JP2018173086A - High pressure fluid rail - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a high pressure fluid supply device for a common rail system for a large-sized internal combustion engine.SOLUTION: A high pressure fluid supply device has a pressure accumulator unit 7 including a central bore having an outer peripheral surface, substantially extending along a longitudinal shaft 14 of the pressure accumulator unit 7 and having an inner peripheral surface 15, the bore 13 in a radial direction extends from a central bore to the outer peripheral surface 16. The bore 13 in a radial direction has a width 22 measured at a plane perpendicular to the longitudinal shaft 14, the width 22 is larger at the inner peripheral surface 15 than the outer peripheral surface 16 and it is reduced continuously from the inner peripheral surface 15 to the outer peripheral surface 16. The bore 13 in the radial direction has the first and second outer walls 18, 19, the width 22 includes a center axis of the bore 13 in the radial direction and measured as a distance between the first and second outer walls 18, 19 at a plane arranged in perpendicular to the longitudinal axis 14.SELECTED DRAWING: Figure 6

Description

  The present invention relates to a high-pressure fluid rail for the storage of high-pressure fluids used in particular for piston engines.

  In a diesel engine common rail fuel injection system, fuel is supplied to a high pressure fuel reservoir, such as a high pressure accumulator or a so-called common rail, using low and high pressure pumps. From the high pressure fuel reservoir, fuel is further supplied to each cylinder fuel injector along an independent conduit. Fuel is directed from the fuel injector to the respective combustion chambers of the cylinders at desired moments in response to engine operation. There can be several high pressure fuel reservoirs, whereby fuel is supplied from each fuel reservoir to two or more injection nozzles.

  The fuel pressure in the high-pressure fuel reservoir is high, even 2000 bar, so that the fuel accumulator is strong, leading to cracks that can develop in the structural material, in particular in the area of the opening of the cross section of the fuel reservoir wall and its sharp edges Exposed to stress.

  The maximum pressure typically occurs in a fuel injection common rail system. Due to the high fluid pressure up to 2000 bar, the dynamic load caused by this high fluid pressure change results in high stress, the walls of the fuel space must withstand long operating cycles. Especially in marine engines, it is essential that a long operating period can be guaranteed, since the rails must not be replaced or repaired during the service life of the engine.

  The strength of the fuel space wall is limited in particular by a radial bore extending from the central bore. The local stress caused by these radial bores can be increased by three or four factors.

  Patent document 1 discloses a fuel storage part for a piston engine, and a fuel space is constituted by two elongated cylindrical bores. The two elongated cylindrical bores are arranged such that the cross-sections partially overlap thereby forming the main bore. The main bore of the rail of the Waertsilae RT-flex engine is machined with two eccentric bores where the cross section of the main bore will have a peanut shape. From the main bore, an auxiliary bore connects the fuel space to the fuel injector supply conduit. The connecting hole for the auxiliary bore is arranged at the intersection of the two eccentric bores. This reduces the stress at the intersection between the connecting hole drilling and the two main rail drilling because the intersection between the bores is not directly exposed to the main force line.

  U.S. Pat. No. 6,057,051 discloses a fuel reservoir having an orifice opening into the fuel space that is configured to reduce stress applied to 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. Therefore, the durability of the fuel storage unit is increased.

  However, the solution proposed in US Pat. No. 6,057,056 has several drawbacks that prevent its use with a considerable length of fuel rail. The recess must be machined from the inside, meaning from the central bore. Due to the fact that the tool for machining the recess can only project a short distance into the central bore, such a solution has a bore diameter of the central bore of up to 100 mm while having an overall length of at least 1 meter, Not applicable to long and thin fluid spaces.

European Patent No. 1413744 International Publication No. 2008/145818 European Patent Application No. 1426607 European Patent No. 2299102

  An object of the present invention is to provide a fluid space having one or more auxiliary bores that can be used for such a long, thin fluid space.

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

  A high pressure fluid supply device for a common rail system for a large internal combustion engine includes a pressure accumulator unit for supplying high pressure fluid to a plurality of fluid injectors. The accumulator unit has an outer peripheral surface and is disposed in a central bore that extends substantially along the longitudinal axis and inner peripheral surface of the accumulator unit. 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 pressure accumulator unit that has a width at the inner peripheral surface that is greater than the width at the outer peripheral surface, and this width is from the inner peripheral surface to the outer peripheral surface. , Preferably decreasing continuously for at least half of the distance between the inner and outer peripheral surfaces. The radial bore has a first outer wall and a second outer wall. The width is measured as the distance between the first and second outer walls of the radial bore in a plane that includes the central axis of the radial bore and is disposed perpendicular to the longitudinal axis of the accumulator unit.

