EP1939515A1 - High pressure seal - Google Patents

Abstract

The sealing (1) has casing (9) inserted from a side (6) into a hole (4), and a retainer pin (11) placed in another side (7) opposite to the side (6) in the casing, where outer diameter of a pressing element (12) is greater than an inner diameter of a bind hole (19) of the retainer pin. The pressing element is press-fitted in the blind hole so that a form closure is formed between an angular toothed profile (14) of the casing and a body (3) in a region of the hole. A collar of the retainer pin is pressed at the side (7) directly against the body. An independent claim is also included for a fuel injection valve comprising a high pressure sealing.

Description

State of the art

The invention relates to a high-pressure seal, in particular a high-pressure seal for a fuel injection valve and a fuel injection valve with such a high-pressure seal. Specifically, the invention relates to the field of injectors for fuel injection systems of air compressing, self-igniting internal combustion engines.

From the WO 03/026033 A1 a device with a piezoelectric actuator for a fuel injection valve is known. The piezoelectric actuator has two end faces and two electrically conductive contact tracks, each of which passes through the actuator, starting from an end face. The actuator is clamped between two metallic plates, each of which is arranged on an end face. Furthermore, an electrically insulating insulating layer is arranged between each end face and the plate arranged there. Through one of the metallic plates, the electrically conductive contact paths are guided.

The from the WO 03/026033 A1 known device has the disadvantage that the seal against fuel under high pressure is limited. Unless the device is in an actuator space is used, is provided in the high-pressure fuel, there is the problem that compared to a non-pressurized outer side to which the electrically conductive contact paths are guided, a high pressure difference occurs, which is difficult to seal.

For sealing, it is conceivable, for example, for holes through which the electrically conductive contact paths are made to be filled up with a glass enamel functioning as an insulator. For example, a metal body having the holes, and surrounding the bore of glass sleeves electrically conductive contact paths can be heated together to the melting point of the glass, wherein after a subsequent quenching the seal is formed, which results from the tension, the is due to the different thermal expansion coefficients of the materials. It is conceivable that the entire unit is then provided with a nickel-gold coating and is pressed in a conical bore from the high pressure side. However, this system has the disadvantage that the handling is complex, since a variety of different manufacturing steps, additional complex contacts and possibly an additional isolation process to prevent an electrical short circuit or a voltage-induced flashover is required. In addition, due to vibrations, pressure fluctuations or other reasons, the seal may be damaged, in particular in the area of glass melting.

Disclosure of the invention

The high-pressure seal according to the invention with the features of claim 1 and the fuel injection valve according to the invention with the features of claim 13 have the advantage that a reliable high-pressure seal is created, which has a high mechanical stability and is also suitable for high pressures.

The measures listed in the dependent claims advantageous refinements of the specified in claim 1 high-pressure seals and the fuel injection valve specified in claim 13 are possible.

Advantageously, an arrangement of the high-pressure seal in which the high-pressure medium is provided on the second side, so that the force with which the collar is pressed against the body, increases with the pressure of the medium. This results in a self-reinforcing sealing effect, so that a reliable seal is ensured. An additional sealing effect can also be formed by the positive connection between the helical profile of the sleeve and the body in the region of the bore by the helical profile additionally ensures a circumferential seal.

Advantageously, the pressing element is designed as a spherical pressing element. As a result, the pressing element can be easily manufactured and also simply pressed into the blind bore of the sealing bolt.

It is also advantageous that the pressing element has a barrel-shaped injection body, which is pressed into the blind bore. Furthermore, it is advantageous for the pressing element to have a contact element which For example, designed as a rod-shaped contact plug. The barrel-shaped configuration of the pressing body ensures the positioning of the contact element with respect to the blind bore, to allow the contacting of the contact element and to prevent, for example, short circuits. This results in many possibilities for contacting the contact element.

