the passage of the second connection, which between the high-pressure fuel supply port 86 and the valve chamber 44 is released by the intermediate valve member 78 in the open position. In the shut position of the intermediate valve member 78, the second annular sealing face 122 interrupts the second connection between the high-pressure fuel supply port 86 and the valve chamber 44.

[0167] FIG. 5b shows a fragment of a horizontal cross-sectional illustration of a further embodiment of a fuel injection valve according to the invention, wherein this embodiment of the fuel injection valve is embodied so as to correspond to the embodiment shown in FIG. 5a. For this reason, the line A-A along which the cross section shown in FIG. 5b was taken is shown in FIG. 5a. Therefore, FIG. 5b shows an embodiment of the embodiment of a fuel injection valve shown in FIG. 5a. As can be seen in FIG. 5b, the second annular protrusion 762 in the encircling direction has three chamfers 762.1, 762.2 and 762.3 by which an intermediate space 119 (or three mutually corresponding intermediate spaces, respectively), is/are formed between the shaft 76, or the annular protrusion 762, respectively, and the guiding recess 74. While not visible in FIG. 5b, the first annular protrusion 761 in the encircling direction also has corresponding chamfers. As a result of the chamfers 762.1-3 of the second annular protrusion 762 (and of the chamfers of the first annular protrusion), a pathway, formed by the intermediate space 119 between the chamfers and the guiding recess 74, is provided, said pathway serving as a passage of the second connection. Furthermore, by virtue of the chamfers 762.1-3 (and of the chamfers of the first annular protrusion) and of the pathway of the second connection provided as a result, the clearance between the shaft 76 and the guiding recess 74 can be kept smaller than in the embodiment described in the context of FIG. 5a, this leading to improved centering of the shaft. The three chamfers 762.1-3 (and the chamfers of the first annular protrusion) are mutually disposed at an angle of 120°. However, other arrangements are also conceivable; embodiments having in each case one chamfer per annular protrusion or two chamfers per annular protrusion, or a larger number of chamfers, are in particular conceivable.

[0168] Furthermore, the shaft without annular protrusions, i.e. in specific embodiments of the embodiments of the fuel injection valve shown in FIGS. 3 or 4, for example, in the circumferential direction can also have at least one chamfer, or two or three chamfers, such that a pathway for the second connection is again formed by the intermediate space between the chamfer or the chamfers and the guiding recess.

[0169] FIG. 6 shows a fragment of a fourth embodiment of a fuel injection valve 10 according to the invention in a longitudinal section. The fragment represents a region of the fuel injection valve 10 that corresponds to the rectangle denoted with III in FIG. 2, wherein the specific design embodiment of this region of the fourth embodiment of the fuel injection valve 10 according to the invention differs from the fuel injection valve 10' according to WO 2016/041739 A1, shown in FIG. 2, in particular in terms of the hydraulic control device 72.

[0170] The intermediate valve member 78 has a valve chamber passage 441 which is connected to the valve chamber 44 and comprises a bore 441.1, parallel to the longitudinal axis L, and a horizontal bore 441.2. The valve chamber passage 441 connects a blind bore 92 of the intermediate valve member 78, connected to the valve chamber 44, to an annular gap space 118 which in the shut position of the intermediate valve member 78 shown is configured between the intermediate part 66 and the head 80 and is radially delimited by the first and the second annular sealing face 121, 122. The bore 441.1, which is parallel to the longitudinal axis L, by way of a first end opens into the annular gap space 118 and by way of a second end opens into the horizontal bore 441.2. The horizontal bore 441.2 in turn, by way of a first end, opens into the blind bore 92. As can be seen in FIG. 5a, a second end of the horizontal bore 441.2 is closed by a stopper 441.3. In one variant, the intermediate valve member 78, or the head 80, respectively, has a further valve chamber passage 441 which is shown in dashed lines in FIG. 5a. The horizontal bore 441.2, shown in dashed lines, of the further valve chamber passage 441 is not separately closed by a stopper because the horizontal bore 441.2, shown in dashed lines, can be bored conjointly with the horizontal bore 441.2, the latter shown on the left with solid lines.

