Fuel injection valve for internal combustion engines

Abstract

The invention relates to a fuel injection valve (10) with a hydraulic control device (72) for controlling the axial movement of an injection valve member (56). A stem (76) of a mushroom-shaped intermediate valve part (78) of an intermediate valve (83) is guided in a guide recess (74) of an intermediate part (66). The intermediate valve member (78) releases a second connection (118, 117, 96) between a fuel high-pressure inlet (86) and a valve space (44) in an open position and interrupts the second connection (118, 117, 96) between the fuel high-pressure inlet (86) and the valve space (44) in a closed position. A head (80) of the intermediate valve member (80) abuts against an intermediate valve seat (82) on a first sealing surface (111.2) with a side facing the intermediate part (66) in the closed position of the intermediate valve member (78) and on a second sealing surface (112.2) in such a way that a first annular sealing surface (121) which is closed in itself in a circumferential direction is formed, which extends at a first radial spacing (r1) about the stem (76) or the guide recess (74), and a second annular sealing surface (122) which is closed in itself in a circumferential direction is formed, which extends at a second radial spacing (r2) about the stem (76) or the guide recess (74), wherein the first radial spacing (r1) is greater than the second radial spacing (r2).

Description

Technical Field

[0001] The present invention relates to a fuel injection valve for intermittently injecting fuel into the combustion chamber of an internal combustion engine. Background Technology

[0002] For example, document WO2016 / 041739A1 describes a fuel injection valve for intermittently injecting fuel into the combustion chamber of an internal combustion engine. This fuel injection valve has a hydraulic control device for controlling the axial movement of the injection valve member by changing the pressure in the control space. The intermediate valve of the hydraulic control device has a mushroom-shaped intermediate valve member, the rod of which is guided in a tight sliding fit within a guide gap extending through the intermediate member. The head of the intermediate valve member, with its sealing surface extending radially around the rod—in the closed position of the intermediate valve member—abuts against an annular intermediate valve seat constructed on the intermediate member. An annular space, defined by the intermediate member, the rod, and the head, and having an internal annular space extending around the rod, is permanently connected to a high-pressure fuel inlet constructed on the housing of the fuel injection valve via a high-pressure fuel inlet extending through the intermediate member. The intermediate valve, with its rod guided at the intermediate component under tight sliding fit, continuously separates the control space from the valve space, except for a precisely sized throttling through-hole constructed on the intermediate valve member, which permanently connects the control space and the valve space. In the closed position of the intermediate valve member, the intermediate valve separates the high-pressure fuel inlet and the annular space from the control space, and as the intermediate valve member moves out of the closed position, the connection between the annular space and the high-pressure fuel inlet and the control space is released through the intermediate valve. The valve space can be connected to and disconnected from the low-pressure fuel return section via an electrically actuated actuator assembly. To trigger the injection process, the valve space is connected to the low-pressure fuel return section via the actuator assembly, after which fuel flows from the control space into the valve space through the throttling through-hole in the intermediate valve member, and due to the resulting pressure drop in the control space, the injection valve member is lifted from the injection valve seat arranged on the housing.

[0003] Another fuel injection valve is described in document EP1991773B1. The control space and valve space are permanently interconnected by a precise throttling through-hole, while an intermediate valve permanently separates these two spaces. The throttling through-hole is arranged directly adjacent to the control space. The through-hole, which connects to the high-pressure space of the injection valve and leads into the control space, has a larger cross-section than the throttling through-hole and is controlled by the intermediate valve. Since the cross-section of the outflow portion from the valve space, controlled by an electrically driven actuator assembly, can also be significantly larger than the cross-section of the throttling through-hole, the opening movement of the injection valve component is essentially only related to the cross-section of the throttling through-hole. When the outflow portion of the valve space is closed by the actuator assembly, the intermediate valve rapidly opens and releases the large-cross-section through-hole connected to the high-pressure space, thereby causing a rapid termination of the injection process. Summary of the Invention

[0004] In fuel injection valves, it is generally desirable to simplify the structure, where, with reduced structural costs, not only should reliable controllability of the opening movement of the injection valve components be achieved, but also rapid closing of the injection valve components should be realized.

[0005] Therefore, the object of the present invention is to provide a fuel injection valve that at least partially improves upon the prior art.

[0006] This invention relates to a fuel injection valve for intermittently injecting fuel into the combustion chamber of an internal combustion engine. The fuel injection valve has a housing defining a longitudinal axis, the housing having a high-pressure fuel inlet and an injection valve seat. A high-pressure space is arranged within the housing, extending from the high-pressure fuel inlet to the injection valve seat. Furthermore, an injection valve member, which interacts with the injection valve seat, is arranged within the housing and is adjustable along the longitudinal axis.

[0007] The fuel injection valve further includes: a compression spring that loads the injection valve member with a closing force pointing toward the injection valve seat and preferably supports one side of the injection valve member and the other side fixedly supports it relative to the housing; a guide member in which the control piston of the injection valve member is guided by a sliding fit; an intermediate member that, together with the guide member and the control piston, defines a control space; and a hydraulic control device for controlling the axial movement of the injection valve member by changing the pressure in the control space.

[0008] The hydraulic control device has an intermediate valve comprising: an intermediate valve member with a mushroom-shaped structure and an intermediate valve seat; the intermediate valve member having a rod and a head guided in a guide gap of an intermediate component; and the intermediate valve seat being constructed on the head-facing side of the intermediate component and acting in conjunction with the head.

[0009] In the open position, the intermediate valve assembly releases the connection between the high-pressure fuel inlet and the control space, which are connected to the high-pressure space. In the closed position, the intermediate valve assembly interrupts the connection between the high-pressure fuel inlet and the control space, and separates the control space from the valve space—except for the throttling through-hole.

[0010] The fuel injection valve also includes an electrically actuated actuator assembly for connecting the valve space to the low-pressure fuel return section and for separating the valve space from the low-pressure fuel return section.

[0011] The head, in the closed position of the intermediate valve member, rests against the intermediate valve seat on a first sealing surface facing the intermediate component, forming a first annular sealing surface that is closed in the circumferential direction, and on a second sealing surface, forming a second annular sealing surface that is closed in the circumferential direction. The first sealing surface extends around the rod or the guide gap at a first radial distance, and the second sealing surface extends around the rod or the guide gap at a second radial distance, wherein the first radial distance is greater than the second radial distance.

[0012] The guide component and the intermediate component can be constructed as separate components. However, the guide component and the intermediate component can also be constructed as a single piece.

[0013] The throttling through-hole is preferably constructed on the intermediate valve member, particularly preferably on the head of the intermediate valve member. However, the throttling through-hole can also be constructed on an intermediate component. In another variation, the throttling through-hole can be constructed between the intermediate valve member and another component, for example, through a gap between the intermediate component or a guide component. The throttling through-hole constructed on the intermediate valve member can extend into a blind hole recessed in the intermediate valve member, belonging to the valve space, on the side opposite to the control space. Preferably, the throttling through-hole is constructed adjacent to the control space in the intermediate valve member. The throttling through-hole and the blind hole are preferably centered relative to the longitudinal axis. Thus, on the one hand, a throttling through-hole with a desired length can be constructed, and on the other hand, the blind hole can form part of the valve space.

[0014] Preferably, the first sealing surface and the second sealing surface are concentric annular surfaces. Depending on the design, the first sealing surface may be constructed on the head, i.e., on the side of the head facing the intermediate component, or on the intermediate component, i.e., on the side of the intermediate component facing the head. Depending on the design, the second sealing surface may also be constructed on the head, i.e., on the side of the head facing the intermediate component, or on the intermediate component, i.e., on the side of the intermediate component facing the head.

[0015] By sealing the head against the intermediate valve seat in the closed position of the intermediate valve member with the first and second annular sealing surfaces formed, fluid interruption at the connection between the high-pressure fuel inlet and the control space can be improved in the closed position of the intermediate valve member. Furthermore, this improves the separation between the control space and the valve space (excluding the throttling through-hole) in the closed position of the intermediate valve member, enabling more precise control of the axial movement of the injection valve member by coordinating the dimensions of the throttling through-hole and thus the injection process. Therefore, the sealing characteristics of the intermediate valve can be coordinated through a specific design of the sealing surface, for example, by its geometry or dimensions. Here, since the annular sealing surface is smaller than the facets of the head and intermediate component facing each other, the sealing characteristics of the intermediate valve can be improved by limiting or minimizing the adhesion force between the intermediate component and the intermediate valve member.

[0016] Furthermore, preferably in the closed position of the intermediate valve member, an intermediate space, preferably a gap annular space, is formed between the annular sealing surface, the intermediate component, and the head. In certain designs, the annular sealing surface seals the intermediate space not only relative to the valve space but also relative to the control space. In certain further embodiments, the annular sealing surface seals the intermediate space relative to the high-pressure fuel inlet. As will be further described below, it is advantageous to construct one or more through-holes in the intermediate component or intermediate valve member, depending on the design, which through-holes extend into the intermediate space in the closed position of the intermediate valve member and have no or negligible interference with the control of the injection process.

[0017] In a particular embodiment, the gap annular space has a gap width of less than 1 mm, or less than 0.5 mm, or less than 0.1 mm, or less than 0.05 mm when measured in the direction of the longitudinal axis.

[0018] In one embodiment, a high-pressure fuel inlet extends in an intermediate member such that, in the closed position of the intermediate valve member, the high-pressure fuel inlet passes into a gap annular space, which is constructed between the intermediate member and the head in the closed position of the intermediate valve member and is radially limited by first and second annular sealing surfaces.

[0019] By allowing the high-pressure fuel inlet to flow into the annular space defined by the intermediate component, the head, and the first and second annular sealing surfaces in the closed position of the intermediate valve member, both the valve space and the control space can be fluidly separated from the high-pressure fuel inlet or the high-pressure space through the sealed annular sealing surfaces in the closed position of the intermediate valve member. This provides the advantage that, in the closed position of the intermediate valve member, the inflow of fuel from the high-pressure space through the high-pressure fuel inlet into the valve space or control space can be minimized or avoided, thereby improving the control accuracy of the injection process.

[0020] In particular, an increased clearance can be provided between the rod of the intermediate valve member and the guide gap of the intermediate component, since the first and second annular sealing surfaces perform the function of fluidly sealing the high-pressure fuel inlet with the valve space and control space, and therefore no additional fluid sealing is required by guiding the rod in the guide gap of the intermediate component. Thus, a tight sliding fit of the rod in the guide gap to reduce leakage, as described in WO2016 / 041739A1, is no longer mandatory. Advantageously, the increased size of the possible clearance between the rod and the guide gap simplifies the manufacture of the components, i.e., the intermediate valve member or the rod and the intermediate component or the guide gap. In addition to larger manufacturing tolerances for the rod and the intermediate component, the height of the rod in the axial direction, i.e., along the longitudinal axis, can also be reduced, since the guidance of the rod in the guide gap no longer has to additionally perform the function of fluid sealing. This advantageously allows for a more compact structural form. Furthermore, due to the increased clearance during the opening movement of the intermediate valve member (to end the injection process), the valve space can be filled more quickly by the fuel flowing between the rod and the guide gap, thereby accelerating the end of the injection process.