Advantageously, an electrically insulating insulating means is provided which electrically isolates the sealing bolt against the body. As a result, an embodiment of the sealing bolt and the body and possibly other elements made of metallic and thus electrically conductive materials is possible. This allows for a seal against high pressures with relatively inexpensive materials and on the other hand, a high media resistance, especially against fuel. It is advantageous that the insulating means is formed of an electrically insulating coating. Preferably, the electrically insulating coating is applied to the sealing bolt, which can be done relatively inexpensively. The electrically insulating coating can be formed, for example, from Teflon.

It is advantageous that the electrically insulating coating in a sealing region has a layer thickness which is not greater than an extrusion limit thickness. Especially in the sealing area occur relatively large forces, whereby an extrusion can occur. In order to prevent this extrusion of the insulating material on the sealing surface by the applied pressure, the maximum layer thickness, that is, the extrusion limit thickness, is preferably defined by the ratio of the layer thickness to the bolt diameter. At a Material combination of steel and Teflon results for the ratio of the extrusion limit thickness to the bolt diameter a value of, for example, 1/150 with the friction coefficient of the mating Teflon to steel of μ ₀ = 0.08.

It is advantageous that the collar of the sealing bolt has a biting edge on which sealing bolts are pressed against the body. The pressing can also be done indirectly, in particular via the insulating layer. This has the advantage that a defined seal is formed, which has a high pressure resistance, wherein a self-reinforcing seal is achieved by the application of the federal government of the sealing bolt with the fuel under high pressure.

It is also advantageous that the sealing bolt has a contact element which is formed by a blind bore. As a result, a simple contacting of the high-pressure seal on the side of the sealing bolt is possible. Other embodiments of the contact element are advantageous, for example, the configuration as a rod-shaped contact plug, which is provided on the side of the collar of the sealing bolt.

It is advantageous that the bore provided in the body is designed as a stepped bore, wherein the sleeve is inserted at least substantially up to a step of the stepped bore in the stepped bore, so that the assembly of the high-pressure seal simplified and a reliable sealing effect is ensured in the assembled state ,

Brief description of the drawings

Preferred embodiments of the invention are explained in more detail in the following description with reference to the accompanying drawings, in which corresponding elements are provided with corresponding reference numerals.

• Fig. 1 eine Hochdruckabdichtung in einer schematischen Schnittdarstellung entsprechend einem ersten Ausführungsbeispiel der Erfindung vor einer Montage;
• Fig. 2 die in Fig. 1 dargestellte Hochdruckabdichtung im teilmontierten Zustand;
• Fig. 3 die in Fig. 1 dargestellte Hochdruckabdichtung im montierten Zustand;
• Fig. 4 den in Fig. 3 mit IV bezeichneten Ausschnitt der Hochdruckabdichtung des ersten Ausführungsbeispiels;
• Fig. 5 eine Hochdruckabdichtung in einer schematischen Schnittdarstellung entsprechend einem zweiten Ausführungsbeispiel und
• Fig. 6 ein Brennstoffeinspritzventil mit einer Hochdruckabdichtung entsprechend einem dritten Ausführungsbeispiel der Erfindung in einer schematischen Schnittdarstellung.

It shows:

• Fig. 1 a high-pressure seal in a schematic sectional view according to a first embodiment of the invention prior to assembly;
• Fig. 2 in the Fig. 1 illustrated high-pressure seal in the partially assembled state;
• Fig. 3 in the Fig. 1 illustrated high-pressure seal in the assembled state;
• Fig. 4 the in Fig. 3 labeled IV section of the high pressure seal of the first embodiment;
• Fig. 5 a high pressure seal in a schematic sectional view according to a second embodiment and
• Fig. 6 a fuel injection valve with a high pressure seal according to a third embodiment of the invention in a schematic sectional view.