[0171] The intermediate valve member 78 in the open position, by way of the bore 441.1, releases a second connection between the high-pressure fuel supply port 86 and the blind bore 92, or the valve chamber 44, respectively, so that the blind bore 92, or the valve chamber 44, respectively, can be flooded with fuel. In the shut position of the intermediate valve member 78, the second annular sealing face 122 interrupts the second connection between the high-pressure fuel supply port 86 and the valve chamber 44.

[0172] As opposed to the embodiments shown in FIGS. 3 to 5, the high-pressure fuel supply port 86 according to the embodiment shown in FIG. 6 opens into an annular chamber 120 which in the shut position of the intermediate valve member 78 is delimited by the intermediate part 66, the shaft 76 and the head 80. In the shut position of the intermediate valve member 78, the annular chamber 120 adjoins the second annular sealing face 122 and is radially disposed so as to be closer to the shaft 76 than the second annular sealing face 122.

[0173] The annular chamber 120 has an internal annular chamber 108 which runs about the shaft 76, in the radial direction is delimited by the shaft 76 and the intermediate part 66 and is recessed on the shaft 76 per se. The high-pressure fuel supply port 86 opens into the internal annular chamber 108. The annular chamber 120 furthermore has an annular gap space 117 which adjoins the internal annular chamber 108 and in the shut position of the intermediate valve member 78 is formed by an encircling gap between the intermediate part 66 and the head 80 and is radially adjacent to the second annular sealing face 122. The internal annular chamber 108 is formed by an encircling annular groove which in the radial direction is open toward the outside and has a trapezoidal cross section, wherein the obliquely running side faces away from the head 80.

[0174] The shaft 76 is guided in a tight sliding fit of approx. 3 .Math.m to 10 .Math.m in the guiding recess 74. The diameter of the vertical bore 441.1 of the valve chamber passage 441 is larger than the diameter of the throttle passage 90 and enables the blind bore 92 and the valve chamber 44 to be rapidly flooded when the intermediate valve member 78 moves away from the shut position.

[0175] In one variant, a secondary passage 97 is configured on the intermediate part 66, as is shown in dashed lines in FIG. 6. The secondary passage 97 connects the high-pressure chamber 26 to the valve chamber 44 and facilitates the opening procedure of the intermediate valve member 78 when the tappet 40 closes the low-pressure outlet 42 and separates the valve chamber 44 from the low-pressure fuel return 46.

[0176] FIG. 7 shows a fragment of a fifth embodiment of a fuel injection valve 10 according to the invention in a longitudinal section. The fragment represents a region of the fuel injection valve 10 that corresponds to the rectangle denoted with III in FIG. 2, wherein the specific design embodiment of this region of the fifth embodiment of the fuel injection valve 10 according to the invention differs from the fuel injection valve 10' according to WO 2016/041739 A1, shown in FIG. 2, in particular in terms of the hydraulic control device 72.

[0177] As opposed to the fourth embodiment shown in FIG. 6, the valve chamber passage 441 has a bore 441.1 which is inclined in relation to the longitudinal axis L. Thanks to the inclined bore 441.1 it is possible for the first sealing bead 111 to be disposed radially farther away from the shaft 76 in comparison to the fourth embodiment according to FIG. 6, without the stopper 441.3 having to be reduced in size. The valve chamber passage 441 by way of the inclined bore 441.1 opens into the annular gap space 118 which is delimited by the head 80, the intermediate part 66 and the first as well as the second annular sealing face 121, 122. As in the fourth embodiment shown in FIG. 6, the horizontal bore 441.2 by way of one end opens into the blind bore 92.

[0178] In comparison to the fourth embodiment shown in FIG. 6, the internal annular chamber 108 of the annular chamber 120 is furthermore delimited by a recess on the shaft 76 as well as by a recess on the intermediate part 66. An annular gap space 117 again adjoins the internal annular chamber 108, said annular gap space 117 in the shut position of the intermediate valve member 78 being formed by an encircling gap between the intermediate part 66 and the head 80 and being radially adjacent to the second annular sealing face 122.

[0179] An optional secondary passage 97 which is configured by a rectilinear, horizontal bore on the shaft 76 and via the annular chamber 120 connects the high-pressure chamber 26, or the high-pressure fuel supply port 86, respectively, to the blind bore 92, is shown in dashed lines.

[0180] In comparison to the fourth embodiment shown in FIG. 6, the first and the second sealing bead 111, 112 are configured so as to be longer in the longitudinal direction L so that the annular gap space 118 has a larger depth in the longitudinal direction L.