[0021] Since, for example, a gap annular space with a smaller size in the axial direction, i.e., along the longitudinal axis, compared to the length of the rod, can reduce the radial pressure in the gap annular space, which may be detrimental to the sealing effect of the annular sealing surface.

[0022] As described above, the gap annular space, when measured in the direction of the longitudinal axis, can have a gap width of less than 1 mm, or less than 0.5 mm, or less than 0.1 mm, or less than 0.05 mm.

[0023] However, an intermediate space with a larger dimension along the axial direction can be provided instead of the aforementioned annular space.

[0024] The high-pressure fuel inlet may include a horizontal hole and a vertical hole relative to the longitudinal axis, wherein the vertical hole opens into the gap annular space in the closed position of the intermediate valve member.

[0025] In particular, the rod can be guided in a sliding fit within the guide gap of the intermediate component, such that there is a gap of at least 10 μm, preferably between 20 μm and 50 μm, in the radial direction between the rod and the guide gap.

[0026] In one embodiment, the intermediate valve member has an inlet that extends into the valve space at a first end and to the outside of the intermediate valve member at a second end, such that the second end is arranged with a smaller radial distance from the rod in the closed position of the intermediate valve member compared to the second annular sealing surface.

[0027] The inlet allows for the opening of the intermediate valve because, when the valve space is separated from the low-pressure fuel return section by the actuator assembly to end the injection process, the valve space can be filled more quickly with fuel from the high-pressure space via the inlet. In this regard, the outer side of the intermediate valve member should be understood as the guide gap surface of the intermediate member facing the intermediate component. Preferably, a blind hole is constructed in the rod of the intermediate valve member from the end opposite to the head, which preferably extends into the head and forms part of the valve space. In such an embodiment, the inlet can pass into the blind hole at its first end.

[0028] Preferably, in the closed position of the intermediate valve member, an internal annular space is formed between the intermediate component and the head, the internal annular space being adjacent to the rod and the second annular sealing surface, wherein the inlet connects the internal annular space to the valve space in the closed position of the intermediate valve member.

[0029] The access portion extends to the outside of the rod or head at its second end. In one variation, the second end of the access portion is arranged on a line along which the rod abuts the head. The access portion can be constructed as an inclined or horizontal hole relative to the longitudinal axis.

[0030] In one embodiment, the diameter of the inlet is larger than the minimum diameter of the low-pressure fuel return section. The large diameter of the inlet allows for rapid filling of the valve space, which positively impacts the opening process of the intermediate valve. In particular, the large inlet size can be achieved without additional leakage because the inlet can be separated from the high-pressure fluid in the closed position of the intermediate valve assembly due to the arrangement of the second end.

[0031] In one embodiment, the rod has at least one surrounding annular protrusion through which the rod is guided in a guide gap.

[0032] A throttling through-hole can be constructed axially around the rod via an annular protrusion. The throttling through-hole constructed with the annular protrusion offers the advantage that turbulent flow can be achieved instead of laminar flow for fluid flowing longitudinally through the intermediate space between the rod and the guide gap. In particular, the permissible radial clearance between the rod and the guide gap can be further increased.

[0033] In one embodiment, the rod has two annular protrusions spaced apart from each other in the longitudinal direction of the rod.

[0034] Because of the two annular protrusions spaced apart from each other in the longitudinal direction of the rod, two throttling through-holes connected in series along the longitudinal axis and surrounding the rod can be constructed in the longitudinal direction. This further promotes the formation of eddies and turbulence in the fluid flowing through the intermediate space between the rod and the guide gap.

[0035] Furthermore, in embodiments having two annular protrusions spaced apart from each other in the longitudinal direction of the rod, the gap between the rod and the guide gap in the radial direction can be further increased by the function of the throttling through-hole as a series connection.

[0036] In particular, the rod can be guided in the guide gap of the intermediate component, such that there is a gap of at least 50 μm, preferably between 70 μm and 100 μm, in the radial direction between the rod and the guide gap.

[0037] In one embodiment, the intermediate valve member has a valve space through-hole connected to a valve space, the valve space through-hole extending in the intermediate valve member such that, in the closed position of the intermediate valve member, the valve space through-hole opens into a gap annular space, the gap annular space being constructed between the intermediate member and the head in the closed position of the intermediate valve member and being radially limited by first and second annular sealing surfaces.

[0038] With this arrangement, in the closed position of the intermediate valve member, the valve space through-hole can advantageously seal relative to the control space and the high-pressure fuel inlet. This advantageously allows for a larger diameter of the valve space through-hole compared to, for example, the diameter of a throttling through-hole, without thereby promoting leakage from the control space or the high-pressure fuel inlet to the valve space through-hole or the valve space in the closed position of the intermediate valve member. The large size of the valve space through-hole provides the advantage that the valve space can be quickly filled through the valve space through-hole when the intermediate valve member moves away from the closed position, achieving rapid termination of the injection process.

[0039] In one embodiment, the fuel injection valve has an annular space that is bounded by an intermediate component, a rod, and a head in the closed position of the intermediate valve member, into which a high-pressure fuel inlet enters.

[0040] Preferably, the annular space has an inner annular space extending around the rod and bounded in the radial direction by the rod and the intermediate component, the inner annular space being recessed at the rod itself, wherein the high-pressure fuel inlet preferably extends into the inner annular space.

[0041] Preferably, the annular space has a gap annular space adjacent to the inner annular space, which is formed by the surrounding gap between the head of the intermediate component and the intermediate valve component in the closed position of the intermediate valve component.

[0042] In the closed position of the intermediate valve component, the annular space of the gap can have at least a substantially constant gap width. Here, the gap width is preferably at least five times smaller than the inner annular space, measured in the direction of the longitudinal axis.

[0043] This annular space design further reduces adhesion.

[0044] Preferably, the internal annular space on the stem of the intermediate valve member is formed by a surrounding annular groove that opens outward in the radial direction. This annular groove, when viewed along the longitudinal axis, preferably has dimensions such that the inlet portion of the high-pressure fuel inlet is always at least almost entirely located within the region of the annular groove. Furthermore, the annular groove is preferably directly adjacent to the head. This advantageously achieves a simple construction for the intermediate component.

[0045] Preferably, the entire inlet of the high-pressure fuel inlet is located within the area of ​​the inner annular space. This avoids the need for angled holes that might otherwise be required in intermediate components.

[0046] Preferably, the annular groove has a trapezoidal cross-section, wherein the inclined extending side faces away from the head. Utilizing this side, when the intermediate valve member is open, the fuel flowing through the high-pressure fuel inlet can be diverted with minimal loss in the direction toward the head.

[0047] In the following embodiment, the intermediate valve member has a valve space through-hole connected to the valve space. In the closed position of the intermediate valve member, the valve space through-hole opens into the gap annular space, and the high-pressure fuel inlet opens into the annular space bounded by the intermediate component, the rod, and the head. The rod is preferably guided in the guide gap of the intermediate component with a tight sliding fit, thereby preventing leakage from the high-pressure fuel inlet through the guide portion of the rod into the valve space or minimizing such leakage.

[0048] In one embodiment, a secondary through-hole is constructed on the intermediate valve member, preferably on the rod, which connects the high-pressure fuel inlet or high-pressure space to the valve space. Alternatively or supplementarily, the secondary through-hole can be constructed on the intermediate component.

[0049] The secondary through-hole preferably enters the valve space through a straight throttling orifice extending in the radial direction, or more preferably through a blind hole in the rod.

[0050] The secondary through-section is preferably connected to the high-pressure space through an annular space limited by the intermediate component, rod, and head at the closed position of the intermediate valve component.

[0051] In one embodiment, the secondary through-hole can extend from the annular groove, preferably from its radially inner bottom, and preferably radially relative to the longitudinal axis into the valve space. Alternatively, the rod of the intermediate valve member can have a pocket-shaped opening, preferably groove-shaped, originating from the annular groove, from which the secondary through-hole preferably also extends radially relative to the longitudinal axis into the valve space. In embodiments with pocket-shaped openings, it is preferable to construct two radially opposite pocket-shaped openings on the rod to achieve symmetrical pressure conditions.

[0052] In one embodiment, the valve space through-hole has a hole in the head that is parallel to or inclined relative to the longitudinal axis, the hole opening into the gap annular space in the closed position of the intermediate valve member.

[0053] Preferably, the valve space through portion also has a horizontal hole in the head, which connects a hole parallel to or inclined relative to the longitudinal axis to a blind hole.

[0054] The intermediate valve component may also have two or more valve space through-holes, each opening into the annular gap space. Accordingly, a plurality of parallel or inclined holes associated with the respective valve space through-holes may exist in the head, each opening into the annular gap space.

[0055] Preferably, a first annular sealing ridge is formed on the side of the head facing the middle component or on the side of the middle component facing the head, the first annular sealing ridge having a first end side forming a first sealing surface.

[0056] The sealing protrusion offers the following advantages: it can provide a reliable fluid seal when forming an annular sealing surface, while reducing or minimizing the adhesion between the intermediate component and the intermediate valve assembly.

[0057] Preferably, a second annular sealing ridge is formed on the side of the head facing the middle component or on the side of the middle component facing the head, the second annular sealing ridge having a second end side, the second end side forming a second sealing surface.

[0058] In embodiments where the sealing ridge is constructed on the head, the flat surface of the intermediate member opposite the sealing ridge typically forms an intermediate valve seat. In embodiments where the sealing ridge is constructed on the intermediate member, the end face of the sealing ridge typically forms not only the intermediate valve seat but also a sealing surface, which seals in conjunction with the flat surface of the head opposite the sealing ridge. In embodiments where both the first and second sealing ridges are constructed on the intermediate member, the intermediate valve seat may therefore include not only the end face of the first sealing ridge but also the end face of the second sealing ridge.

[0059] Preferably, both the first sealing protrusion and the second sealing protrusion are constructed on the head or both are constructed on the intermediate component. However, it is also conceivable that one of the sealing protrusions is constructed on the head, while the other of the sealing protrusions is constructed on the intermediate component.

[0060] In one embodiment, the intermediate component has at least one stepped portion in the radial direction on the side facing the head, and the head has at least one stepped portion in the radial direction on the side facing the intermediate component, wherein, in the closed position of the intermediate valve member, the offset edges of the stepped portions of the intermediate component and the head respectively reach the first and / or second annular sealing surfaces in the radial upper limit.

