KR20190040167A - A high pressure fluid rail - Google Patents

Abstract

A high pressure fluid supply device (1) of a common rail system of a large internal combustion engine includes an accumulator unit (7) to supply a high pressure fluid to a plurality of fluid injection devices (8). The accumulator unit (7) has an outer circumferential surface (16), practically extends along a longitudinal axial line (14) of the accumulator unit (7), and is arranged on a center bore (11) having an inner circumferential surface (15). At least one radial bore (13) extends from the center bore (11) to the outer circumferential surface (16) of the accumulator unit (7). The radial bore (13) has a width (22) measured on a plane perpendicular to the longitudinal axial line (14) of the accumulator unit (7). The width is larger on the inner circumferential surface (15) than on the outer circumferential surface (16), and continuously decreases preferably from the inner circumferential surface (15) to the outer circumferential surface (16) with respect to at least a half of the distance between the inner circumferential surface (15) and the outer circumferential surface (16). The radial bore (13) has a first and a second side wall (18, 19). The width (22) is measured as the distance between the first and the second side wall (18, 19) of the radial bore (13) on a plane including a center axial line (17) of the radial bore, and is arranged to be perpendicular to the longitudinal axial line (14) of the accumulator unit (7).

Description

[0001] A HIGH PRESSURE FLUID RAIL [0002]

More particularly, the present invention relates to a high-pressure fluid rail for storage of high-pressure fluid applied for a piston engine.

In a common rail fuel injection system of a diesel engine, the fuel is supplied to the high-pressure fluid reservoir by a low-pressure pump and a high-pressure pump, such as a high-pressure accumulator or so-called common rail. From the high-pressure fluid reservoir, fuel is additionally supplied to the fuel injectors of each cylinder along separate conduits. From the fuel injection device, the fuel is introduced into each combustion chamber of the cylinder at a moment required according to the operation of the engine. There may be a plurality of high pressure fuel reservoirs, so that fuel is supplied to each of the two or more injection nozzles from each fuel reservoir.

The fuel pressure in the high-pressure fuel reservoir is high, even 2000 bar, so that the fuel accumulator is exposed to high stresses, resulting in cracks which are generated in the structural material, particularly in the region of the opening of the fuel reservoir wall, Type cross sectional area change portion.

The highest pressure typically occurs in the fuel rail common rail system. Due to the fact that high fluid pressures below 2000 bar, the dynamic loads caused by these high pressure fluid pressure fluctuations cause high stresses, the wall of the fuel space must be maintained for a long operating cycle. In particular, in marine engines, it is essential that the rail should not be replaced or repaired during the lifetime of the engine, but must be assured during the long operating cycle.

The strength of the wall of the fuel space is particularly limited by the radial bore extending from the central bore. The local stress introduced by this radial bore can be increased by three or four factors.

Patent document EP 1413744 discloses a fuel reservoir for a piston engine in which the fuel space is constituted by two elongated cylindrical bores arranged so as to partially overlap the cross-section to form the main bore. On the rails of the Wartsila RT-Flex engine, the main bore is machined from two eccentric bores, so that the main bore section has a peanut shape. From the main bore, the secondary bore connects the fuel space to the fuel injector supply conduit. The junction drilling portion of the auxiliary bore is located at the intersection of two eccentric bores. Thereby, the stress at the intersection between the junction drilling portion and the two main rail drilling portions is reduced, since the intersection between the bores is not directly exposed to the main stress line.

 Patent document WO 2008/145818 discloses a fuel reservoir having an orifice open in the fuel space configured to reduce the stress imposed on the fuel reservoir in the region of the orifice. Thereby, the risk of crack formation in the structural material of the fuel space body is reduced. As a result, the durability of the fuel reservoir is increased.

However, the solution proposed in WO 2008/145818 has several problems that can not be used in a fuel rail of considerable length. The recess must be machined from the inside, e.g. from the central bore. Due to the fact that the tool machining the recess can protrude only a small distance into the central bore, this solution can not be applied to long and thin fluid spaces with a diameter of the central bore of less than 100 mm and a total length of at least 1 meter Do.

It is an object of the present invention to provide a fluid space having at least one secondary bore that is applicable to such a long and thin fluid space.

The object of the present invention can be achieved by the features of claim 1. Advantageous embodiments of the invention are the subject matter of the dependent claims.

