JP4340231B2 - Fuel injector with high pressure resistant connection area - Google Patents

Description

2. Description of the Related Art A fuel injector that is supplied with fuel via a high-pressure accumulator (common rail) is used today for a self-ignition internal combustion engine. A fuel injection system with a high-pressure accumulator advantageously makes it possible to adapt the injection and the course of injection to the load and speed of a self-igniting internal combustion engine. In fuel injectors that are exposed to high pressures, special requirements are imposed on the high pressure resistance of the injector body of the fuel injectors used, in order to reliably suppress the high operating pressures that are generated. In the next generation of fuel injectors, it is expected that the injector body of the fuel injector will be exposed to a further increased operating pressure.

BACKGROUND DE-A 19650865 Pat relates to a fuel injector is operable by an electromagnetic valve. The fuel injector according to this solution has a high-pressure connection that opens laterally into the injector body. Through this high pressure connection, fuel under high pressure is supplied from the high pressure accumulator to a pressure hole extending in the longitudinal direction in the injector body. A fuel amount to be injected is supplied to the injection opening via a pressure hole extending in the injector body. This amount of fuel is injected into the combustion chamber of a self-ignition internal combustion engine. An inflow hole extends from a connection region disposed laterally on the injector body. This inflow hole supplies the fuel under high pressure to the annular chamber surrounding the valve piece, in addition to the pressure hole extending through the injector body in the longitudinal direction already described above. An inflow restrictor is formed on the wall of the valve piece. Due to this inflow restriction, fuel under high pressure is supplied as a control volume to a control chamber partitioned by a valve piece and an injection valve member. An inflow hole for the annular chamber extending obliquely through the injector body opens at the annular chamber at a predetermined inflow angle and forms an intersecting region with the wall surface of the annular chamber. This crossing region constitutes a potential weakening point with respect to the pressure resistance of the injector body of the known fuel injector according to German Offenlegungsschrift 19650865.

  EP-A-0916842 relates to a fuel injector for supplying fuel into the combustion chamber of a self-igniting internal combustion engine. A high pressure connection is accommodated laterally in the injector body. Via this high-pressure connection, fuel under high pressure is supplied to the pressure hole for supplying fuel to the nozzle chamber, and fuel under high pressure is supplied to the annular chamber surrounding the valve piece. According to this solution, the first hole leading to the annular chamber is branched at the first angle with respect to the axis of symmetry of the fuel injector at the end face of the hole accommodating the high-pressure connection. Two holes diverge at a second angle with respect to the axis of symmetry of the fuel injector. Based on the selected hole geometry, the injector body of the fuel injector according to EP 0 916 842 can be kept relatively slim, but an intersection region is created at the end face of the high-pressure connection. This is because there are two holes that are located directly side by side. This constitutes a weakening point with respect to the strength to be achieved. Furthermore, in order to supply the control chamber via the inflow restriction element, an intersection region is created in the region of the opening that loads the annular chamber with fuel under high pressure. This constitutes a weakening point of the injector with respect to the height of the pressure load.

  German Offenlegungsschrift 19640480 relates to a fuel high pressure accumulator. According to this solution, the fuel is supplied from the fuel high-pressure pump to the fuel high-pressure accumulator for the fuel injection system used in the internal combustion engine. The fuel high pressure accumulator has an elongated tubular body made of steel. This tubular body is provided with connections for fuel supply and fuel withdrawal. The connecting portion for supplying and deriving the fuel is formed as a connecting pipe piece. From this connecting tube piece, one connecting hole opens eccentrically with respect to the axis of the tubular body.

  German Patent 1,997,946 relates to a high-pressure fuel accumulator for a fuel injection system which is also used in internal combustion engines. According to this solution, the fuel high-pressure accumulator is provided with a plurality of connecting pipe pieces. In this case, a plurality of connection holes extend between the hollow chamber of the fuel high-pressure accumulator and one connection pipe piece. The connection hole opens in the tangential direction to the hollow chamber of the fuel high-pressure accumulator. In this case, the connection hole opened in the tangential direction to the hollow chamber of the fuel high-pressure accumulator has a larger diameter than the connection hole not opened in the tangential direction to the pressure accumulation chamber.