Embodiments of the invention

Fig. 1 shows a high-pressure seal 1 according to a first embodiment of the invention prior to assembly. The high-pressure seal 1 is particularly suitable for a fuel injection valve 2, as it is also in Fig. 6 is shown schematically. The high-pressure seal is used specifically for sealing a high-pressure fuel to atmospheric pressure, the high-pressure seal 1 allows the passage of electrical signals or electrical energy. The high pressure seal 1 can serve to seal very high pressures, for example, about 200 MPa (2000 bar). A preferred use of the fuel injection valve 2 is for a fuel injection system with a common rail, which leads diesel fuel under high pressure to a plurality of fuel injection valves 2. However, the high-pressure seal 1 according to the invention and the fuel injection valve 2 according to the invention are also suitable for other applications.

The high-pressure seal 1 is used to seal a provided in a body 3 bore 4, which is designed as a stepped bore 4 and at least one stage 5 has. The body 3 has a first side 6 and a second side 7 opposite the first side 6. In operation, there is a high pressure against the first side 6 on the second side 7. For example, can be located on the second side 7 under high pressure fuel, while on the first side 6 there is atmospheric pressure. The high-pressure seal 1 is mounted so that a seal of the pressure acting on the second side 7 is ensured compared to the relatively low pressure on the first side 6. The bore 4 has from the first side 6 forth to level 5 a diameter a, wherein a bevägter Section 8 may be provided. In the part of the bore 4 with the diameter a, a sleeve 9 is introduced from the first side 6, as illustrated by the arrows 10. Furthermore, the high-pressure seal 1 has a sealing bolt 11 and a compression element 12. The sleeve 9 is inserted into the bore 4 in such a way that the sleeve 9 is supported on the step 5. The sleeve 9 has on an outer side 13 a helical profile 14 which is inclined slightly against the insertion direction represented by the arrows 10.

Fig. 2 shows the high-pressure seal 1 in the partially assembled state, wherein the sleeve 9 is inserted into the bore 4. An outer diameter of the outer side 13 of the sleeve 9 corresponds substantially to the diameter a of the bore 4 to the step 5. The sleeve 9 also has a bore 15 which has a diameter b. The bore 15 may already be formed prior to insertion of the sleeve 9. However, the bore 15 can be drilled only after the introduction of the sleeve 9 in the bore 4 to achieve an alignment of the bore 15 in the direction of an axis 16 of the high-pressure seal 1 with relatively high accuracy.

In the in the Fig. 2 shown partially assembled state is introduced from the second side 7 of the sealing bolt 11 in the bore 4 and the sleeve 9. An outer diameter of an outer side 17 of the sealing bolt 11 is substantially equal to the diameter b of the bore 15 of the sleeve 9. The sealing bolt 11 is inserted so far into the sleeve 9 until a collar 18 of the sealing bolt 11 on the second side 7 of the body 3 is present.

The sealing bolt 11 has a blind bore 19, which has an inner diameter d substantially. Of the Inner diameter d of the blind bore 19 is slightly smaller than an outer diameter c of the compression element 12, which is designed as a spherical compression element 12. The pressing element 12 is inserted into the blind bore 19 after the assembly of the sealing bolt 11. As a result, the sealing bolt 11 is expanded in the region of the blind bore 19, so that the diameter of the outer side 17 increases. Thus, the sleeve 9 is also expanded, so that the helical profile 14 at least slightly penetrates into the body 3 and a positive connection between the sleeve 9 and the body 3 is created.

Fig. 3 shows the high-pressure seal 1 in the mounted state in which the pressing element 12 is inserted into the blind bore 19 of the sealing bolt 11. Due to the excess of the spherical compression element 12 to the inner diameter d of the blind bore 19 of the sealing pin 11 is deformed in the region of the blind bore 19 and thus also the sleeve 9 in the helical teeth 14, in particular extended. At the same time the deformation caused by the engagement of the helical profile 14 in the body 3, a tensile stress in a lower portion 20 of the sealing bolt 11, so that the collar 18 is pressed against the body 3 , Furthermore, the pressure of the fuel on the second side 7 of the body 3, which is illustrated by the arrows 21, in a normal force F _N on the collar 18 of the sealing pin 11 in the direction of the axis 16 acts. This normal force F _N causes an additional enhancement of the sealing effect, as determined by the Fig. 4 is further explained in detail. Since the normal force F _{N is} pressure-dependent, this results in a self-reinforcing sealing effect of the high-pressure seal 1.