[0061] The stepped portion of the intermediate component or head is typically constructed around the rod or guide gap. The stepped portion of the intermediate component or head may be constructed with concave or convex features. The stepped portion of the intermediate component and / or head may have vertical and horizontal surfaces relative to the longitudinal axis. However, alternatively or additionally, the stepped portion may also have chamfered or curved surfaces. In this regard, the stepped portion may in particular include steps formed by the edges of the head or intermediate component. The dimensions of the first and / or second annular sealing surfaces can advantageously be coordinated by suitable stepped portion dimensions. Furthermore, by appropriately constructing the stepped portion and / or its combination with one or more sealing protrusions, one or more intermediate spaces, particularly gap annular spaces, can be constructed in the closed position of the intermediate valve member, into which one or more through-holes, such as valve space through-holes, fuel high-pressure inlets, etc., can enter.

[0062] In one embodiment, the stepped portion of the intermediate component forms an internal annular space, which is bounded by the intermediate component, rod, and head in the closed position of the intermediate valve member.

[0063] Preferably, the rod is continuously guided within the guide gap of the intermediate component.

[0064] Preferably, the fuel injection valve housing has a housing body with a high-pressure fuel inlet and a nozzle body, with the injection valve seat constructed on the nozzle body. Preferably, the intermediate component and therefore the intermediate valve are arranged in the nozzle body. Advantageously, this results in a construction that is short in the longitudinal direction, as well as the housing body and the injection valve components.

[0065] In another embodiment, the housing has a housing body with a high-pressure fuel inlet and a nozzle body, with an injection valve seat constructed on the nozzle body; however, an intermediate component and thus an intermediate valve are arranged between the housing body and the nozzle body. This advantageously allows for a slender design of the nozzle body.

[0066] In one embodiment, the guide gap (open in the direction toward the control space) is constructed as a blind orifice, wherein the discharge orifice is constructed at an intermediate part from the guide gap, preferably from its bottom to the low-pressure fuel return section. Preferably, the discharge orifice is constructed in a stepped narrowing manner as viewed from the guide gap.

[0067] Alternatively, a two-piece solution can be used, such as that described in WO2016 / 041739A1. Figures 2 to 4 In , 8 and 9 or in WO2007 / 098621A1 Figure 2 , 4 As disclosed in 5, 7, and 8. For example, an intermediate element may be adjacent above the intermediate component, wherein a discharge hole may be constructed in the intermediate element, and a guide gap may be constructed as a continuous hole in the intermediate component. The intermediate element is preferably constructed in a plate shape.

[0068] The valve space typically includes the space defined by the intermediate valve member, particularly the end of the rod facing the low-pressure fuel return section, and the space for guiding the clearance, the discharge port, and, if possible, the blind port in the intermediate valve member.

[0069] Preferably, the inlet portion of the discharge port facing the low-pressure fuel return section forms a low-pressure outlet.

[0070] In another embodiment, the housing has a housing body with a high-pressure fuel inlet and a nozzle body, with an injection valve seat constructed on the nozzle body. An intermediate body is arranged between the housing body and the nozzle body, and an intermediate component is disposed within or preferably received by the intermediate body. For this purpose, the intermediate body preferably has a receiving gap that opens toward the nozzle body and connects to the high-pressure space, in which the intermediate component is disposed. The intermediate body may here be part of an actuator assembly.

[0071] Preferably, the plunger of the actuator assembly extends through a corresponding through-hole in the intermediate body to close or open a low-pressure outlet constructed on the intermediate body. The intermediate body here preferably forms a guide element for the plunger. Preferably, the housing body is hermetically abutted against one end of the intermediate body, while the nozzle body is hermetically abutted against the opposite end of the intermediate body.

[0072] In one embodiment, the guide gap is limited on the control space side by a shoulder constructed on the intermediate member and recessed relative to the nozzle body-facing end, which may have an intermediate valve seat. Thus, a head space can be formed between the shoulder and the nozzle body-facing end of the intermediate member, into which the head of the intermediate valve member can be received. This embodiment allows for the simple construction of the guide member because its end facing the intermediate member can form a stop for limiting the stroke of the intermediate valve member.

[0073] Preferably, the guide member is formed of a cylindrical guide sleeve, on which a compression spring supports, wherein the compression spring thereby presses the guide sleeve against the intermediate member in a sealing manner.

[0074] When the fuel injection valve is in operation, the throttling through section can be temporarily closed to reduce fuel loss. On one hand, this can be as described in the following paragraph. On the other hand, there is also the possibility of temporarily closing the throttling through section using a check valve, as is known, for example, from WO2018 / 162747A1 and DE19516565A1.

[0075] In one embodiment, the control piston of the injection valve component has a cam-shaped protrusion on its side facing the intermediate valve, which can close the throttling passage when it abuts against the intermediate valve component.

[0076] The present invention also relates to a fuel injection valve for intermittently injecting fuel into the combustion chamber of an internal combustion engine, the fuel injection valve comprising: a housing defining a longitudinal axis, the housing having a high-pressure fuel inlet and an injection valve seat; a high-pressure space disposed in the housing, the high-pressure space extending from the high-pressure fuel inlet to the injection valve seat; an injection valve member adjustablely disposed in the housing along the longitudinal axis, the injection valve member interacting with the injection valve seat; a compression spring loading the injection valve member with a closing force pointing toward the injection valve seat; a guide member, a control piston of the injection valve member being guided by a sliding fit in the guide member; an intermediate member, the intermediate member, together with the guide member and the control piston, defining the control space; and a hydraulic control device for controlling the axial movement of the injection valve member by changing the pressure in the control space, the hydraulic control device having An intermediate valve comprising: a mushroom-shaped intermediate valve member and an intermediate valve seat, the intermediate valve member having a rod and a head guided in a guide gap of an intermediate component, the intermediate valve seat being constructed on the head-facing side of the intermediate component and acting in conjunction with the head, wherein the intermediate valve member, in an open position, releases a connection between a high-pressure fuel inlet connected to a high-pressure space and a control space, and in a closed position interrupts the connection between the high-pressure fuel inlet and the control space, and separates the control space from the valve space—except for the throttling through-hole; and an electrically actuated actuator assembly for connecting the valve space to a low-pressure fuel return section and for separating the valve space from the low-pressure fuel return section, wherein the intermediate valve member, in an open position, releases a second connection between the high-pressure fuel inlet and the valve space and in a closed position interrupts the second connection between the high-pressure fuel inlet and the valve space.

[0077] By releasing the second connection between the high-pressure fuel inlet and the valve space in the open position, the valve space can be filled with fuel through the second connection, enabling a faster opening movement of the intermediate valve member. In particular, the second connection improves valve space filling compared to fuel injection valves, where the valve space is filled, for example, only from the control space through a throttling through-hole. Therefore, advantageously, the valve space can be filled through the second connection even with a small opening movement of the intermediate valve member. As for the throttling through-hole, it is advantageously sufficient here that fuel flows from the control space through the throttling through-hole into the valve space, causing an initial small opening movement of the intermediate valve member, because the valve space can then be filled with a large amount of fuel through the second connection.

[0078] By interrupting the second connection between the high-pressure fuel inlet and the valve space in the closed position of the intermediate valve member, it is advantageous to prevent fuel from flowing from the high-pressure space to the low-pressure fuel return section via the second connection in the closed position of the intermediate valve member. In examples where additional filling of the valve space is achieved through a secondary through-hole in the intermediate component or intermediate valve member that permanently connects the high-pressure space to the valve space, fuel may also flow through the valve space to the low-pressure fuel return section during the injection process, i.e., in the closed position of the intermediate valve member, which may result in adverse fuel loss and increased wear due to fuel depressurization in the high-pressure space. By interrupting the second connection between the high-pressure fuel inlet and the valve space in the closed position of the intermediate valve member, adverse fuel loss and wear due to fuel depressurization from the high-pressure space to the valve space can be reduced or mitigated during injection, while simultaneously enabling rapid filling of the valve space for the opening movement of the intermediate valve member.

[0079] In one embodiment, the second connection extends between the high-pressure fuel inlet and a hole that extends through a rod passing through an intermediate valve member, the hole being part of the valve space. This hole is preferably constructed as a blind hole.

[0080] In one embodiment, the head, in the closed position of the intermediate valve member, rests against the intermediate valve seat on a first sealing surface facing the intermediate member, forming a first annular sealing surface that is closed in the circumferential direction, and on a second sealing surface, rests against the intermediate valve seat on a second sealing surface, forming a second annular sealing surface that is closed in the circumferential direction. The first sealing surface extends about the rod or the guide gap at a first radial distance, and the second sealing surface extends about the rod or the guide gap at a second radial distance, wherein the first radial distance is greater than the second radial distance.

[0081] In one embodiment, a first annular sealing ridge is formed on the side of the head facing the middle component or on the side of the middle component facing the head, the first annular sealing ridge having a first end side forming a first sealing surface.

[0082] In one embodiment, a second annular sealing ridge is formed on the side of the head facing the middle component or on the side of the middle component facing the head, the second annular sealing ridge having a second end side forming a second sealing surface.

[0083] In one embodiment, the intermediate component has at least one stepped portion on the side facing the head, and the head has at least one stepped portion on the side facing the intermediate component, wherein, in the closed position of the intermediate valve member, the offset edges of the stepped portions of the intermediate component and the head respectively reach the first and / or second annular sealing surfaces at the radial upper limit.

[0084] In one embodiment, the stepped portion of the intermediate component forms an internal annular space, which is bounded by the intermediate component, rod, and head in the closed position of the intermediate valve member.

[0085] In one embodiment, the high-pressure fuel inlet extends in the intermediate member such that, in the closed position of the intermediate valve member, the high-pressure fuel inlet passes into a gap annular space, the gap annular space being constructed between the intermediate member and the head in the closed position of the intermediate valve member and being radially limited by first and second annular sealing surfaces.

[0086] In one embodiment, the second connection includes an inlet to the intermediate valve member, the inlet having a first end opening into the valve space and a second end opening to the outside of the intermediate valve member. As explained above, the valve space can advantageously be filled by the inlet to support the opening movement of the intermediate valve member. Preferably, the inlet has its first end opening into the blind hole, which extends through the rod and is part of the valve space.

[0087] In one embodiment, the inlet extends to the outside of the intermediate valve member at a second end, such that the second end is arranged with a smaller radial distance from the rod in the closed position of the intermediate valve member compared to the second annular sealing surface.

[0088] In one embodiment, the second connection portion includes a through portion formed by a gap of at least 10µm, preferably between 20µm and 50µm, existing radially between the rod and the guide gap.

[0089] In one embodiment, the rod has two annular protrusions spaced apart from each other in the longitudinal direction of the rod.

[0090] In one embodiment, the annular protrusions each have at least one chamfer along the circumferential direction, wherein the second connecting portion includes a through-hole formed by an intermediate space between the at least one chamfer and the guide gap. The at least one chamfer keeps the gap between the rod and the guide gap sufficiently small, allowing for better centering of the rod, i.e., simultaneously avoiding or reducing eccentricity or tilting of the rod. Meanwhile, despite the small gap, the at least one chamfer between the outer side of the rod and the guide gap still provides a sufficient through-hole formed by the intermediate space between the at least one chamfer and the guide gap, which serves as the through-hole of the second connecting portion.

[0091] In one embodiment, the annular protrusion has two or three chamfers along the circumferential direction.