DISCLOSURE OF THE INVENTION With the solution according to the invention, the pressure resistance of the injector body of the fuel injector can be significantly increased without the need for additional sealing elements. This is achieved by a reduction in the angle between the nozzle supply hole extending in the injector body and the inlet section of this nozzle supply hole. By this means, a stress reduction is caused in the transition region (bending region) from the inflow hole section inside the injector body to the nozzle supply hole. The inlet hole section formed in the side pressure tube piece with an optimized bending angle can be sealed by a high-pressure connection threaded into the pressure tube piece.

  Based on the decrease in the bend angle between the inlet hole section in the injector body and the nozzle supply hole, the bend angle in the transition region is oriented vertically, ie, closer to the ideal case of the bend region without intersection. Based on the decrease in the bend angle between the inlet hole section and the nozzle supply hole, a steeper position between the inlet hole section extending through the pressure tube piece and the nozzle supply hole is created. This reduces the comparative stress in the transition region (bending region) between these holes.

  Furthermore, the pressure resistance of the injector body is as far as possible from the valve chamber while the transition region between the inlet hole section and the nozzle supply hole is kept at a minimum distance from the peripheral surface of the injector body. It can be enhanced by being formed. Furthermore, the risk of damage to the injector body when applying an elevated operating pressure level can be reduced by the injector body not subjecting it to material removal as much as possible at the height of its high pressure connection.

In the following, embodiments of the present invention will be described in detail with reference to the drawings.

  From FIG. 1, it is possible to know the high-pressure connection area provided in the injector body with a hole image according to the known prior art.

  The fuel injector 1 has an injector body 2. The injector body 2 has a center hole 3 in a lower region thereof. An assembly chamber 4 is formed in the upper region of the injector body 2. A solenoid valve assembly (not shown in FIG. 1) is fitted into the assembly chamber 4. This solenoid valve assembly operates the valve member. This valve member is also not shown in FIG. 1 for reasons of clarity. A pipe piece 6 is formed on the injector body 2 on the side. This tube piece 6 has a connection region 5. This connection region 5 can accommodate a connection line from a high pressure accumulator (common rail) not shown in connection with FIG. The connection area 5 is preferably formed as a connection thread. An end face 7 is provided in a tube piece 6 formed on the side of the injector body 2. This end face 7 ends with an oblique chamfer 8 and is loaded with fuel under pressure which is pumped into the injector body 2 via a high pressure connection. An inflow hole section 9.1 branches off from the end face 7 in the tube piece 6. This inflow hole section 9.1 transitions to the hole section 13. This hole section 13 is formed with a smaller diameter than the diameter of the inlet hole section 9.1. The inlet hole section 9.1 and the hole section 13 are accommodated coaxially with each other and are formed at a first inclination angle 11 with respect to the axis 19 of the injector body 2. Due to the configuration of the inflow hole section 9.1 and the hole section 13 with a smaller diameter following this inflow hole section 9.1, a first bending angle 10 is produced inside the transition area 20 (bending area). Therefore, the inflow hole section 9.1, the hole section 13 following the inflow hole section 9.1, and the nozzle supply hole 9 formed in the injector body 2 are arranged inside the transition region 20 (bending region). Meet at the intersection 12 of. In the configuration corresponding to the known prior art shown in FIG. 1, the tilt angle indicated by reference numeral 11 is set to 36.5 °. Based on this, a first bending angle of 143.5 ° with respect to the axis 19 of the injector body 2 is produced.

  The configuration of the inflow hole section 9.1 as a hole branched from the end face 7 of the pipe piece 6 and the generated first bending angle 10 of about 143.5 ° are the same as those of the fuel injector 1 shown in FIG. Limit the pressure level to which the injector body 2 can be exposed to pressures in the range of about 1350 bar. Thus, this can cause sealing problems in the region of the tube piece 6 and damage can occur in the material of the injector body 2, especially on the basis of high stress levels in the transition region 20 when the pressure is higher. This can result in a complete failure of the fuel injector 1. This limits the operating pressure level at which the injector body 2 of the fuel injector 1 shown in FIG. 1 can be exposed to a pressure level of about 1350 bar.