The sealing bolt 11 is also partially coated with an electrically insulating coating 25 which constitutes an electrically insulating insulating means, which is an electrically insulating material or an electrically insulating material, between the sealing bolt 11 and the body 3. The electrically insulating coating 25 prevents an electrical short circuit between the sealing bolt 11 and the body 4. Thus, both from the first side 6 and from the second side 7 made an electrical contact with the sealing bolt 11, for example, an electrical energy from the first Page 6 to the second page 7 to lead, without causing a short circuit to the body 3. The connection of an electrical consumer can then take place on the one hand via the high-pressure seal 1 and on the other hand via the body 3. However, it is also possible to provide a plurality of high-pressure seals 1, wherein a connection to an electrical positive pole is made via a high-pressure seal and a connection to an electrical negative pole via another high-pressure seal.

Fig. 4 shows the in Fig. 3 labeled IV section of the high pressure seal 1 of the first embodiment. The sealing bolt 11 has in the region of an edge 26 of the body 3, which is formed through the bore 4 in the body 3 toward the second side 7, a recess 27, so that the sealing bolt 11 in the region of the edge 26 spaced from the body. 3 is. Further, the collar 18 of the sealing bolt 11 to the second side 7 of the body 3 toward a negative angle with respect to its radial extent, so that the collar 18 rests against a sealing edge 30 of the collar 18 on the second side 7 of the body 3. Due to the coating 25 is this system indirectly, so that the sealing surface 31 is formed at the sealing edge 30 between the coating 25 and the body 3. The sealing surface 31 serves to seal against the fuel pressure, which generates a force F _D in the region of the sealing edge 30. The layer thickness h of the coating 25 is less than or equal to an extrusion limit thickness in order to prevent extrusion of the coating 25 on the sealing surface 31 by the applied pressure. The determination of the layer thickness h as extrusion boundary thickness is shown below by way of example.

The effective pressure surface A _{B of} the sealing bolt 11 results from the in Fig. 3 illustrated outer diameter e of the collar 18 of the sealing bolt 11 and the Ludolph number π to: $${\mathrm{A}}_{\mathrm{B}}=\mathbf{\pi }*{\mathrm{<figure-callout\; id="2"\; label="e"\; filenames="imgf0004.png"\; state="\{\{state\}\}">e</figure-callout>}}^{\mathrm{2}}\mathrm{/}\mathrm{4th}$$

wobei der Druck p beispielsweise 200 MPa betragen kann. Aus den Formeln (1) und (2) ergibt sich für die Normalkraft F_N auf den Dichtbolzen 11: $${\mathrm{F}}_{\mathrm{N}}=\mathrm{p}\mathbf{*}\mathbf{\pi }*{\mathrm{e}}^{\mathrm{2}}\mathrm{/}4.$$

With the pressure p of the medium provided on the second side 7 of the body 3, the normal force F _N on the sealing bolt 11 results: $${\mathrm{F}}_{\mathrm{N}}\mathrm{=}\mathrm{p}\mathrm{*}{\mathrm{A}}_{\mathrm{B}}\mathrm{.}$$

wherein the pressure p may be 200 MPa, for example. From the formulas (1) and (2) results for the normal force F _N on the sealing bolt 11: $${\mathrm{F}}_{\mathrm{N}}=\mathrm{p}\mathbf{*}\mathbf{\pi }*{\mathrm{<figure-callout\; id="2"\; label="e"\; filenames="imgf0004.png"\; state="\{\{state\}\}">e</figure-callout>}}^{\mathrm{2}}\mathrm{/}\mathrm{4th}$$

The lateral surface A _{D of} the seal results from the outer diameter e of the collar 18 of the sealing bolt 11 and the layer thickness h: $${\mathrm{A}}_{\mathrm{D}}=\mathbf{\pi }*\mathrm{e}*\mathrm{H}\mathrm{,}$$