The high-pressure fluid supply device of the common rail system for a large-sized internal combustion engine includes an accumulator unit for supplying a high-pressure fluid to a plurality of fluid injection devices. The accumulator unit has an outer peripheral surface and is arranged with a central bore extending substantially along the longitudinal axis of the accumulator unit and having an inner peripheral surface. At least one radial bore extends from the central bore to the outer peripheral surface of the accumulator unit. The radial bore has a width measured in a plane perpendicular to the longitudinal axis of the accumulator unit, the width being larger at the inner circumferential surface than at the outer circumferential surface, and preferably at least half of the distance between the inner circumferential surface and the outer circumferential surface, To the outer circumferential surface. The radial bore has a first sidewall and a second sidewall. The width is measured as the distance between the first sidewall and the second sidewall of the radial bore in a plane perpendicular to the longitudinal axis of the accumulator unit and including the central axis of the radial bore.

According to one embodiment of the invention, the successive decreases are substantially linear. Thereby, in the portion along a plane perpendicular to the longitudinal axis of the accumulator unit including the axis of the radial bore, the first sidewall and the second sidewall are represented as straight lines. The opening angle between the first sidewall and the second sidewall is 10 to 75 degrees, preferably 10 to 60 degrees, particularly preferably 10 to 45 degrees. The opening angle is constant from the inner circumferential surface to the outer circumferential surface.

The width of the radial bore in the inner peripheral surface is at least twice the width of the radial bore in the outer peripheral surface. The width of the radial bore in the inner circumferential surface is measured in a projection on the plane including the longitudinal axis of the accumulator unit as viewed in the axial direction of the radial bore. The width is a distance from the first sidewall to the second sidewall.

If the width at the inner circumferential surface is significantly larger than the width at the outer circumferential surface and is at least twice the width of the circumferential surface, the stress acting on the inner circumferential surface of the accumulator unit about the radial bore is less than that of the cylindrical bore as disclosed in EP 1426607 A1 Can be distributed over a fairly large surface. In addition, due to the fact that the first sidewall extending between the inner circumferential surface and the outer circumferential surface has a constant tilt angle, the stress is particularly smoothly reduced due to the fact that there is no local sharp transition portion of the wall surface, as in WO2008 / 145818.

 In one embodiment, the central bore has a circular cross section. This central bore is particularly easy to manufacture, which means that the length of the accumulator unit per couple of meters is possible and can be manufactured at a low cost. Due to the fact that the pressure of the high-pressure fluid can be between 600 and 2000 bar, the central bore of the circular cross section is the most favorable shape for pressure distribution. However, an elliptical shape or a shape as disclosed in EP 1 413 744 A1 may be used.

The radial bore has a thickness approximately the same as the width at the outer circumferential surface. The thickness of the bore is measured in a direction perpendicular to the width. The thickness is measured in the direction of the longitudinal axis of the accumulator unit. By keeping the width and thickness of the bore at the outer circumferential surface small, the stress acting on the tube wall near the outer circumferential surface is reduced. In addition, on the one hand the minimum material is removed, on the one hand the waste is reduced and surprisingly has a beneficial effect on stress distribution. Thus, in one embodiment, the radial bore has a thickness on the inner circumferential surface that deviates from the thickness of the outer circumferential surface by 15% or less, preferably by 10% or less, particularly preferably by 5% or less.

The high-pressure fluid supply device according to one of the above embodiments can be advantageously used for fuel or servo oil or water as a high-pressure fluid.

The internal combustion engine in which the pressure fluid supply is most advantageously employed comprises a cylinder in which the piston is arranged to be movable back and forth along the longitudinal cylinder axis at the top dead center position and the bottom dead center position. In the cylinder, a combustion chamber is formed by the cylinder cover, the cylinder wall of the cylinder and the piston surface of the piston. A fuel injection device is provided for injection into the combustion chamber, and a high pressure fluid supply device according to any of the above embodiments can be used to supply high pressure fuel to the fuel injection device. The internal combustion engine may be configured as a dual fuel engine or gas engine operable in a crosshead type engine, in particular a crosshead large diesel engine, a trunk piston engine, a two or four stroke internal combustion engine, a diesel or an otto mode .