  Furthermore, in the injector body 2, the side of the transition region 20 between the inlet hole section 9.1, the hole section 13 at the reduced diameter and the nozzle supply hole 9 vertically passing through the injector body 2. A valve chamber 14 is formed in the front. A valve member (not shown) is movably disposed in the valve chamber 14. This valve member can be operated by an actuator (not shown) that is desired to be disposed inside the assembly chamber 4, for example, an electromagnetic valve assembly. An inner wall 17 of the valve chamber 14 inside the injector body 2 has an annular groove 18 formed symmetrically. The annular groove 18 is located approximately in the middle of the valve chamber 14 partitioned by the inner wall 17. In order to fix an actuator to be fitted into the assembly chamber 4, for example, a solenoid valve assembly, a male thread 16 is provided in an upper region of the injector body 2. The position of the actuator is fixed inside the assembly chamber 4 by the male thread 16. Further, the injector body 2 is penetrated by a hole 15 extending substantially vertically. This hole 15 serves to release and control leakage oil.

  From FIG. II-II, a cross-sectional view of an injector body formed according to the present invention can be seen. In this case, the cross-sectional profile II-II is clear from FIG.

  As is clear from the cross-sectional process II-II, in the configuration according to the invention of the injector body 2 of the fuel injector 1, here an inflow hole section 9.1, shown in broken lines, penetrates the connection region 5 of the tube piece 6. ing. An inflow hole 22 branches off from the end surface 7 of the pipe piece 6 into the valve chamber 14. The inflow hole 22 is disposed at an angle 23 with respect to the axis 19 of the injector body 2. This angle 23 is advantageously chosen to be greater than 70 °. An inflow hole 22 extending from the end surface 7 opens into an annular groove 18 formed in the wall 17 of the valve chamber 14. The opening of the inflow hole 22 leading to the valve chamber 14 is indicated by reference numeral 24.

  An inflow hole section 9.1 indicated by a broken line in the sectional view II-II keeps the course indicated by reference numeral 25 in the injector body 2. The inlet hole section 9.1, on the one hand, penetrates the wall of the tube piece 6 at a first location 26, and preferably comprises a connection region 5 which is formed as a thread and an end face 7 of the tube piece 6. It extends through. Inflow hole section 9.1 transitions to hole section 13. This hole section 13 has a reduced diameter, similar to a known construction based on the known prior art shown in FIG. Inside the transition region 20, an inlet hole section 9.1 or a hole section 13 following the inlet hole section 9.1 is shown here as a broken line, vertically formed in the injector body 2 / nozzle supply hole / throttle Transition to hole 9. For reasons of easier manufacture, the connection area 5 provided on the inner surface of the tube piece 6 provided as an internal thread does not extend completely to the end face 7. Between the end surface 7 and the connection region 5 that can be advantageously formed as a female thread, an oblique chamfered portion 8 that extends in an annular shape is provided. The transition region 20 between the inlet hole section 9.1, the hole section 13 and the nozzle supply hole / throttle hole 9 shown in the cross-sectional course II-II also has an intersection 12. However, this intersection 12 is based on its geometry and has a significantly advantageous stress profile, as will be explained further below. In the cross-section course II-II, a hole 15 serving as a return passage for leaking oil is hidden by the material of the injector body 2. The hole 15 extends along the assembly chamber 4. The assembly chamber 4 is formed inside the injector body 2 and below the external thread 16 in the region above the injector body 2.

  From FIG. 2, a plan view of the slightly rotated injector body formed according to the invention can be seen.

  As is clear from the plan view shown in FIG. 2, the tube piece 6 is arranged on the injector body 2 of the fuel injector 1 on the side. A connection region 5 is formed inside the tube piece 6. This connection region 5 is preferably formed as a female thread. On the upper surface of the tube piece 6, the first location 26 of the inlet hole section 9.1 is located (see cross-section progress II-II). The inlet hole section 9.1 extends through the connection area 5 and the end face 7 in the tube piece 6. Inflow hole section 9.1 transitions to hole section 13. The hole section 13 is formed with a reduced diameter compared to the inlet hole section 9.1. In the plan view shown in FIG. 2, an intersection in the transition region 20 not shown here is indicated by reference numeral 12. Further, as is apparent from the plan view shown in FIG. 2, the inflow hole 22 branched from the end face 7 in the tube piece 6 is used to load the valve chamber 24 with fuel under high pressure, so that the injector body 2 It extends with an angular deviation 28 with respect to the axis 19 of This ensures that the opening 24 of the inflow hole 22 opens eccentrically into the valve chamber 14. This results in an advantageous stress course on the inner wall 17 (see cross-section course II-II) of the valve chamber 14 provided inside the injector body 2. The horizontal angular deviation of the inlet hole 22, indicated by reference numeral 28 in the plan view shown in FIG. 2, is independent of the selected diameter of the valve chamber 14 or the symmetrically extending annular groove 18 formed in the valve chamber 14. Is set to an order of about 10 °.