The pressure force F _D on the seal given by the sealing surface 31 results from the pressure p of the medium and the lateral surface A _{D of} the seal: $${\mathrm{F}}_{\mathrm{D}}\mathrm{=}\mathrm{p}\mathrm{*}{\mathrm{A}}_{\mathrm{D}}\mathrm{,}$$

From the formulas (4) and (5) thus results in the pressure force F _D
to the seal too: $${\mathrm{F}}_{\mathrm{D}}=\mathrm{p}\mathbf{*}\mathbf{\pi }*\mathrm{e}*\mathrm{H}\mathrm{,}$$

wobei in Formel (7) die Normalkraft F_N entsprechend der Formel (3) verwendet worden ist.The force F _R for overcoming the static friction of the material pairing of the material of the body 3 and the material of the coating 25 results from the related coefficient of friction μ ₀ and the normal force F _N on the sealing bolt 11: $${\mathrm{F}}_{\mathrm{R}}\mathrm{=}{\mathrm{\mu }}_{\mathrm{0}}\mathrm{*}{\mathrm{F}}_{\mathrm{N}}\mathrm{=}{\mathrm{\mu }}_{\mathrm{0}}\mathrm{*}\mathrm{p}\mathrm{*}\mathrm{\pi }\mathrm{*}{\mathrm{<figure-callout\; id="2"\; label="e"\; filenames="imgf0004.png"\; state="\{\{state\}\}">e</figure-callout>}}^{\mathrm{2}}\mathrm{/}\mathrm{4}\mathrm{.}$$

wherein in formula (7) the normal force F _N according to the formula (3) has been used.

wobei das Dreifache der Druckkraft F_D für die Reibungskraft F_x mit 3-facher Sicherheit gewählt ist. Durch Gleichsetzen der Reibungskraft F_R entsprechend der Formel (7) und der Reibungskraft mit 3-facher Sicherheit F_x entsprechend der Formel (8), das heißt: $${\mathrm{F}}_{\mathrm{R}}\mathrm{=}{\mathrm{F}}_{\mathrm{X}}\mathrm{,}$$

ergibt sich nach einigen Vereinfachungen: $$\mathrm{h}\mathrm{/}\mathrm{e}\mathrm{=}{\mathrm{\mu }}_{\mathrm{0}}\mathrm{/}\left(\mathrm{3}\mathrm{*}\mathrm{4}\right)\mathrm{.}$$

In order to increase the reliability of the seal, an x-fold safety for the frictional force F _R is preferably taken into account. For example, x may be equal to 3. It then follows: $${\mathrm{F}}_{\mathrm{x}}\mathrm{=}\mathrm{3}\mathrm{*}{\mathrm{F}}_{\mathrm{D}}\mathrm{=}\mathrm{3}\mathrm{*}\mathrm{p}\mathrm{*}\mathrm{\pi }\mathrm{*}\mathrm{e}\mathrm{*}\mathrm{H}$$

wherein the triple of the pressing force F _{D is selected} for the frictional force F _x with 3 times certainty. By equalizing the frictional force F _R according to the formula (7) and the frictional force with 3 times certainty F _x according to the formula (8), that is: $${\mathrm{F}}_{\mathrm{R}}\mathrm{=}{\mathrm{F}}_{\mathrm{X}}\mathrm{.}$$

results after some simplifications: $$\mathrm{H}\mathrm{/}\mathrm{e}\mathrm{=}{\mathrm{\mu }}_{\mathrm{0}}\mathrm{/}\left(\mathrm{3}\mathrm{*}\mathrm{4}\right)\mathrm{,}$$

ergibt sich für das Verhältnis der Extrusionsgrenzdicke, das heißt der maximal wählbaren Schichtdicke h und dem Außendurchmesser e des Dichtbolzens 11: $$\mathrm{h}\mathrm{/}\mathrm{e}\mathrm{=}{\mathrm{\mu }}_{\mathrm{0}}\mathrm{/}\mathrm{12}\mathrm{=}\mathrm{0}\mathrm{,}\mathrm{08}\mathrm{/}\mathrm{12}\mathrm{=}\mathrm{1}\mathrm{/}\mathrm{150.}$$