The manufacturing method of the high-pressure fluid supply apparatus according to any one of the above-mentioned embodiments includes a step of milling or drilling the radial bore. When the radial bores are drilled, the drilling is performed by drilling the central radial bore and at least the further side radial bores so that the drill holes of the central radial bore and the side radial bore are identical on the outer circumference, And is inclined with respect to the central radial bore hole on the inner peripheral surface. The milling or drilling step is performed from the outer circumferential surface to the inner circumferential surface of the accumulator unit including the central bore. Surprisingly, a milling or drilling step can be carried out from the outside of the accumulator unit. This is an unexpected advantage as compared to the prior art, as described in WO 2008/145818 or EP 2299102. In this specification, the indentation must be machined from a central bore that is quite cumbersome. In addition, it may not be possible to introduce a drilling or milling tool into the accumulator unit formed as a single long tube. Therefore, a plurality of accumulator units of small length should be used as shown in WO2008 / 145818. This results in that the assembling of the accumulator unit of the prior art becomes more difficult and time consuming as well as the control thereof becomes difficult.

Accordingly, the accumulator unit is particularly preferably constructed of an elongated tube. The fluid space inside the central bore may be a fuel space, a servo fluid space, but may also be a space used for gas space or water use. The fluid space is surrounded by the inner peripheral surface and at least one end, and the bore can be covered by the closure stopper.

At least one of the outer circumferential surface or the inner circumferential surface of the accumulator unit may have a circular, elliptical or polygonal cross section, for example a rectangular, in particular a square cross section, a triangular or a hexagonal cross section. In addition, the outer peripheral surface need not be concentric to the inner peripheral surface. Thus, the central bore may have a longitudinal axis that is not the same as the longitudinal axis of the body of the accumulator unit.

By means of a pump, a working fuel, for example a driving fluid for driving a valve, or a working medium for controlling a fuel injector, for example, is fed under high pressure from the fluid space for the desired use. The fluid space forms a central bore in the accumulator unit. The accumulator unit forms a common rail for supplying high-pressure fluid to a plurality of users. For this reason, a plurality of radial bores may be foreseen. In the case of a fuel injection common rail system, the fuel is distributed to the fuel injectors located in each cylinder by the common rail through the fuel conduit. The fuel injection device includes a fuel injection nozzle that supplies fuel to the combustion chamber of each cylinder.

BRIEF DESCRIPTION OF THE DRAWINGS The invention will now be described with reference to the accompanying schematic drawings, in which: FIG.

1 is a view showing a structure of a high-pressure fluid supply device of a fuel rail common rail system for a large-sized internal combustion engine.
2 is a cross-sectional view taken along the longitudinal axis of the accumulator unit;
3 is a cross-sectional view taken along line BB in Fig.
Figure 4 is a view of the C portion of the radial bore produced by drilling.
5 is a view of the C portion of the radial bore produced by milling.
6 is a cross-sectional view taken along a plane perpendicular to the longitudinal axis of the accumulator.
7 is a view showing a radial bore from the outer peripheral surface of the accumulator unit.
8 to 12 are diagrams showing a further embodiment of the present invention.

1 shows a fuel supply system 1 of a diesel engine, in particular a large diesel engine, which comprises several cylinders. As used herein, a large diesel engine refers to such an engine that can be used, for example, as a main or auxiliary engine at a ship or power plant for the generation of electricity and / or heat. Fuel is supplied from the fuel tank 2 to the high-pressure fuel storage 5 by the pump 4 along the pipe 3. The high-pressure fuel storage (5) is configured as a high-pressure accumulator unit (7).

The flow rate of the pump can be adjusted by the electronic control unit 20 based on the amount of fuel required by the fuel injector 8. The electronic control unit provides timing for the operation of the fuel injector 8 based on engine parameters such as engine load or engine speed. In addition, the control unit receives an input from the pressure sensor 21 mounted on the accumulator unit 7. The pressure sensor 21 detects the fluid pressure in the accumulator unit 7. Based on the detected pressure value, the operation of the pump is controlled, for example, by controlling the rotational speed of the pump motor 24. [

According to an alternative embodiment, a plurality of high-pressure pumps 4 may be provided. Each of the pumps may be provided with a control valve and a piston member (not shown). The piston member can be guided by the piston member from the cam member of the camshaft of the engine. If necessary, each cam member may include several cams, so that when the high-pressure pump 4 provides a predetermined volume flow rate per unit time to the accumulator unit 7, , So that the pressure shock provided to the accumulator by the pump is small.

The accumulator unit 7 is thus connected to the fuel injector 8 of the cylinder by a separate fuel injection conduit 9. Thereby, the accumulator unit 7 is connected to the two or more fuel injection devices 8. The fuel pressure in the accumulator unit 7 is at least 600 bar, typically 1000 to 2000 bar. The operation of the high-pressure pump 4 and the injection pressure used can be controlled in accordance with the engine load, operating speed or other parameters in a manner known per se.