[0092] In one embodiment (without the annular protrusion), the rod has at least one chamfer in the circumferential direction, wherein the second connection includes a through-hole formed by an intermediate space between the at least one chamfer and the guide gap. As already explained, the at least one chamfer allows the gap between the rod and the guide gap to be kept sufficiently small, which allows for better centering of the rod, i.e., simultaneously avoiding or reducing eccentric or tilted positions of the rod. Meanwhile, despite the small gap, the at least one chamfer between the outer side of the rod and the guide gap still provides a sufficient through-hole formed by the intermediate space between the at least one chamfer and the guide gap, which serves as the through-hole of the second connection.

[0093] In one embodiment, the rod has two or three chamfers along the circumferential direction.

[0094] In one embodiment, the second connection includes a hole extending through the head of the intermediate valve member, the hole at least partially forming a valve space through-hole connected to the valve space and opening at one end to the side of the head facing the intermediate member.

[0095] In one embodiment, the valve space through-hole extends in the intermediate valve member such that the valve space through-hole passes into the gap annular space in the closed position of the intermediate valve member, the gap annular space being constructed between the intermediate component and the head in the closed position of the intermediate valve member and being radially limited by the first and second annular sealing surfaces.

[0096] In one embodiment, the fuel injection valve has an annular space bounded by an intermediate component, a rod, and a head in the closed position of the intermediate valve member, into which a high-pressure fuel inlet enters. Attached Figure Description

[0097] Embodiments of the invention will be explained in more detail with the aid of the following figures and related description. The figures schematically illustrate:

[0098] Figure 1 A longitudinal section is shown of a fuel injection valve in the prior art;

[0099] Figure 2 and Figure 1 Compared to the enlarged view of a portion of the fuel injection valve in the prior art, which is enclosed by a rectangle marked II;

[0100] Figure 3 A partial longitudinal section is shown of a first embodiment of the fuel injection valve according to the invention, wherein the partial section presents a corresponding section of the fuel injection valve. Figure 2 The region marked as III in the middle;

[0101] Figure 4 A partial longitudinal section is shown of a second embodiment of the fuel injection valve according to the invention, wherein the partial section presents a corresponding section of the fuel injection valve. Figure 2 The region marked as III in the middle;

[0102] Figure 5a A partial longitudinal section is shown of a third embodiment of the fuel injection valve according to the invention, wherein the partial section represents a portion of the fuel injection valve corresponding to... Figure 2 The region marked as III in the middle;

[0103] Figure 5b A partial horizontal cross-sectional view of another embodiment of the fuel injection valve according to the present invention is shown;

[0104] Figure 6 A partial longitudinal section is shown of a fourth embodiment of the fuel injection valve according to the invention, wherein the partial section presents a corresponding aspect of the fuel injection valve. Figure 2 The region marked as III in the middle;

[0105] Figure 7 A partial longitudinal section is shown of a fifth embodiment of the fuel injection valve according to the invention, wherein the partial section presents a corresponding section of the fuel injection valve. Figure 2 The region marked as III in the middle. Detailed Implementation

[0106] In the accompanying drawings, the same reference numerals are used for components that correspond to each other in the embodiments.

[0107] Figure 1The diagram shows a fuel injection valve 10' according to WO2016 / 041739A1, used for intermittently injecting fuel into the combustion chamber of an internal combustion engine. Here, the fuel is under very high pressure, for example, up to 2000 bar or higher.

[0108] The fuel injection valve 10′ has a housing 12′ defining a longitudinal axis L. This housing has a housing body 14′, a nozzle body 16′, and an actuator receiver 20′. An injection valve seat 18′ is constructed on the nozzle body, and the actuator receiver is arranged between the housing body 14′ and the nozzle body 16′. A locking nut 22′ supported on the nozzle body 16′ receives the actuator receiver 20′ and is threaded onto the housing body 14′. The housing body 14′, the actuator receiver 20′, and the nozzle body 16′ abut against each other at their ends, are pressed together in a sealing manner by the locking nut 22′, and are aligned with each other in the direction of the longitudinal axis L.

[0109] In a known manner, the outer shape of the shell 12′ is at least approximately cylindrical.

[0110] On the end side of the housing body 14′ facing away from the nozzle body 16′, a high-pressure fuel inlet 24′ is arranged. A high-pressure space 26′ extends from the high-pressure fuel inlet inside the housing 12′—through the housing body 14′, the actuator receiver 20′, and the nozzle body 16′—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-shaped perforated filter 32′ for trapping any foreign particles in the fuel. The disc-shaped valve member of the check valve 30′, which interacts with the valve seat constructed on the valve carrier 28′, has a bypass port.

[0111] The check valve 30′ allows fuel supplied via the high-pressure feed line to flow virtually unimpeded into the high-pressure space 26′ in a known manner, but prevents fuel from flowing out of the high-pressure space 26′ into the high-pressure feed line, except for bypasses.

[0112] The construction and operating principle of a cylindrical structural unit comprising a valve carrier 28', a check valve 30', and a perforated filter 32' are disclosed in document WO2014 / 131497A1. The high-pressure fuel inlet 24' and the valve carrier 28' with the check valve 30' and the perforated filter 32' can also be designed as disclosed in document WO2013 / 117311A1. Possible embodiments of the high-pressure fuel inlet 24', the check valve 30', and a rod filter replacing the perforated filter 32' are known from document WO2009 / 033304A1. The corresponding disclosures of the above documents are incorporated herein by reference.

[0113] Adjacent to the valve carrier 28′, the high-pressure space 26′ has discrete storage chambers 34′ constructed on the housing body 14′, which are connected to the injection valve seat 18′ via the flow channel 36′ of the high-pressure space 26′.

[0114] The dimensions and operating principle of the discrete storage chamber 34′ together with the check valve 30′ with bypass are disclosed in document WO2007 / 009279A1; the corresponding disclosure is deemed to be incorporated herein by reference.

[0115] Instead of check valve 30', a fixed throttle valve can also be installed in certain embodiments.

[0116] An electrically operated actuator assembly 38' is received in a known manner within the gap of actuator receiver 20'. This actuator assembly is characterized by a plunger 40', which is spring-loaded in one direction and movable in another direction by means of an electromagnet of the actuator assembly 38', for closing the low-pressure outlet 42' to connect the valve space 44' with the low-pressure fuel return section 46' (see [link]). Figure 2 The valve space 44' is separated from the low-pressure outlet 42' to connect the low-pressure fuel return section 46'. The longitudinal axis of the plunger 40' and the actuator assembly 38', marked with 48', extends parallel to and eccentrically to the longitudinal axis L.

[0117] The channel 52′ extends from the electrical connector 50′ through the housing body 14′ to the actuator assembly 38′, parallel to the discrete storage chamber 34′ eccentrically arranged relative to the longitudinal axis L of the housing 12′ and therefore the fuel injection valve 10′, and receives electrical control lines for controlling the actuator assembly 38′ in the channel.

[0118] A plunger 40' passes through the bottom of a cup-shaped actuator receiver 20', which forms a guide element for the plunger 40'. The plunger 40' has a guide wing projecting radially, which allows the plunger to be movably slidably guided on the guide element parallel to the longitudinal direction L. The guide wing forms a through-hole extending in the longitudinal direction L, through which fuel can flow from the low-pressure outlet 42' to the low-pressure fuel return section 46'.

[0119] Figure 2 Show Figure 1 A magnified view of the fuel injection valve in the rectangular area marked II.

[0120] A conical injection valve seat 18' is integrally formed on the nozzle body 16', which is directly connected to the storage chamber 34' through the flow channel 36' and thus to the high-pressure fuel inlet 24'.

[0121] Downstream of the injection valve seat 18′, along the direction of fuel flow, the injection opening 54′ is constructed in a known manner in the free end region of the hemispherical nozzle body 16′. When the injection valve member 56′ is lifted from the injection valve seat 18′, fuel under very high pressure is injected into the combustion chamber of the internal combustion engine through this injection opening.

[0122] The injection valve component 56′ is configured as a needle and works in conjunction with the injection valve seat 18′. The injection valve component 56′ is movably guided along the longitudinal axis L in a guide hole 57′ that is concentric with the longitudinal axis L and belongs to the high-pressure space 26′ in the nozzle body, wherein low-loss flow of fuel to the injection valve seat 18′ and to the injection opening 54′ is achieved through a gap on the injection valve component 56′ that extends longitudinally and opens outward in the radial direction.

[0123] Upstream of the guide hole 57′, the internal space 58′ of the nozzle body 16′ belonging to the high-pressure space 26′ is designed to be twice as wide toward the actuator receiver 20′, wherein the section of the internal space 58′ extending at approximately the longitudinal center of the nozzle body 16′ to its end facing the actuator receiver 20′ defines an internal cylindrical section 60′ of the nozzle body 16′ with a constant cross-section.

[0124] Between section 60′ and guide hole 57′, a support ring is integrally formed on the injection valve member 56′, and a compression spring 62′ is supported on the support ring at one end. The other end of the compression spring 62′ is supported on the guide sleeve 64′′ that forms the guide member 64′. The compression spring 62′ loads the injection valve member 56′ with a closing force acting in the direction of injection valve seat 18′. On the other hand, the compression spring 62′ holds the guide member 64′ or guide sleeve 64′′, wherein its end facing away from the compression spring 62′ is sealed against the intermediate member 66′. The guide member 64′ can be designed in a different form than the sleeve, for example, it can be designed as a cuboid or annular body.

[0125] In the guide member 64' or guide sleeve 64'', a dual-acting control piston 68' integrally formed on the injection valve member 56' is movably guided in the direction of the longitudinal axis L with a tight sliding fit of approximately 3µm to 5µm. The control piston 68', the guide member 64'' or guide sleeve 64'', and the intermediate member 66' divide the control space 70' relative to the high-pressure space 26'. The intermediate member 66' is part of the hydraulic control device 72'.

[0126] Figure 3 A partial longitudinal section is shown of a first embodiment of the fuel injection valve 10 according to the present invention. This section presents an area of ​​the fuel injection valve 10 corresponding to... Figure 2The rectangle marked III, wherein the specific design of this region according to the first embodiment of the fuel injection valve 10 of the present invention differs from that according to WO2016 / 041739A1. Figure 2 The fuel injection valve 10' shown is particularly relevant to the hydraulic control unit 72, and is referenced below. Figure 3 Description. The remaining area of ​​the fuel injection valve 10 in the first embodiment, outside the rectangle marked III, substantially corresponds to... Figure 1 and 2 The fuel injection valve 10' shown is illustrated. This also applies accordingly to portions of other embodiments of the fuel injection valve 10 according to the invention, which... Figures 4 to 7 As shown in the image.

[0127] A cylindrical guide gap 74 extends from the flat end facing the control space 70 through the intermediate member 66 to the equally flat end facing away from the control space 70. The rod 76 of the mushroom-shaped intermediate valve member 78 is guided within this guide gap. The head 80 of the intermediate valve member 78, integrally constructed with the rod 76, is located in the control space 70 and interacts with the intermediate member 66 on its side facing the intermediate member, the flat end of which forms an annular intermediate valve seat 82.