Factor 3 takes into account 3 times the safety. Instead of the factor 3, another factor may be chosen to generally specify a frictional force F _x with x-fold certainty. For the friction coefficient of mating Teflon and steel of $${\mathrm{\mu }}_{\mathrm{0}}\mathrm{=}\mathrm{0}\mathrm{.}\mathrm{08}$$

results for the ratio of the extrusion boundary thickness, that is, the maximum selectable layer thickness h and the outer diameter e of the sealing bolt 11: $$\mathrm{H}\mathrm{/}\mathrm{e}\mathrm{=}{\mathrm{\mu }}_{\mathrm{0}}\mathrm{/}\mathrm{12}\mathrm{=}\mathrm{0}\mathrm{.}\mathrm{08}\mathrm{/}\mathrm{12}\mathrm{=}\mathrm{1}\mathrm{/}\mathrm{150th}$$

It should be noted that the extrusion limit thickness given by the formula (10), in particular the formula (12), is to be understood as the maximum value which is maintained at least in the region of the sealing edge 30 in order to allow extrusion of the coating 25 in the region of the sealing edge 30 prevent. The remaining coating 25, that is the coating 25 outside the sealing edge 30, may also have a different layer thickness. Further, the layer thickness h may be also smaller than the extrusion limit thickness determined by the formula (10). In addition, the layer thickness h can be influenced within certain limits by the choice of the safety factor x, which is selected equal to 3 above, and the friction coefficient μ ₀ .

Fig. 5 shows the in Fig. 3 illustrated high-pressure seal 1 according to a second embodiment of the invention. The designated IV section is according to the basis of the Fig. 4 designed neckline designed. In this embodiment, the sealing bolt 11, a contact element 35, that is, a contact point, which is formed by a blind bore. Thus, a plug or the like for contacting the high-pressure seal 1 on the second side can be inserted into the contact member 35.

Furthermore, in a remaining part 36 of the blind bore 19, through which the compression element 12 has been pressed into the blind bore 19, a plug or the like can be used to allow contacting of the high-pressure seal 1 from the first side 6.

The contacting on the first side 6 and / or the second side 7 of the body 3 can also be done in other ways, for example by soldering.

Fig. 6 shows a simplified illustrated fuel injection valve 2 with a high-pressure seal 1 according to a third embodiment of the invention. The section marked IV is in accordance with the in Fig. 4 designated neckline designed. In this embodiment, the body 3 is inserted into a valve housing 37 of the fuel injection valve 2. The body 3 may also be part of the valve housing 37 or be formed integrally with the valve housing 37. The fuel injection valve 2 has a simplified illustrated actuator 38, which is supplied to a fuel under high pressure via a line 39. During operation of the fuel injection valve 1, high-pressure fuel may also be located in a valve chamber 40. The actuating device 38 is electrically contacted on the one hand with the contact element 35 of the high-pressure seal 1 and on the other hand with the body 3. Furthermore, a control unit 44 is provided, which is contacted on the one hand with the compression element 12 and on the other hand with the body 3 electrically. Thereby, the passage of electrical energy through the valve housing 37 into the interior of the valve housing 37 to the actuator 38 is possible to actuate the fuel injection valve 2, wherein fuel can be sprayed off via a nozzle opening 41. In this exemplary embodiment, the pressing element 12 has a barrel-shaped pressing body 42 and a contact element 43. The barrel-shaped compression body 42 is pressed into the blind bore 19 in order to form a press connection between the sleeve 9 in the region of the helical profile 14 and the body 13. The contact element 43 of the compression element 12 is designed as a rod-shaped contact plug to allow contacting by means of a socket with the control unit 44. Furthermore, the sealing bolt 11 has a contact element 35 designed as a contact plug in order to connect to the actuating device 38 by means of a bushing enable. The barrel-shaped configuration of the compression body 42 and the arrangement of the sealing bolt 11 in the bore 15 (FIG. Fig. 2 ) thereby allow alignment of the contact element 43 of the compression element 12 and the contact element 35 of the sealing bolt 11 along the axis 16 of the high pressure seal. 1