Fig. 1 schematically shows a cylinder structure 100 according to the present invention having a fuel injection device according to the present invention for an internal combustion engine, which is a crosshead type large diesel engine exhausted in the longitudinal direction in the present embodiment. The cylinder structure 100 according to FIG. 1 includes a cylinder 101 in which a piston 103 is arranged to be movable back and forth along a longitudinal cylinder axis 107 between a top dead center position and a bottom dead center position. In the cylinder 101, the combustion chamber 104 is defined by the cylinder cover 102, the cylinder wall 105 of the cylinder 101, and the piston surface 106 of the piston 103. Only one charge-cycle valve 109, here an outlet valve, is provided in the gas exchange opening 110 of the cylinder cover 102 and the gas exchange opening 110 is in itself a well- Through a gas supply conduit 111 to a turbocharger assembly (not shown). The charge-cycle valve 109 includes a valve disc 112 which cooperates with the valve seat 113 of the gas exchange opening 110 in an operative state, so that in the closed position of the charge-cycle valve 109, 104 are sealed to the gas supply conduit 111 and at the open position of the charge-cycle valve 109, combustion gases can be supplied to the turbo assembly from the combustion chamber 104.

Figure 2 shows a cross-sectional view of the accumulator unit 7 taken along the longitudinal axis. The accumulator unit 7 includes a body 10 having an elongated fuel space for pressurized fuel. The fuel space includes a central bore 11 of a cylindrical shape. As shown in Figure 6, the cross section of the central bore 11 is circular. The central bore (11) extends along the longitudinal axis of the accumulator unit (7). Normally, the diameter of the bore is 20 to 100 mm. In addition, the main body 10 includes a supply channel (not shown in Fig. 2) that opens from the pipe 3 to the fuel space. The pressurized fuel is introduced from the high-pressure pump 4 into the fuel space through the supply channel along the pipe 3. In addition, the main body 10 includes a discharge channel that opens into the fuel space, through which channel fuel is discharged from the fuel space and introduced along the injection nozzle of the fuel injector 8 (see FIG. 1). A separate discharge channel is foreseen in each injection nozzle in flow connection with the accumulator unit 7. [ Radial bores 13 are foreseen in each discharge channel. The radial bore extends from the central bore 11 of the inner peripheral surface 15 to the outer peripheral surface 16 of the body 10. Each radial bore 13 has a longitudinal axis 17.

  Due to the high fuel pressure prevailing in the fuel space cracks and failures due to fatigue of the material may occur in the region of the body 10, in particular the radial bore 13 for the discharge channel. The radial bore 13 has a width measured in a plane perpendicular to the longitudinal axis 14 of the accumulator unit 7 and its width is defined by the outer circumferential surface 16 to prevent this breakage to the accumulator unit. And is continuously reduced from the inner circumferential surface 15 to the outer circumferential surface 16 as shown in Figs. 3 to 7. According to Fig. 3 or 6, the radial bore has a first sidewall 18 and a second sidewall 19.

Fig. 3 shows a section B-B in Fig. The radial bore 13 shown in Fig. 3 is produced by a drilling method. This drilling is performed by drilling the central radial bore and the radial bores 26, 27 of the first and second sides. The central radial bore 25 and the central drill hole 28 of the first and second radial bores 26 and 27 are identical on the outer circumferential surface 16 of the body 10. The first and second radial bores 26, 27 are angled with respect to the central radial bore 25. The drill holes 29 and 30 on the first and second sides of the radial bores 26 and 27 on the first and second sides are thus formed only in the inner circumferential surface 15, .

4 is a view of the C portion of the radial bore produced by drilling which is essentially the radial bore shown in Fig. The first and second side walls 31, 32 extend between the first and second side walls 18, 19. Due to the circular shape of the drill in each of the central radial bores, the radial bores on the first and second sides are cylindrical in shape. Due to the fact that at the level of the inner circumferential surface 15 the radial bores in the middle, the radial bores in the first and second sides no longer completely overlap, the first and second side walls 31, And a concave portion. The thickness of the radial bore on the inner circumferential surface is defined as the maximum distance between the first and second side walls 31, 32, which is defined as the distance between the center radial bore, the first side radial bore or the second side radial bore ≪ / RTI > The thickness 23 of the bore 13 in the inner peripheral surface 15 is substantially equal to the thickness of the bore 13 in the outer peripheral surface 16. [ In the present embodiment, there is no point where the thickness of the inner circumferential surface 15 is larger than the thickness of the outer circumferential surface 16.