[0128] The intermediate valve component 78 together with the intermediate valve seat 82 constructed on the intermediate component 66 forms the intermediate valve 83.

[0129] An annular first sealing ridge 111 is formed on the side of the head 80 facing the intermediate member 66. The first sealing ridge extends around the rod 76 at a first radial distance r1. The first sealing ridge has a first end face 111.1, which forms a first sealing surface 111.2. Furthermore, an annular second sealing ridge 112 is formed on the side of the head 80 facing the intermediate member 66. The second sealing ridge extends around the rod 76 at a second radial distance r2. The second sealing ridge has a second end face 112.1, which forms a second sealing surface 112.2. Figure 3 As shown, the intermediate valve member 78 is in the closed position. In this closed position, the head 80 rests against the intermediate valve seat 82 on the first sealing surface 111.2 with its side facing the intermediate member 66 forming a first annular sealing surface 121 that is closed in the circumferential direction, and on the second sealing surface 112.2 with a second annular sealing surface 122 that is closed in the circumferential direction. Here, the first radial distance r1 is greater than the second radial distance r2 from the rod 76.

[0130] A high-pressure fuel inlet 86 extends from the intermediate component 66, connecting to the high-pressure space 26 and including a horizontal orifice 861 and a vertical orifice 862. In the closed position of the intermediate valve component 78, the vertical orifice 862 opens into the annular clearance space 118, which is constructed between the intermediate component 66 and the head 80 and radially limited by the first and second annular sealing surfaces 121, 122. Figure 3 As can be seen, multiple high-pressure fuel inlets 86 can be provided. An optional second high-pressure fuel inlet 86 is located in the intermediate component 66. Figure 3 The area on the right side of the middle section is shown by a dashed line.

[0131] Between the rod 76 and the guide gap 74, there is preferably a gap of at least 10 μm in the radial direction. However, the gap can also be smaller, for example, between 3 µm and 10 µm. In other embodiments, the gaps can be larger and, for example, have values ​​between 20 µm and 50 µm. The second radial distance r2 between the second annular sealing surface 122 and the rod 76 is greater than the gap (e.g., a large number of 1 / 10 mm). Since the high-pressure fuel inlet 86 is sealed by the annular sealing surfaces 121, 122 in the closed position of the intermediate valve member 78, the possibility of additional leakage in the inlet valve space 44 caused by the gap between the rod 76 and the guide gap 74 is minimized or negligible. It can also be seen that, for this reason, the rod 76 can be constructed to be shorter along the longitudinal axis L compared to the prior art, for example, compared to the case of the fuel injection valve in WO2016 / 041739A1. Furthermore, the intermediate member 66 can also be designed to be shorter in the direction of the longitudinal axis L, thereby achieving a more compact structural form.

[0132] Although the high-pressure fuel inlet 86 is reliably sealed in the closed position of the intermediate valve member 78, the adhesion between the head 80 and the intermediate part 66 remains small thanks to the seal achieved by the intermediate valve member 78 through the two annular sealing surfaces 121, 122.

[0133] exist Figure 3 In this intermediate component 66, an intermediate element 98 is disposed adjacent to it, through which a stepped, narrowed discharge port 102 is present. This discharge port connects to a guide gap 74 at one end and forms a low-pressure outlet 42 at the other end. The discharge port 102 is eccentrically arranged relative to the longitudinal axis L. In a particular embodiment, the intermediate element 98 and the intermediate component 66 are integrally constructed as a single intermediate component, in which the guide gap is constructed as a blind hole (see, for example...). Figure 5a ).

[0134] Compared to the guide gap 74, the length dimension of the rod 76 in the longitudinal axis L direction is designed such that, in the closed position of the intermediate valve member 78, a flow gap 100 is maintained between the end side of the rod 76 facing the discharge port 102 and the intermediate element 98.

[0135] The intermediate valve member 78 has an inlet 96 that extends at a first end into a blind hole 92 (which is part of the valve space 44) extending through the rod 76 and at a second end into a line on the outside of the intermediate valve member 78, on which the rod 76 is adjacent to the head 80.

[0136] In the closed position of the intermediate valve component 78, an internal annular space 117 is constructed between the intermediate component 66 and the head 80. This annular space is adjacent to the rod 76 and the second annular sealing surface 122. In the closed position of the intermediate valve component 78, the inlet 96 connects the internal annular space 117 to the blind hole 92 or the valve space 44.

[0137] A blind hole 92 extends through the rod 76 and into the head 80. The entry portion 96 is configured as a hole inclined relative to the longitudinal axis L. However, in a further embodiment, the entry portion 96 may also be configured as a horizontal hole.

[0138] A throttling through-hole 90 is constructed on the head 80, extending from the end of the head 80 facing the control piston 68 to the blind hole 92 and connecting the valve space 44 to the control space 70. The diameter of the inlet 96 is larger than the diameter of the throttling through-hole 90. Although schematically... Figure 3 Not shown in the image, the diameter of the inlet 96 may also be greater than the minimum diameter of the stepped outlet 102.

[0139] In the open position, the intermediate valve member 78 releases the second connection between the high-pressure fuel inlet 86 and the valve space 44 through the inlet 96, allowing the valve space 44 or blind orifice 92 to fill with fuel. As the intermediate valve member 78 makes a small movement away from the intermediate component 66, fuel can also flow from the high-pressure fuel inlet 86 through the gap annular space 118 and the inner annular space 117 through the inlet 96 into the blind orifice 92, supporting the opening movement of the intermediate valve member 78. In the closed position, the second connection between the high-pressure fuel inlet 86 and the valve space 44 or blind orifice 92 is interrupted by the second sealing protrusion 112 or the second sealing surface 112.2.

[0140] The second connection is particularly advantageous for the intermediate valve member with the mushroom-shaped structure according to the invention, because the aforementioned rapid filling of the blind hole of the intermediate valve member can be achieved for the rapid opening movement of the intermediate valve member.

[0141] The control piston 68 has a cam-shaped protrusion 561 with a preferably circular cross-section on its head-facing side 80, which serves as a stroke limiter for the injection valve member 56 and can rest against the intermediate valve member 78. The cam-shaped protrusion 561 has a gap 5611 extending perpendicular to the plane of the figure, allowing fuel to flow from the control space 70 through the throttling through-hole 90 into the valve space 44 or blind orifice 92 even when the cam-shaped protrusion 561 rests against the intermediate valve member 78. The gap 5611 thus extends radially (or...) Figure 3 The direction shown is perpendicular to the plane of the figure and is constructed openly toward the control space 70.

[0142] A stop shoulder 84 is constructed spaced apart from the intermediate member 66 on the guide sleeve 641 forming the guide member 64. The stop shoulder restricts the opening stroke of the intermediate valve member 78. To allow fuel to flow from the high-pressure fuel inlet 86 into the control space 70 with minimal loss, a sufficiently large gap exists radially outward between the head 80 and the guide sleeve 641. The head 80 has a wedge-shaped flow groove on its side facing the stop shoulder 84. When the intermediate valve member 78 is in the open position and the head 80 abuts against the stop shoulder 84, the flow groove allows fuel to flow with minimal loss from the gap to the control piston 68. In a particular embodiment, the guide member 64 or the guide sleeve 641 may be integrally constructed with the intermediate member 66 as a single piece.

[0143] The intermediate valve 83 has the following functions: in the closed position of the intermediate valve member 78, it separates the fuel high pressure inlet 86 from the control space 70 and the valve space 44, and in the open position of the intermediate valve member 78, that is, when the head 80 is lifted from the intermediate valve seat 82, it releases the connection between the fuel high pressure inlet 86 and the control space 70 and the valve space 44.

[0144] The intermediate element 98 is arranged in the nozzle body 16 and abuts against the corresponding end side of the actuator receiver 20 with its flat end side facing away from the intermediate part 66.

[0145] In order to properly position the intermediate element 98 relative to the actuator receiver 20 and thus relative to the actuator assembly 38, both the intermediate element 98 and the actuator receiver 20 have mutually aligned, mutually facing, blind-hole-shaped positioning holes 106, in which a common positioning pin 104 is inserted.

[0146] To fix the position of the intermediate components 66 relative to the intermediate element 98, additional blind-hole-shaped positioning holes are provided on these components, and positioning pins 1041 are also embedded in these positioning holes. These positioning holes are located in... Figure 3 Since the locating pin 1041 is outside the drawing plane, it is shown as a dashed line.

[0147] Typically, each component has at least two locating holes that are aligned in pairs with the locating holes of adjacent components, so that the two adjacent components are held in place relative to each other by at least two locating pins.

[0148] Figure 4 A partial longitudinal section is shown of a second embodiment of the fuel injection valve 10 according to the present invention. This section presents an area of ​​the fuel injection valve 10 corresponding to... Figure 2 The rectangle marked III, wherein the specific design of this region according to the second embodiment of the fuel injection valve 10 of the present invention differs from that according to WO2016 / 041739A1. Figure 2 The fuel injection valve 10′ shown is particularly relevant to the hydraulic control device 72.

[0149] Figure 4 The second embodiment of the fuel injection valve according to the invention shown herein substantially corresponds to Figure 3 The first embodiment shown differs in that the first and second sealing protrusions 111 and 112 are constructed on the intermediate member 66 instead of on the head 80. An annular first sealing protrusion 111, extending about a guide gap 74 at a first radial distance r1, is constructed on the side of the intermediate member 66 facing the head 80. This first sealing protrusion has a first end face 111.1, which forms a first sealing surface 111.2. An annular second sealing protrusion 112, extending about a guide gap 74 at a second radial distance r2, is also constructed on the side of the intermediate member 66 facing the head 80. This second sealing protrusion has a second end face 112.1, which forms a second sealing surface 112.2. The first and second end faces 111.1 and 112.1 simultaneously form an intermediate valve seat 82. In the closed position of the intermediate valve member 78, the intermediate valve seat and the flat surface of the head 80 opposite to the first and second sealing protrusions 111 and 112 work together in a sealing manner. The intermediate valve seat 82 therefore includes not only the first end face 111.1 of the first sealing protrusion 111, but also the second end face 112.1 of the second sealing protrusion 112.

[0150] like Figure 4 As shown, the intermediate valve member 78 is in the closed position, in which the head 80 rests against the intermediate valve seat 82 on the first sealing surface 111.2 with its side facing the intermediate member 66 forming a first annular sealing surface 121 that is closed in the circumferential direction, and against the intermediate valve seat on the second sealing surface 112.2 with a second annular sealing surface 122 that is closed in the circumferential direction. The first radial distance r1 is here greater than the second radial distance r2 from the guide gap 74.