[0181] Furthermore, the intermediate part 66 is configured as a single-piece component in which the outlet bore 102 comprising an inclined bore runs in a manner similar to that of FIG. 5a. However, a separate intermediate element and a separate intermediate part, as in FIG. 6, could be provided instead of the single-piece intermediate part 66. However, it is also conceivable for the intermediate element and the intermediate part in FIG. 6 to be configured as an integral component in a single piece.

[0182] In a manner similar to that shown in FIG. 6, a further valve chamber passage can be provided, this being shown in dashed lines in the right-hand region of the head 80.

[0183] The shaft 76 is guided in a tight sliding fit of approx. 3 .Math.m to 10 .Math.m in the guiding recess 74. The diameter of the inclined bore 441.1 of the valve chamber passage 441 is larger than the diameter of the throttle passage 90 and enables the blind bore 92 and the valve chamber 44 to be rapidly flooded when the intermediate valve member 78 moves away from the shut position.

[0184] The intermediate valve member 78 in the open position, by way of the bore 441.1, releases a second connection between the high-pressure fuel supply port 86 and the blind bore 92, or the valve chamber 44, respectively, so that the blind bore 92, or the valve chamber 44, respectively, can be flooded with fuel. In the shut position of the intermediate valve member 78, the second annular sealing face 122 interrupts the second connection between the high-pressure fuel supply port 86 and the valve chamber 44.

[0185] Proceeding from the shut position of the intermediate valve 83 shown in the figures, for injecting the tappet 40 by means of the solenoid of the actuator assembly 38 is lifted from the intermediate element 98 or the intermediate part 66, as a result of which the low-pressure outlet 42 is released. This has the consequence that a larger quantity of fuel per unit of time flows out of the valve chamber 44 into the low-pressure fuel return 46 than can be replenished by a flow from the throttle passage 90 and the potentially present secondary passage 97 into the valve chamber 44. As a result, the pressure in the valve chamber 44 drops, this having the consequence that the intermediate valve member 78 by way of the resulting compressive force is pressed against the intermediate part 66 so as to hold the intermediate valve 83 securely closed, on the one hand, and the pressure in the control chamber 70 drops, on the other hand. This in turn has the consequence that, as a result of the effect of the dual-action control piston 68 counter to the force of the compression spring 62', the injection valve member 56 is lifted from the injection valve seat 18', as a result of which an injection of fuel into the combustion chamber of the internal combustion engine is started.

[0186] If this injection is to be terminated, the tappet 40 is brought to bear on the intermediate element 98 or the intermediate part 66, as a result of which the low-pressure outlet 42 is closed. By means of the fuel flowing in through the throttle passage 90 and the potentially present secondary passage 97, the pressure in the valve chamber 44 increases, this causing a movement of the intermediate valve member 78 away from the intermediate valve seat 82. This movement is further facilitated as soon as the intermediate valve member 78 has carried out a minimum opening movement, because the annular cross section open as a result rapidly becomes substantially larger than the cross section of the supply port 96 and the inner annular chamber 117 in the embodiment shown in FIG. 3, for example, is flooded. In embodiments in which the high-pressure fuel supply port 86 opens into the annular gap space 118, the high system pressure in the annular gap space 118 facilitates the opening movement of the intermediate valve member 78. If there is an increased clearance between the shaft 76 and the guiding recess 74, fuel flows into the valve chamber 44 during the opening movement of the intermediate valve member 78, this fuel being able to rapidly flood said valve chamber 44 as soon as the sealing action by the annular sealing faces 121, 122 is cancelled.

[0187] In embodiments in which the valve chamber passage 441 opens into the annular gap space 118, the valve chamber 44 can be rapidly flooded by fuel which flows into the valve chamber passage 441 when the head 80 is lifted from the shut position of the intermediate valve 78, so that the opening movement of the intermediate valve member 78 is facilitated.

[0188] As a result of the head 80 of the intermediate valve member 78 being lifted from the intermediate part 66, a large flow cross section from the high-pressure fuel supply port 86 into the control chamber 70 is likewise rapidly released, this leading to a rapid termination of the injection procedure in that the injection valve member 56 is rapidly moved toward the injection valve seat 18 and comes to bear on the latter.