Figure 5 shows the C portion of the radial bore 13 produced by milling. In this case, the side walls 31, 32 do not have any protrusions or recesses. The thickness 23 of the bore 13 corresponds to the diameter of the bore 13. The thickness 23 of the bore 13 in the inner peripheral surface 15 is substantially equal to the thickness of the bore 13 in the outer peripheral surface 16. [

However, there is a possibility that at least one position where the thickness at the inner circumferential surface 15 is slightly larger than the thickness at the outer circumferential surface 16 may exist. If the thickness 23 of the bore is 15% or less, preferably 10% or less, particularly preferably 5% or less, from the thickness at the peripheral surface, a favorable distribution of the stress can be observed.

6 is a cross-sectional view of the accumulator unit 7 taken along a plane perpendicular to the longitudinal axis 14. Fig. The width 22 of the radial bore 13 is defined by the distance between the first sidewall and the second sidewall 18, 19 of the radial bore in a plane including the central axis 17 of the radial bore 13 . The width is larger at the inner circumferential surface 15 than at the outer circumferential surface 16 and is continuously reduced from the inner circumferential surface 15 to the outer circumferential surface 16. [ The reduction in width occurs progressively, so that it is substantially linear. In the cross section shown in Fig. 6, the reduction is shown by a straight line.

7 is a view of a radial bore viewed from the outer peripheral surface of the accumulator unit. The width 22 of the central bore 11 in the inner peripheral surface 15 is at least twice the width of the radial bore 13 in the outer peripheral surface 16. [

In the further embodiment shown in Fig. 8, the flat surface 32 may be machined on the outer surface 16. Thereby, the segment of the main body 10 of the accumulator unit 7 may be removed. Thereby, the outer circumferential surface 16 of the body 10 is planarized at the position of the radial bore 13. Advantageously, the maximum thickness of the segment is 30% or less of the distance between the inner and outer circumferential surfaces, preferably 25% or less of this distance, particularly preferably 15% or less of this distance. The maximum thickness is the flat surface measured at an angle of 90 ° from the flat surface and is the distance from the original outer surface before machining. That is, the maximum thickness is the shortest distance between the parallel plane and the flat plane forming the plane tangent to the original outer circumferential surface.

 The bore may be provided with a concave portion on the outer circumferential surface (16). Two examples of such recesses are shown in Figs. 9 and 10. Fig. This recess may also be used to attach the adapter member for the high-pressure conduit exiting the radial bore 13. According to Fig. 9, the concave portion 34 is conical. According to Fig. 10, the concave portion 35 is cylindrical. Advantageously, if the concave portion is directly machined on the original outer circumferential surface, the depth of the concave portion is not more than 30% of the distance between the outer circumferential surfaces, preferably not more than 25% of the distance, particularly preferably not more than 15% of the distance.

9 and 10, the depth of the segment to be removed and the depth of the recesses 34, 35 in order to obtain the flat surface 32 at the time of combination are determined by the inner circumferential surface 15 Of the distance between the outer circumferential surface 16 and the outer circumferential surface 16, preferably not more than 25% of the distance, particularly preferably not more than 15% of the distance.

In the embodiment according to Fig. 11, a cross section through the main body 10 of the accumulator unit 7 is shown. The outer circumferential surface 16 need not be concentric with the inner circumferential surface 15. The central bore 11 has a longitudinal axis 36 which does not correspond to the longitudinal axis 14 of the body 10 of the accumulator unit 7. [ The longitudinal axis 14 can be parallel to the longitudinal axis 36 as shown in Figure 11 but the longitudinal axis 14 and the longitudinal axis 36 form a staggered arrangement That is, they can be arranged at an angle with respect to each other.

In Fig. 12, a cross section through the main body 10 of the accumulator unit 7 of the further embodiment is shown. In this case, the outer peripheral surface has a square shape. The inner peripheral surface 15 is circular. Alternatively, at least one of the outer circumferential surface 16 and the inner circumferential surface 15 may have a polygonal cross-section, i.e., a triangular, rectangular or hexagonal cross-section.

As described above, the present invention should not be construed as being limited to any form in the embodiment according to the drawings. Many other various embodiments can be implemented within the scope of the spirit of the present invention and the appended claims. The reference numerals in the drawings are the same for parts having the same function.