[0151] Figure 3 The features of the high-pressure fuel inlet 86 described herein, as well as the sealing effect of the high-pressure fuel inlet 86 and the sealing effect relative to the gap between the rod 76 and the guide clearance 74, can be applied accordingly. Figure 4 The second embodiment is shown. Specifically, the high-pressure fuel inlet 86, extending in the intermediate member 66 and connected to the high-pressure space 26, enters the annular gap space 118 in the closed position of the intermediate valve member 78. The annular gap space is constructed between the intermediate member 66 and the head 80 and is radially defined by first and second annular sealing surfaces 121, 122. As shown in... Figure 4 As can be seen, two radially opposing high-pressure fuel inlets 86 are constructed in the intermediate component 66. An additional high-pressure fuel inlet may be constructed in the intermediate component 66, for example, on a plane perpendicular to the plane of the figure, which extends through the longitudinal axis L.

[0152] As in Figure 4 As can be seen, the rod 76 has a side recess adjacent to the head 80, which forms an inner annular space 108 extending radially around the rod 76 and bounded in the intermediate member 66. An inner annular space 117 is adjacent to the inner annular space 108, which is adjacent to the rod 76 and the second annular sealing surface 122. In one embodiment, for example, an additional entry portion configured as a horizontal hole (…) Figure 4 (Not shown) can be arranged in the rod 76, and this additional access connects the blind hole 92 to the internal annular space 108 and is designed to support the opening process of the intermediate valve member 78.

[0153] exist Figure 4 In the embodiment shown, the gap between the rod 76 and the guide clearance 74 serves as a through portion for the second connection, and the intermediate valve member 78 releases this second connection between the fuel high-pressure inlet 86 and the valve space 44 in the open position. If the intermediate valve member 78 (as shown) Figure 4 (As shown) does not have an entry portion (and) that is part of the second connection portion. Figure 3 In the case of the entry portion 96), the gap between the rod 76 and the guide gap 74 is preferably larger than that in the embodiment having the entry portion, i.e., for example, larger than... Figure 3 The gap between the rod and the guide clearance. In the closed position of the intermediate valve component 78, the second sealing protrusion 112 or the second annular sealing surface 122 interrupts the second connection between the fuel high pressure inlet 86 and the valve space 44.

[0154] It is clear to those skilled in the art that in Figure 3 In this case, the gap between the rod and the guide clearance can also replace or supplement the inlet portion as part of the second connecting portion. Accordingly, in Figure 4 In this case, the entry part can also replace or supplement the gap between the rod and the guide gap as part of the second connection part.

[0155] Furthermore, a compression spring 63 is arranged centered about the longitudinal axis L between the control piston 68 and the head 80. The compression spring 63 is used to hold the intermediate valve member 78 in the closed position when the low-pressure outlet 42 is released due to the lifting of the plunger 40, by pressing the head 80 against the intermediate member 66, which is particularly effective at low system pressures of about 200 to 300 bar at engine idling.

[0156] Figure 5a A partial longitudinal section is shown of a third embodiment of the fuel injection valve 10 according to the present invention. This section presents an area of ​​the fuel injection valve 10 corresponding to... Figure 2 The rectangle marked III, wherein the specific design of this region according to the third embodiment of the fuel injection valve 10 of the present invention differs from that according to WO2016 / 041739A1. Figure 2 The fuel injection valve 10′ shown is particularly relevant to the hydraulic control device 72.

[0157] and Figure 3 Similar to the embodiment of the fuel injection valve shown, the head 80 of the intermediate valve member 78 has a first sealing ridge 111 extending around the rod 76 at a first radial distance r1 on the side of the head 80 facing the intermediate member 66. The first sealing ridge has a first end face 111.1, which forms a first sealing surface 111.2.

[0158] But with Figure 3 and 4 The embodiment of the fuel injection valve shown differs in that the second sealing surface is not formed by a sealing bulge, but by a stepped portion 127 on the side of the head 80 facing the intermediate member 66 along the longitudinal axis L, which extends around the rod 76 at a first radial distance r1. The intermediate member 66 also has a stepped portion 125 on the side facing the head 80, surrounding the guide gap 74, wherein the offset edges 125.1 and 127.1 of the stepped portions 125 and 127 radially delimit the second annular sealing surface 122 in the closed position shown for the intermediate valve member 78.

[0159] The stepped portion 127 of the head 80 is formed by a side recess, which simultaneously constructs a gap annular space 118 into which the high-pressure fuel inlet 86 enters. The stepped portion 127 has a horizontal surface forming a second sealing surface 112.2, which, in the closed position of the intermediate valve member 78, forms a second annular sealing surface 122 that is closed in the circumferential direction and is sealed against the surface 781 of the intermediate member 66 facing the head 80 along the longitudinal axis L. The surface 781 of the intermediate member 66 facing the head 80 along the longitudinal axis L thus forms an intermediate valve seat 82, and the first sealing surface 111.2 of the first sealing protrusion 111, in the closed position of the intermediate member, forms a first annular sealing surface 121 that is closed in the circumferential direction and is sealed against the intermediate valve seat.

[0160] The stepped portion 125 of the intermediate component 66 is formed by an annular gap 126, which has a rectangular cross-sectional profile along the circumferential direction. In a further variation, the annular gap 126 may have a chamfered or curved cross-sectional profile along the circumferential direction. The annular gap 126 forms an internal annular space, which is bounded by the intermediate component 66, the rod 76, and the head 80 in the closed position of the intermediate valve component 78.

[0161] exist Figure 5a It can also be seen that the discharge port 102 extends within the intermediate component 66. The intermediate component 66 is received within a blind-hole-shaped receiving cavity 151 of the intermediate body 15, which serves as the actuator receiving body 20 of the actuator assembly 38. Figure 3 and 4 Unlike other embodiments, there are no separate intermediate components and separate intermediate elements; instead, these two components are integrally constructed as a single intermediate component 66. The discharge port 102 has an inclined port section that connects the blind-hole-shaped guide gap 74 of the intermediate component 66 to the eccentrically arranged low-pressure outlet 42.

[0162] Both rod 76 and head 80 can be received in the blind-hole-shaped guide gap 74 of intermediate member 66. Guide gap 74 widens in its region facing control piston 68 into head space 128, in which head 80 can be received. The end side 84 of guide sleeve 641 facing intermediate member 66 and adjacent to intermediate member serves as a stop shoulder for head 80 in the open position of intermediate valve member 78.

[0163] However, instead of a one-piece intermediate component 66 (such as...) Figure 3 (As shown in Figure 4), separate intermediate elements and separate intermediate components can be provided. It is also conceivable that the intermediate components and guide sleeves be constructed as a single piece. Furthermore, it is also conceivable that... Figure 3Or, as shown in 4, the intermediate elements and intermediate components are constructed as a single piece.

[0164] The rod 76 has two annular protrusions 761 and 762, spaced apart from each other along the longitudinal direction L of the rod 76, surrounding the rod 76. Figure 5a (Partially highlighted by dashed lines), the rod 76 is guided in the guide gap 74 through the annular protrusions. Two throttling passages, connected in series along the longitudinal axis L and surrounding the rod 76, are constructed via annular protrusions 761 and 762. This promotes the formation of eddies and turbulence in the fluid flowing through the intermediate space between the rod 76 and the guide gap 74. A gap of at least 50 μm exists radially between the rod 76 and the guide gap 74. In a further embodiment, the gap may have a value between 70 μm and 100 μm. Due to the radial gap, the radial extension of the second annular sealing surface 122 can vary depending on the current radial position of the rod 76 in the guide gap 74. To ensure the sealing function of the intermediate valve, the maximum radial extension of the second annular sealing surface 122 is greater than the gap.

[0165] exist Figure 5a In the illustrated embodiment, the gap between the rod 76 and the guide gap 74 serves as a through portion for the second connection, which is released between the fuel high-pressure inlet 86 and the valve space 44 in the open position by the intermediate valve member 78. In the closed position of the intermediate valve member 78, the second annular sealing surface 122 interrupts the second connection between the fuel high-pressure inlet 86 and the valve space 44.

[0166] Figure 5b A partial horizontal cross-sectional view of another embodiment of the fuel injection valve according to the invention is shown, wherein this embodiment of the fuel injection valve is based on... Figure 5a The illustrated embodiment is implemented. For this reason, in... Figure 5a Line AA is shown in the middle. Figure 5b The cross-section shown is obtained along this line. Therefore, Figure 5b Show Figure 5a An embodiment of the fuel injection valve shown is described. Figure 5b As can be seen, the second annular protrusion 762 has three chamfers 762.1, 762.2, and 762.3 along the circumferential direction, which form an intermediate space 119 (or three corresponding intermediate spaces) between the rod 76 or the annular protrusion 762 and the guide gap 74. Although in Figure 5bWhile not visible in the center, the first annular protrusion 761 also has a corresponding chamfer along the circumferential direction. The chamfers 762.1-3 of the second annular protrusion 762 (and the chamfer of the first annular protrusion) provide a passage formed by the intermediate space 119 between the chamfer and the guide gap 74, which serves as a through-hole for the second connecting portion. Furthermore, due to the chamfers 762.1-3 (and the chamfer of the first annular protrusion) and the through-hole provided by this second connecting portion, the gap between the rod 76 and the guide gap 74 can be kept smaller than that for... Figure 5a The gaps in the described embodiment result in better rod centering. The three chamfers 762.1-3 (and the chamfer of the first annular protrusion) are arranged at an angle 120° apart from each other. However, other arrangements are also conceivable, especially embodiments with one chamfer per annular protrusion or two or more chamfers per annular protrusion.

[0167] Furthermore, the rod can also be used without the annular protrusion, for example in... Figure 3 or Figure 4 In a particular embodiment of the fuel injection valve shown, there is at least one, two, or three chamfers in the circumferential direction, thereby forming a passage for the second connection portion again through the intermediate space between the one or more chamfers and the guide gap.

[0168] Figure 6 A partial longitudinal section is shown of a fourth embodiment of the fuel injection valve 10 according to the present invention. This section presents an area of ​​the fuel injection valve 10 corresponding to... Figure 2 The rectangle marked III, wherein the specific design of this region according to the fourth embodiment of the fuel injection valve 10 of the present invention differs from that according to WO2016 / 041739A1. Figure 2 The fuel injection valve 10′ shown is particularly relevant to the hydraulic control device 72.

[0169] The intermediate valve member 78 has a valve space through-hole 441 connected to the valve space 44, which includes a hole 441.1 parallel to the longitudinal axis L and a horizontal hole 441.2. The valve space through-hole 441 connects the blind hole 92 of the intermediate valve member 78 connected to the valve space 44 to a clearance annular space 118, which is constructed between the intermediate member 66 and the head 80 in the indicated closed position of the intermediate valve member 78 and is radially defined by first and second annular sealing surfaces 121, 122. The hole 441.1 parallel to the longitudinal axis L opens into the clearance annular space 118 at its first end and into the horizontal hole 441.2 at its second end. The horizontal hole 441.2, in turn, opens into the blind hole 92 at its first end. Figure 5aAs can be seen, the second end of the horizontal hole 441.2 is sealed by a plug 441.3. In a variant, the intermediate valve member 78 or the head 80 has an additional valve space through-hole 441, which... Figure 5a The horizontal hole 441.2 of the additional valve space through-part 441, shown in dashed line, is not sealed separately by a plug, because the horizontal hole 441.2 shown in dashed line can be drilled together with the horizontal hole 441.2 shown in solid line on the left.