  Sectional section III-III shows the inlet hole segment / hole segment transition region to the nozzle supply / throttle hole extending vertically in the injector body.

  According to the passage of the inlet hole section 9.1 in the upper region of the injector body 2, indicated by the reference numeral 25, the inlet hole section 9.1 transitioning to the hole section 13 of the reduced diameter is formed in the injector body 2. It is formed with an optimized tilt angle 30 with respect to the axis 19. The tilt angle 30 optimized according to the invention follows the inflow hole section 9.1 or the inflow hole section 9.1 for the nozzle supply / throttle hole 9 that penetrates the injector body 2 parallel to the central hole 3. The ascending course of the reduced diameter hole section 13 is assured as much as possible. The optimized tilt angle 30 is set in a range between 15 ° and 25 °. Particularly good stress results are obtained when the optimized tilt angle 30 is set in the range between 24 ° and 23 °. The inlet hole section 9.1 ends at a first location 26 on the outer surface of the tube piece 6. Furthermore, the inflow hole section 9.1 passes through the tube piece 6 at the inner surface in the region of the connection region 5 and further through the end surface 7. The inflow hole section 9.1, which extends in the injector body 2 with a steep inclination by an optimized tilt angle 30, has transitioned to a hole section 13 of reduced diameter. This hole section 13 itself opens to the nozzle supply hole / throttle hole 9 in the transition region 20 (bending region). Based on the selected optimized tilt angle 30 of about 23 °, an optimized bend angle 29 is obtained. Based on this, compared to the intersection 12 inside the transition region 20 (bent region) shown in FIG. 1, a transition region 20 almost without intersection is generated.

  A comparison between the transition region 20 shown in FIG. 1 and the transition region 20 according to the configuration of the injector body 2 according to the present invention shown in the cross-sectional process III-III shows that the bending angle 10 shown in FIG. This shows that the bending angle 29 has been optimized. For example, an increase in the bend angle from 143.5 ° to 157 ° (see section profile III-III) reduces the comparative stress inside the transition region 20 (bend region). Further stress reduction inside the transition region 20 of the smaller diameter hole section 13 to the nozzle supply hole / throttle hole 9 is obtained by rounding the opening edge of the hole section 13 to the nozzle supply hole / throttle hole 9. be able to. By avoiding hole transitions with sharp edges in the transition region 20 (intersection region), the stress level created there can be further reduced. Rounding of the interior of the transition region 20 can be performed by various manufacturing methods, and can be performed while maintaining the outer wall thickness 32 of the injector body 2 when the injector body 2 is structured or designed.

  Another advantageous means for reducing the comparative stress is that the transition region 20 (bending region) is formed as far as possible from the wall 17 of the valve chamber 14 inside the injector body 2. While maintaining the required minimum wall thickness 32 of the material of the injector body 2, the increased distance between the transition region 20 (bending region) and the wall 17 of the valve chamber 14 is denoted 31 in the cross-sectional course III-III. It is shown by. The distance indicating the distance of the valve chamber 14 from the transition region 20 of the holes 9; 13, indicated by the reference numeral 31, is set to be larger than the first distance 21 of the valve chamber 14 to the bent region 20. This is because the angle of the inlet hole section 9.1 shown in the cross-sectional course III-III is significantly steeper than the angle of the inlet hole section 9.1 shown in FIG. Thereby, the outer wall thickness 32 in the injector body 2 can be kept larger. Compared to the spacing 21 between the valve chamber 14 and the bent region 20 shown in FIG. A distance 31 of 5 to 1.8 mm is obtained, whereas the distance indicated by reference numeral 21 in FIG. 1 is dimensioned only to 1.2 to 1.3 mm.

  The high pressure side seal, i.e. the seal of the inflow hole section 9.1 and the diameter reduction following this inflow hole section 9.1, so that the solution according to the invention can be known without difficulty from the cross-section progress III-III. The high-pressure connection portion from the high-pressure accumulator (common rail) is screwed into the connection region 5 with the seal of the hole section 13 having the diameter and the seal of the nozzle supply hole / throttle hole 9 and the permissible tightening torque This can be done by being fixed. The upper inlet section 9.1 extending from the connection area 5 to the first location 26 is sealed against the end face 7 by thread overlap without the need for a separate sealing element to be fitted. This allows the same injector body 2 to be positioned at a higher pressure which can be located in a higher range of about 1600 bar or more by changing the hole positions of the inlet hole section 9.1 and the hole section 13 and appropriately forming the transition region 20. Can be used.