The tension in the body of the pressure reservoir of the common rail system, which is caused by a high pressure difference in the system or a total dynamic pressure fluctuation, can be clearly reduced in a simple manner by the present invention. In particular, in the region where the through bore through which the medium passes under high pressure can be extracted, the increase in the stress in the wall of the pressure reservoir is considerably reduced. By this means, for a given fatigue strength of the material constituting the body of the pressure reservoir, the allowable internal pressure and the bandwidth of the dynamic pressure fluctuations can be considerably increased, and / or the external dimensions of the pressure reservoir can, Its diameter can be reduced, for example because the walls of the body can be made thin. Thereby, notable gains in space occur in operation, significant savings in weight up to several hundred kilos of weight can occur, and the pressure reservoir can be made even more economically.

Claims (15)

1. A high-pressure fluid supply device (1) for a common rail system for a large internal combustion engine,
And an accumulator unit (7) for supplying a high-pressure fluid to the plurality of fluid ejection apparatuses (8)
The accumulator unit 7 has an outer peripheral surface 16 and a central bore 11 extending along the longitudinal axis 14 of the accumulator unit 7 and having an inner peripheral surface 15,
At least one radial bore 13 extends from the central bore 11 to the outer peripheral surface 16 of the accumulator unit 7,
The radial bore 13 has a width 22 measured in a plane perpendicular to the longitudinal axis 14 of the accumulator unit 7 and in a direction perpendicular to the central axis 17 of the radial bore 13 And its width is larger at the inner circumferential surface 15 than at the outer circumferential surface 16 and continuously decreases from the inner circumferential surface 15 to the outer circumferential surface 16 for at least half of the distance between the inner circumferential surface 15 and the outer circumferential surface 16 ,
The radial bore 13 includes a central radial bore 25, a first side radial bore 26 and a second side radial bore 27,
The central drill hole 28 in the outer circumferential surface 16 is identical to the central radial bore 25 and the first and second side radial bores 26 and 27,
The first side radial bore 26 and the second side radial bore 27 are angled relative to the central radial bore 25 so that the first and second side radial bores 26, Is partially overlapped with said central radial bore (25) only in said inner peripheral surface (15). The method according to claim 1,
Characterized in that the continuous reduction is linear. ≪ RTI ID = 0.0 > [0002] < / RTI > The method according to claim 1,
Characterized in that the width (22) of the radial bore (13) in the inner peripheral surface (15) is at least twice the width of the radial bore (13) in the outer peripheral surface (16) Supply device. The method according to claim 1,
Wherein the central bore (11) has a circular cross-section. The method according to claim 1,
Wherein the pressure of the high-pressure fluid is 600 to 2000 bar. The method according to claim 1,
Wherein the radial bore (13) has a thickness on the outer circumferential surface (16) equal in width to the outer circumferential surface. The method according to claim 1,
Wherein the radial bore has a thickness on the inner circumferential surface that is not more than 15% of the thickness on the outer circumferential surface of the common rail system. The method according to claim 1,
Wherein the high-pressure fluid is a fuel. The method according to claim 1,
Wherein the high-pressure fluid is a servo oil or water. An internal combustion engine (100) comprising a cylinder (101) in which a piston (103) is arranged to be movable back and forth along a longitudinal cylinder axis (107) at a top dead center position and a bottom dead center position,
In the cylinder 101, a combustion chamber 104 is formed by the cylinder cover 102, the cylinder wall 105 of the cylinder 101, and the piston surface 106 of the piston 103, and the fuel injection device is connected to the combustion chamber Characterized in that it is provided for fuel injection and comprises a high-pressure fluid supply device (1) according to any one of claims 1 to 9. 11. The method of claim 10,
Wherein the internal combustion engine is a dual fuel engine or a gas engine operable in one of a crosshead type engine, a trunk piston engine, a two-stroke or four-stroke internal combustion engine, a diesel or an otto mode. 10. A method of manufacturing a high-pressure fluid supply device (1) according to any one of claims 1 to 9,
And milling said radial bore (13). ≪ RTI ID = 0.0 > 11. < / RTI > 10. A method of manufacturing a high-pressure fluid supply device (1) according to any one of claims 1 to 9,
And drilling said radial bore (13). ≪ RTI ID = 0.0 > 11. < / RTI > 13. The method of claim 12,
Wherein the milling step is performed from an outer peripheral surface (16) to an inner peripheral surface (15) of an accumulator unit (7) including a central bore (11). 14. The method of claim 13,
Wherein said drilling is performed from an outer peripheral surface (16) to an inner peripheral surface (15) of an accumulator unit (7) including a central bore (11).

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