[0170] In the open position, the intermediate valve member 78 is released through the orifice 441.1 at the second connection between the high-pressure fuel inlet 86 and the blind orifice 92 or valve space 44, so that the blind orifice 92 or valve space 44 can be filled with fuel. In the closed position, the second annular sealing surface 122 interrupts the second connection between the high-pressure fuel inlet 86 and the valve space 44.

[0171] and Figure 3 The embodiments shown in 5 are different, according to Figure 6 In the embodiment shown, the high-pressure fuel inlet 86 enters an annular space 120 defined by the intermediate member 66, the rod 76, and the end cap 80 in the closed position of the intermediate valve member 78. The annular space 120 is adjacent to the second annular sealing surface 122 in the closed position of the intermediate valve member 78 and is arranged to be closer to the rod 76 in the radial direction than the second annular sealing surface 122.

[0172] The annular space 120 has an inner annular space 108 that extends around the rod 76 and is radially bounded by the rod 76 and the intermediate member 66, the inner annular space being recessed at the rod 76 itself. A high-pressure fuel inlet 86 opens into the inner annular space 108. The annular space 120 also has a gap annular space 117 adjacent to the inner annular space 108, which, in the closed position of the intermediate valve member 78, is constructed through a surrounding gap between the intermediate member 66 and the head 80 and is radially adjacent to the second annular sealing surface 122. The inner annular space 108 is formed by a surrounding, radially outwardly opening annular groove having a trapezoidal cross-section, wherein the inclinedly extending side faces away from the head 80.

[0173] The rod 76 is guided in the guide gap 74 with a tight sliding fit of approximately 3 μm to 10 μm. The diameter of the vertical hole 441.1 of the valve space through-hole 441 is larger than the diameter of the throttling through-hole 90, and when the intermediate valve member 78 moves away from the closed position, the blind hole 92 and the valve space 44 can be quickly filled.

[0174] In one variation, the secondary through-hole 97 is constructed on the intermediate component 66, such as Figure 6As shown by the dashed line. When the plunger 40 closes the low-pressure outlet 42 and separates the valve space 44 from the low-pressure fuel return section 46, the secondary through section 97 connects the high-pressure space 26 to the valve space 44 and supports the opening process of the intermediate valve component 78.

[0175] Figure 7 A partial longitudinal section is shown of a fifth embodiment of the fuel injection valve 10 according to the present invention. This section presents an area of ​​the fuel injection valve 10 corresponding to... Figure 2 The rectangle marked III, wherein the specific design of this region according to the fifth embodiment of the fuel injection valve 10 of the present invention differs from that according to WO2016 / 041739A1. Figure 2 The fuel injection valve 10′ shown is particularly relevant to the hydraulic control device 72.

[0176] and Figure 6 Compared to the fourth embodiment shown, the valve space through portion 441 has a hole 441.1 that is inclined relative to the longitudinal axis L. Due to the inclined hole 441.1, compared to the embodiment shown... Figure 6 Compared to the fourth embodiment, the first sealing protrusion 111 can be arranged radially further away from the rod 76 without reducing the size of the plug 441.3. The valve space through-hole 441 extends into the gap annular space 118 via an inclined hole 441.1, the gap annular space being defined by the head 80, the intermediate member 66, and the first and second annular sealing surfaces 121, 122. Figure 6 In the fourth embodiment shown, the horizontal hole 441.2 extends into the blind hole 92 at one end.

[0177] In addition, with Figure 6 Compared to the fourth embodiment shown, the inner annular space 108 of the annular space 120 is limited not only by the gap on the rod 76 but also by the gap on the intermediate member 66. The gap annular space 117 is adjacent to the inner annular space 108, which is formed by the surrounding gap between the intermediate portion 66 and the head 80 in the closed position of the intermediate valve member 78 and is radially adjacent to the second annular sealing surface 122.

[0178] An optional secondary through-hole 97 is shown in dashed lines. This secondary through-hole is constructed on the rod 76 through a straight horizontal hole and connects the high-pressure space 26 or the fuel high-pressure inlet 86 to the blind hole 92 through the annular space 120.

[0179] and Figure 6 Compared to the fourth embodiment shown, the first and second sealing bulges 111 and 112 are constructed to be higher in the longitudinal direction L, thereby giving the annular gap space 118 a greater depth in the longitudinal direction L.

[0180] Furthermore, the intermediate component 66 is designed as a one-piece component, including an outlet 102 with an inclined hole extending within this one-piece component, similar to... Figure 5a However, instead of the one-piece intermediate component 66, separate intermediate elements and separate intermediate components can be provided, such as... Figure 6 As shown in the image. However, it is also conceivable that... Figure 6 The intermediate elements and intermediate components are constructed as a single unit.

[0181] Similar to Figure 6 As shown, an additional valve space through-section can be provided, which is shown in dashed lines in the right region of the head 80.

[0182] The rod 76 is guided in the guide gap 74 with a tight sliding fit of approximately 3 μm to 10 μm. The diameter of the inclined hole 441.1 of the valve space through-part 441 is larger than the diameter of the throttling through-part 90, and when the intermediate valve member 78 moves away from the closed position, the blind hole 92 and the valve space 44 can be quickly filled.

[0183] In the open position, the intermediate valve member 78 is released through the orifice 441.1 at the second connection between the high-pressure fuel inlet 86 and the blind orifice 92 or valve space 44, allowing the blind orifice 92 or valve space 44 to be filled with fuel. In the closed position, the second annular sealing surface 122 interrupts the second connection between the high-pressure fuel inlet 86 and the valve space 44.

[0184] Starting from the closed position of the intermediate valve 83 shown in the figure, in order to initiate injection, the plunger 40 is lifted from the intermediate element 98 or intermediate component 66 by means of the electromagnet of the actuator assembly 38, thereby releasing the low-pressure outlet 42. This causes the amount of fuel flowing out of the valve space 44 into the low-pressure fuel return section 46 per unit time to be greater than the amount of fuel flowing back into the valve space 44 through the throttling through-hole 90 and the possibly present secondary through-hole 97. As a result, the pressure in the valve space 44 drops, which causes: on the one hand, the intermediate valve component 78 presses against the intermediate component 66 with the resulting compressive force to keep the intermediate valve 83 reliably closed, and on the other hand, the pressure in the control space 70 drops. This, in turn, causes: the action of the double-acting control piston 68 to lift the injection valve component 56 against the force of the compression spring 62' from the injection valve seat 18', thereby initiating fuel injection into the combustion chamber of the internal combustion engine.

[0185] To terminate the injection, the plunger 40 is brought against the intermediate element 98 or intermediate component 66, thereby closing the low-pressure outlet 42. The pressure in the valve space 44 increases by the fuel flowing in through the throttling through-hole 90 and, if present, the secondary through-hole 97, causing the intermediate valve member 78 to move away from the intermediate valve seat 82. Once the intermediate valve member 78 has performed its minimum opening movement, this movement is further supported because the resulting annular cross-section rapidly and significantly exceeds the cross-section of the inlet 96, and, for example, in… Figure 3 In the illustrated embodiment, the internal annular space 117 is filled. In the embodiment where the fuel high-pressure inlet 86 enters the gap annular space 118, the high system pressure in the gap annular space 118 supports the opening movement of the intermediate valve member 78. If there is an increased gap between the rod 76 and the guide gap 74, fuel flows into the valve space 44 during the opening movement of the intermediate valve member 78, and the valve space is rapidly filled with fuel once the seal of the annular sealing surfaces 121, 122 is released.

[0186] In the embodiment where the valve space through-part 441 enters the annular space 118, when the head 80 is lifted from the closed position of the intermediate valve member 78, the valve space 44 can be quickly filled with fuel flowing into the valve space through-part 441, thereby supporting the opening movement of the intermediate valve member 78.

[0187] By lifting the head 80 of the intermediate valve member 78 from the intermediate component 66, a large flow cross-section from the high-pressure fuel inlet 86 to the control space 70 is also rapidly released, resulting in the rapid termination of the injection process by causing the injection valve member 56 to move rapidly toward and abut against the injection valve seat 18.

Claims

1. A fuel injection valve (10) for intermittently injecting fuel into the combustion chamber of an internal combustion engine, the fuel injection valve comprising: A housing (12′) defining a longitudinal axis (L), the housing having a high-pressure fuel inlet (24′) and an injection valve seat (18′). A high-pressure space (26) is arranged in the housing (12′), which extends from the fuel high-pressure inlet (24′) to the injection valve seat (18′). The injection valve component (56) is adjustablely arranged in the housing (12′) along the longitudinal axis (L), and the injection valve component works together with the injection valve seat (18′). A compression spring (62′) loads the injection valve component (56) with a closing force pointing toward the injection valve seat (18′). The control piston (68) of the guide component (64) and the injection valve component (56) is guided in a sliding fit within the guide component. Intermediate component (66), together with guide component (64) and control piston (68), defines control space (70). A hydraulic control device (72) for controlling the axial movement of the injection valve component (56) by changing the pressure in the control space (70), the hydraulic control device having an intermediate valve (83) comprising: a mushroom-shaped intermediate valve component (78) and an intermediate valve seat (82), the intermediate valve component having a rod (76) guided in a guide gap (74) of an intermediate component (66) and a head (80), the intermediate valve seat being constructed on the side of the intermediate component (66) facing the head (80) and acting in conjunction with the head (80), wherein, in the open position, the intermediate valve component (78) releases a first connection between the fuel high-pressure inlet (86) connected to the high-pressure space (26) and the control space (70), and in the closed position, interrupts the first connection between the fuel high-pressure inlet (86) and the control space (70), and separates the control space (70) from the valve space (44) – except for the throttling through-hole (90). An electrically operated actuator assembly (38) for connecting the valve space (44) to the low-pressure fuel return section (46) and for separating the valve space (44) from the low-pressure fuel return section. In the open position, the intermediate valve component (78) releases the second connection between the high-pressure fuel inlet (86) and the valve space (44), and in the closed position, it interrupts the second connection between the high-pressure fuel inlet (86) and the valve space (44). The head (80), in the closed position of the intermediate valve member (78), rests against the intermediate valve seat (82) on a first sealing surface (111.2) with a first annular sealing surface (121) that is closed in the circumferential direction, and on a second sealing surface (112.2) with a second annular sealing surface (122) that is closed in the circumferential direction, the first sealing surface extending about the rod (76) or the guide gap (74) at a first radial distance (r1), the second sealing surface extending about the rod (76) or the guide gap (74) at a second radial distance (r2), wherein the first radial distance (r1) is greater than the second radial distance (r2). The high-pressure fuel inlet (86) extends within the intermediate component (66) such that, in the closed position of the intermediate valve member (78), the high-pressure fuel inlet (86) passes into the annular gap space (118), which, in the closed position of the intermediate valve member (78), is constructed between the intermediate component (66) and the head (80) and is radially bounded by a first annular sealing surface (121) and a second annular sealing surface (122). The second connection includes an inlet (96) of the intermediate valve member (78), the inlet extending into the valve space (44) at a first end and extending to the outside of the intermediate valve member (78) at a second end. The inlet (96) extends to the outside of the intermediate valve member (78) at its second end, such that the second end is arranged in the closed position of the intermediate valve member (78) with a smaller radial distance from the rod (76) compared to the second annular sealing surface (122).