  As can already be seen from the cross-sectional profile II-II, the inner wall 17 of the valve chamber 14 is provided with a symmetrical annular groove 18. In the annular groove 18, an inflow hole 22 (not shown in the section progress III-III) is opened at an opening 24 (also not shown in the section progress III-III).

  The valve chamber 14 is shifted to a central hole 3 that extends vertically in the injector body 2 at the transition portion 35. The central hole 3 accommodates an injection valve member that is formed, for example, as a nozzle needle and extends into the nozzle chamber. The nozzle supply hole / throttle hole 9 loads a nozzle chamber (not shown here) surrounding the injection valve member with fuel under high pressure.

  An assembly chamber 4 provided in an upper region of the injector body 2 for accommodating an actuator in the form of an electromagnetic valve assembly includes an internal thread 33 that can fix the electromagnetic valve assembly, and an assembly to the valve chamber 14. It has an annularly extending collar surface 34 that forms a transition region of the attachment chamber 4.

  As a reminder, the maximum distance 31 between the transition region 20 (bending region) and the inner wall 17 of the valve chamber 14 sees its limitation to the minimum material thickness 32. This material thickness 32 may undertake the outer wall of the injector body 2 of the fuel injector 1 in order to meet strength requirements and form a safety margin.

  FIG. 3 shows a plan view of an injector body according to the invention.

  As can be seen from FIG. 3, according to the cross-section progress III-III, the hole 15 formed so as to extend obliquely in the injector body 2 opens below the external thread 16. A first location 26 can be found on the upper surface of the tube piece 6 located on the opposite side of the opening location of the hole 15. From this first location 26, an inflow hole section 9.1 extends through the connection region 5 on the inside of the tube piece 6 and penetrates the end face 7 at a second location 27 (see section III-III). ing. An inflow hole 22 that loads the valve chamber 14 in the injector body 2 branches from the end face 7 with an angular deviation that can be seen from FIG. The inflow hole 22 is an opening portion 24 and opens into an annular groove 18 formed symmetrically in the valve chamber 14. This reduces the comparative stress inside the valve chamber 14 by about 20%. The inlet hole section 9.1 transitions to the hole section 13 at the reduced diameter below the second location 27. This hole section 13 is shifted to a nozzle supply hole / throttle hole 9 formed vertically in the injector body 2 at an intersection 12 inside the transition region 20 oriented substantially vertically.

  With the solution proposed by the present invention, the pressure level at which the injector body 2 can be loaded from about 1350 bar, while maintaining the main features of the injector body 2 and without the need for additional sealing elements. It is possible to increase the pressure level above 1600 bar. Sealing can be achieved by changing the position 25 of the inlet section 9.1. Since the inlet hole section 9.1 passes through the pipe piece 6 provided laterally in the injector body 2, the seal of the inlet hole section 9.1 is accommodated in the connection region 5 provided in the pipe piece 6. Can be made by a high pressure connection. The pressure level at which the injector body 2 formed according to the invention can now be loaded is in particular that the inlet section 9.1 extends with an optimized inclination 30 with respect to the axis 19 of the injector body 2, whereby The optimized bend angle 29 is raised by being caused in the transition area 20 in the inlet hole section 9.1 or the hole section 13 and the nozzle supply hole / throttle hole 9 extending vertically in the injector body 2. Due to the reduction of the tilt angle 30 according to the solution according to the invention, the bend angle 10 (see FIG. 1) is optimized to an optimized bend angle 29, for example instead of 143.5 ° according to the known prior art configuration shown in FIG. Increased to 157 °. Furthermore, when the rounded region is formed inside the transition region 20 (bent region), the comparative stress in the transition region 20 (bent region) can be reduced again. This is because by this means a transition with a sharp edge between the nozzle supply / throttle hole 9 and the smaller diameter hole section 13 can be avoided.