By sealing the collar 18 against the body 3, as it is based on Fig. 4 described in detail, a first high pressure resistant seal is formed. Furthermore, a second high-pressure resistant seal is formed by the positive connection between the helical profile 14 of the sleeve 9 and the body 3. These two seals ensure reliable operation of the high-pressure seal 1 in order to prevent leakage of the highly pressurized fuel from the valve housing 37 provided in the valve space 40. In this case, a plurality of high pressure seals 1 may be provided to lead, for example, measurement signals from the interior of the valve housing 37 to the controller 44 or the like.

The invention is not limited to the described embodiments.

Claims (14)

High-pressure seal (1), in particular high-pressure seal for fuel injection valves, for sealing a bore (4) provided in a body (3) with a sleeve (9) which at least partially has a helical profile (14) on an outer side, a sealing bolt (11) comprising at least one blind bore (19) and a compression element (12), the sleeve (9) being inserted into the bore (4) from a first side (6), the sealing bolt (11) being from one of the first side (6) opposite second side (7) is inserted into the sleeve (9), wherein an outer diameter (c) of the pressing element (12) is greater than an inner diameter (b) of the blind bore (19) of the sealing bolt (11), wherein the Compression element (12) in the blind bore (19) of the sealing bolt (11) is pressed, so that at least a positive connection between the helical profile (14) of the sleeve (9) and the body (3) in the region of the bore (4) is formed , and where at a collar (18) of the sealing bolt (11) on the second side (7) is pressed at least indirectly against the body (3). High pressure seal according to claim 1,
characterized,
that the Verpressungselement (12) is designed as a spherical Verpressungselement (12). High pressure seal according to claim 1,
characterized,
in that the pressing element (12) has a barrel-shaped pressing body (42) which is pressed into the blind bore (19) and a contact element (43). High pressure seal according to claim 3,
characterized,
that the contact element (43) is designed as a rod-shaped contact plug. High-pressure seal according to one of claims 1 to 4,
characterized,
in that an electrically insulating insulating means (25) is provided which electrically insulates the sealing bolt (11) from the body (3). High pressure seal according to claim 5,
characterized,
that the insulating means is formed from an electrically insulating coating (25) which is at least partially applied to the sealing bolt (11). High pressure seal according to claim 6,
characterized,
in that the electrically insulating coating (25) has a layer thickness (h) at least in a sealing region (31) which is not greater than an extrusion boundary thickness. High-pressure seal according to one of claims 1 to 7,
characterized,
in that the collar (18) of the sealing pin (11) has a sealing edge (30), where the sealing pin (11) at least indirectly pressed against the body (3). High-pressure seal according to one of claims 1 to 8,
characterized,
that the sealing pin (11) has a contact element (35). High pressure seal according to claim 9,
characterized,
that the contact element (35) is formed by a blind bore. High pressure seal according to claim 9,
characterized,
that the contact element (35) is designed as a rod-shaped contact plug. High-pressure seal according to one of claims 1 to 11,
characterized,
in that the bore (4) provided in the body (3) is designed as a stepped bore, wherein the sleeve (9) is inserted into the stepped bore at least substantially up to a step (5) of the stepped bore. Fuel injection valve (2), in particular injector for fuel injection systems of air-compressing, self-igniting internal combustion engines, with one in one
Actuating device (38) arranged valve housing (37), wherein at least the actuating device (38) via a high-pressure seal (1) according to one of claims 1 to 12 with a control device (44) is connectable. Fuel injection valve according to claim 13,
characterized,
that the body (13) in which the through the High-pressure seal (1) sealed bore (4) is provided, inserted into the valve housing (37), with the valve housing (37) integrally connected or formed integrally with the valve housing (37).

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