2. The fuel injection valve (10) according to claim 1, characterized in that, The second connection extends between the fuel high-pressure inlet (86) and the hole (92) of the rod (76) extending through the intermediate valve member (78), which is part of the valve space (44).

3. The fuel injection valve (10) according to claim 1, characterized in that, A first annular sealing protrusion (111) is constructed on the side of the head (80) facing the intermediate component (66) or on the side of the intermediate component (66) facing the head (80), the first annular sealing protrusion having a first end side (111.1) and the first end side forming a first sealing surface (111.2).

4. The fuel injection valve (10) according to any one of claims 1 to 3, characterized in that, A second annular sealing protrusion (112) is constructed on the side of the head (80) facing the intermediate component (66) or on the side of the intermediate component (66) facing the head (80), the second annular sealing protrusion having a second end side (112.1) and the second end side forming a second sealing surface (112.2).

5. The fuel injection valve (10) according to any one of claims 1 to 3, characterized in that, The intermediate component (66) has at least one stepped portion (125) on the side facing the head (80), and the head (80) has at least one stepped portion (127) on the side facing the intermediate component (66), wherein, in the closed position of the intermediate valve component (78), the mutually offset edges (125.1, 127.1) of the stepped portions of the intermediate component (66) and the head (80) are respectively radially upper bounded by a first annular sealing surface (121) and / or a second annular sealing surface (122).

6. The fuel injection valve (10) according to claim 5, characterized in that, The stepped portion (125) of the intermediate component (66) forms an internal annular space (126), which is bounded by the intermediate component (66), the rod (76) and the head (80) in the closed position of the intermediate valve component (78).

7. The fuel injection valve (10) according to any one of claims 1 to 3, characterized in that, The second connection includes a through portion formed by a gap of at least 10µm between the rod (76) and the guide gap (74) in the radial direction.

8. The fuel injection valve (10) according to any one of claims 1 to 3, characterized in that, The rod (76) has two annular protrusions (761, 762) spaced apart from each other in the longitudinal direction of the rod (76).

9. The fuel injection valve (10) according to claim 8, characterized in that, The annular protrusions (761, 762) each have at least one chamfer (762.1, 762.2, 762.3) in the circumferential direction, wherein the second connecting portion includes a through portion formed by an intermediate space (119) between the at least one chamfer (762.1, 762.2, 762.3) and the guide gap (74).

10. The fuel injection valve (10) according to claim 9, characterized in that, The annular protrusions (761, 76) have two or three chamfers (762.1, 762.2, 762.3) along the circumferential direction.

11. The fuel injection valve (10) according to any one of claims 1 to 3, characterized in that, The rod (76) has at least one chamfer along the circumferential direction, wherein the second connection includes a through portion formed by an intermediate space between the at least one chamfer and the guide gap (74).

12. The fuel injection valve (10) according to any one of claims 1 to 3, characterized in that, The second connection includes a hole extending through the head (80) of the intermediate valve member (78), the hole forming a valve space through-hole connected to the valve space (44) and opening at one end to the side of the head (80) facing the intermediate member (66).

13. The fuel injection valve (10) according to claim 12, characterized in that, The valve space through-part extends in the intermediate valve member (78) such that the valve space through-part opens into the gap annular space (118) in the closed position of the intermediate valve member (78), the gap annular space being constructed between the intermediate part (66) and the head (80) in the closed position of the intermediate valve member (78) and being radially bounded by the first annular sealing surface (121) and the second annular sealing surface (122).

14. The fuel injection valve (10) according to claim 12, characterized in that, The fuel injection valve has an annular space (120) in the closed position of the intermediate valve member (78) by an intermediate component (66), a rod (76) and a head (80), into which a high-pressure fuel inlet (86) enters.

15. The fuel injection valve (10) according to claim 7, characterized in that, The gap is between 20µm and 50µm.

16. A fuel injection valve (10) for intermittently injecting fuel into the combustion chamber of an internal combustion engine, the fuel injection valve comprising: A housing (12′) defining a longitudinal axis (L), the housing having a high-pressure fuel inlet (24′) and an injection valve seat (18′). A high-pressure space (26) is arranged in the housing (12′), which extends from the fuel high-pressure inlet (24′) to the injection valve seat (18′). The injection valve component (56) is adjustablely arranged in the housing (12′) along the longitudinal axis (L), and the injection valve component works together with the injection valve seat (18′). A compression spring (62′) loads the injection valve component (56) with a closing force pointing toward the injection valve seat (18′). The control piston (68) of the guide component (64) and the injection valve component (56) is guided in a sliding fit within the guide component. Intermediate component (66), together with guide component (64) and control piston (68), defines control space (70). A hydraulic control device (72) for controlling the axial movement of the injection valve component (56) by changing the pressure in the control space (70), the hydraulic control device having an intermediate valve (83) comprising: a mushroom-shaped intermediate valve component (78) and an intermediate valve seat (82), the intermediate valve component having a rod (76) guided in a guide gap (74) of an intermediate component (66) and a head (80), the intermediate valve seat being constructed on the side of the intermediate component (66) facing the head (80) and acting in conjunction with the head (80), wherein, in the open position, the intermediate valve component (78) releases the connection between the high-pressure fuel inlet (86) connected to the high-pressure space (26) and the control space (70), and in the closed position, interrupts the connection between the high-pressure fuel inlet (86) and the control space (70), and separates the control space (70) from the valve space (44) – except for the throttling through-hole (90). An electrically operated actuator assembly (38) for connecting and separating the valve space (44) from the low-pressure fuel return section (46), wherein the head (80), in the closed position of the intermediate valve member (78), rests against the intermediate valve seat (82) on a first sealing surface (111.2) with a first annular sealing surface (121) that is closed in the circumferential direction, and against the intermediate valve seat on a second sealing surface (112.2) with a second annular sealing surface (122) that is closed in the circumferential direction, the first sealing surface extending about the rod (76) or the guide gap (74) at a first radial distance (r1), and the second sealing surface extending about the rod (76) or the guide gap (74) at a second radial distance (r2), wherein the first radial distance (r1) is greater than the second radial distance (r2). The intermediate valve member (78) has a valve space through-hole (441) connected to the valve space (44), the valve space through-hole extending in the intermediate valve member (78) such that the valve space through-hole (441) passes into a gap annular space (118) in the closed position of the intermediate valve member (78), the gap annular space being constructed between the intermediate component (66) and the head (80) in the closed position of the intermediate valve member (78) and being radially limited by a first annular sealing surface (121) and a second annular sealing surface (122).

17. The fuel injection valve (10) according to claim 16, characterized in that, The high-pressure fuel inlet (86) extends in the intermediate component (66) such that the high-pressure fuel inlet (86) passes into the gap annular space (118) in the closed position of the intermediate valve component (78), the gap annular space being constructed between the intermediate component (66) and the head (80) in the closed position of the intermediate valve component (78) and being radially limited by a first annular sealing surface (121) and a second annular sealing surface (122).

18. The fuel injection valve (10) according to claim 17, characterized in that, The rod (76) is guided in a sliding fit within a guide gap (74) of the intermediate component (66), wherein there is a gap of at least 10 µm in the radial direction between the rod (76) and the guide gap (74).

19. The fuel injection valve (10) according to claim 17 or 18, characterized in that, The intermediate valve member (78) has an inlet (96) that extends into the valve space (44) at a first end and to the outside of the intermediate valve member (78) at a second end, such that the second end is arranged in the closed position of the intermediate valve member (78) with a smaller radial distance from the rod (76) compared to the second annular sealing surface (122).

20. The fuel injection valve (10) according to claim 17 or 18, characterized in that, The rod (76) has at least one surrounding annular protrusion, through which the rod (76) is guided in the guide gap (74).

21. The fuel injection valve (10) according to claim 20, characterized in that, The rod (76) has two annular protrusions (761, 762) spaced apart from each other in the longitudinal direction of the rod (76).

22. The fuel injection valve (10) according to claim 21, characterized in that, The rod (76) is guided in the guide gap (74) of the intermediate component (66) such that there is a gap of at least 50 μm in the radial direction between the rod (76) and the guide gap (74).

23. The fuel injection valve (10) according to any one of claims 16 to 18, characterized in that, The fuel injection valve has an annular space (120) in the closed position of the intermediate valve member (78) by an intermediate component (66), a rod (76) and a head (80), into which a high-pressure fuel inlet (86) enters.

24. The fuel injection valve (10) according to any one of claims 16 to 18, characterized in that, The valve space through-part (441) has a hole (441.1) in the head (80) that is parallel to or inclined relative to the longitudinal axis (L), the hole opening into the gap annular space (118) in the closed position of the intermediate valve member (78).

25. The fuel injection valve (10) according to any one of claims 16 to 18, characterized in that, A first annular sealing protrusion (111) is constructed on the side of the head (80) facing the intermediate component (66) or on the side of the intermediate component (66) facing the head (80), the first annular sealing protrusion having a first end side (111.1) and the first end side forming a first sealing surface (111.2).

26. The fuel injection valve (10) according to any one of claims 16 to 18, characterized in that, A second annular sealing protrusion (112) is constructed on the side of the head (80) facing the intermediate component (66) or on the side of the intermediate component (66) facing the head (80), the second annular sealing protrusion having a second end side (112.1) and the second end side forming a second sealing surface (112.2).

27. The fuel injection valve (10) according to any one of claims 16 to 18, characterized in that, The intermediate component (66) has at least one stepped portion (125) on the side facing the head (80), and the head (80) has at least one stepped portion (127) on the side facing the intermediate component (66), wherein, in the closed position of the intermediate valve component (78), the mutually offset edges (125.1, 127.1) of the stepped portions of the intermediate component (66) and the head (80) are respectively radially upper bounded by a first annular sealing surface (121) and / or a second annular sealing surface (122).

28. The fuel injection valve (10) according to claim 27, characterized in that, The stepped portion (125) of the intermediate component (66) forms an internal annular space (126), which is bounded by the intermediate component (66), the rod (76) and the head (80) in the closed position of the intermediate valve component (78).

29. The fuel injection valve (10) according to any one of claims 16 to 18, characterized in that, The rod (76) is continuously guided in the guide gap (74) of the intermediate component (66).

30. The fuel injection valve (10) according to claim 18, characterized in that, The gap is between 20µm and 50µm.

31. The fuel injection valve (10) according to claim 22, characterized in that, The gap is between 70 μm and 100 μm.

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