  Furthermore, the pressure level at which the injector body 2 formed according to the present invention can be loaded can be increased by forming the largest possible gap 31 between the inner wall 17 of the valve chamber 14 and the transition region 20. it can. However, in this case, the allowable outer wall thickness 32 of the injector body 2 must be taken into account. An advantageous course of the comparative stress inside the valve chamber 14 of the injector body 2 can be achieved by machining the symmetrical annular groove 18 into the inner wall 17 that partitions the valve chamber 14. Furthermore, an advantageous influence on the stress course can be achieved by the inflow hole 22 into the valve chamber 14 and the arrangement of the opening in the symmetrical annular groove 18 arranged at an angular deviation 28. . Furthermore, if the inflow hole 22 is formed at the flatest possible angle 23 (see section profile II-II) set to more than 70 °, an advantageous comparative stress in the injector body 2 is achieved. Can do.

It is a figure which shows the high voltage | pressure connection area | region in the injector body provided with the hole image by a well-known prior art.

FIG. 11 is a plan view of a slightly rotated injector body formed according to the present invention, and FIG. II-II is a diagram showing a cross-sectional process of the injector body shown in FIG. It extends through an inflow hole that leads to the valve chamber.

FIG. 3 is a plan view of an injector body according to the present invention, and FIGS. III-III are cross-sectional views of the nozzle supply hole shown in FIG.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Fuel injector, 2 Injector body, 3 Center hole, 4 Assembly chamber, 5 Connection area | region, 6 Pipe piece, 7 End surface, 8 Diagonal chamfering part, 9 Nozzle supply hole, 9.1 Inflow hole division, 10 Bending angle, 11 Tilt angle, 12 intersections, 13 hole sections, 14 valve chamber, 15 holes, 16 male thread, 17 inner wall, 18 annular groove, 19 axis, 20 transition region, 21 spacing, 22 inflow hole, 23 angle, 24 opening position, 25 Progress, 26 locations, 27 locations, 28 angular deviation, 29 bending angle, 30 tilt angle, 31 spacing, 32 outer wall thickness, 33 female thread, 34 brim surface, 35 transition portion

Claims (10)

A fuel injector, provided with an injector body (2), the injector body (2) having a pipe piece (6) arranged laterally, the pipe piece (6) being A connection region (5) and an end face (7) are provided. An inflow hole (22) leading from the end face (7) to the valve chamber (14) inside the injector body (2), and the injector body (2) An inlet hole section (9.1) for loading the nozzle supply hole (9) provided in the nozzle extends, and the nozzle supply hole (9) together with the inlet hole section (9.1) passes through the transition region (20). In the form of the form, the inflow hole section (9.1) extends through the connection region (5) of the tube piece (6) and is connected to the axis (19) of the injector body (2) and the inflow hole classification (9.1), but causing a stress reduction in the transition region (20), 35 ° Remote Ri Contact form small tilt angle (30), the wall (17) of the valve chamber (14) is formed an annular groove (18) is, the annular groove (18), the tube piece (6) A fuel injector, characterized in that the inflow hole (22) extending from the end face (7) opens at an angle (23) set to 70 ° or more.   2. The fuel injector according to claim 1, wherein the connection region (5) is formed as a connection thread.   2. The fuel injector according to claim 1, wherein the inlet hole section (9.1) extends through the end face (7) of the tube piece (6) and the connection region (5).   The fuel injector according to claim 1, wherein the inclination angle (30) is set to be smaller than 30 °.   2. The fuel injector according to claim 1, wherein the tilt angle (30) is advantageously set to be less than 25 [deg.].   The inlet hole (22) opens into the annular groove (18) of the valve chamber (14) with an angular deviation (28) with respect to the normal achieved perpendicular to the axis (19) of the injector body (2). The fuel injector according to claim 1.   The fuel injector according to claim 1, wherein the transition region (20) between the inlet hole section (9.1) and the nozzle supply hole (9) is rounded to cause stress reduction.   The fuel injector according to claim 1, wherein the transition region (20) is arranged with respect to the valve chamber (14) inside the injector body (2) with as large a spacing (31) as possible.   The inlet hole section (9.1) penetrates the pipe piece (6) at the first location (26) in the connection region (5), and the end face (7) of the pipe piece (6) is the second location. The fuel injector according to claim 1, wherein the fuel injector penetrates at (27).   The fuel injector according to claim 1, wherein the inlet hole section (9.1) transitions to a hole section (13) of reduced diameter in front of the transition region (20).

Images