  According to an embodiment, the continuous decrease is substantially linear. Thereby, it is intended that the first outer wall and the second outer wall are represented as straight lines in a cross section along a plane perpendicular to the longitudinal axis of the accumulator unit including the axis of the radial bore. . The opening angle between the first and second outer walls is in the range of 10 to 75 degrees, preferably 10 to 60 degrees, particularly preferably 10 to 45 degrees. The opening angle is constant from the inner peripheral surface to the outer peripheral surface.

  The radial bore width at the inner peripheral surface is at least twice the width at the outer peripheral surface. The width of the radial bore at the inner peripheral surface is measured in a projection onto a plane containing the longitudinal axis of the accumulator unit when viewed in the axial direction of the radial bore. The width is the distance from the first outer wall to the second outer wall.

  If the width at the inner circumferential surface is significantly greater than the width at the outer circumferential surface, and therefore at least twice the width at the outer circumferential surface, the stress acting on the inner circumferential surface of the pressure accumulator unit around the radial bore is For example, it can be distributed over a significantly wider surface than a cylindrical bore as disclosed in US Pat. Furthermore, due to the fact that the first outer wall extending between the inner and outer peripheral surfaces has a constant angle of inclination, the stress is also not subject to sudden changes in the wall as is present, for example, in US Pat. Due to that, it is reduced in a particularly smooth manner.

  In an embodiment, the central bore has a circular cross section. Such a central bore is particularly easy to manufacture, which means that an accumulator unit length of 2-3 meters is possible and can be manufactured at low cost. Due to the fact that the pressure of the high-pressure fluid can range from 600 to 2000 bar, the central bore with a circular cross section is the most advantageous shape for the pressure distribution. However, it is also possible to use an elliptical shape or a shape as disclosed in Patent Document 1.

  The radial bore has a thickness that is approximately the same size as the width at the outer peripheral surface. The thickness of the bore is measured in the 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 the thickness of the bore at the outer peripheral surface small, the stress acting on the tube wall near the outer peripheral surface is reduced. Furthermore, a minimum of material will be discarded, which on the one hand reduces waste and surprisingly also has a beneficial effect on the stress distribution. Thus, in an embodiment, the radial bore has a certain thickness at the inner peripheral surface, which is not more than 15%, preferably not more than 10%, particularly preferably not more than 5% from the thickness on the outer peripheral surface. Sneak away.

  The high pressure fluid supply device according to one embodiment can be advantageously used for fuel or servo oil or water as high pressure fluid.

  The internal combustion engine in which the high pressure fluid supply is most advantageously utilized has a cylinder. In this cylinder, a piston is arranged so as to reciprocate between a top dead center position and a bottom dead center position along the longitudinal cylinder axis. Within the cylinder, the combustion chamber is surrounded by the cylinder cover, the cylinder wall of the cylinder and the piston surface of the piston. A fuel injector is provided for injecting fuel into the combustion chamber, and a high pressure fluid supply device according to one of the previous embodiments may be used to supply high pressure fuel to the fuel injector. The internal combustion engine can be configured as a crosshead engine, in particular a crosshead large diesel engine, a trunk piston engine, a two-stroke or four-stroke internal combustion engine, a dual fuel engine operable in diesel or otto mode, or a gas engine.

  The method of manufacturing a high pressure fluid supply device for any embodiment includes milling or drilling the radial bore. When the radial bore is drilled, the drilling is performed by drilling the central radial bore and at least one further side radial bore, the drill holes in the central radial bore and the side radial bore Are the same on the outer peripheral surface and are inclined relative to the central radial bore hole on the inner peripheral surface. The step of milling or drilling is performed from the outer peripheral surface of the pressure accumulator unit to the inner peripheral surface. This accumulator unit includes a central bore. Surprisingly, the milling or drilling step can be performed from the outer peripheral surface of the accumulator unit. This is an unexpected advantage over the prior art as disclosed in Patent Document 2 or Patent Document 4. The recesses in these disclosures must be machined from the central bore and are quite cumbersome. Furthermore, drilling or milling tools cannot be introduced into the accumulator unit as a single long tube. Therefore, a plurality of short accumulator units must be used as shown in US Pat. This results not only in the assembly of these prior art accumulator units, but also their control becomes more difficult and time consuming.

  Thus, the accumulator unit can be particularly advantageously configured as an elongated tube. The fluid space inside the central bore can be a fuel space, a servo fluid space, but can also be a gas space or a space used for water injection. The fluid space is surrounded by an inner peripheral surface and the bore may be closed by a closing stopper at at least one end.

  At least one of the outer peripheral surface or the inner peripheral surface of the main body of the accumulator unit may have a circular, elliptical, or polygonal cross section such as a rectangular, in particular a square, triangular or hexagonal cross section. Furthermore, the outer peripheral surface need not be concentric with the inner peripheral surface. Accordingly, the central bore may have a longitudinal axis that is not the same as the longitudinal axis of the body of the accumulator unit.

  Using a pump, fuel for injection, for example hydraulic oil for driving a valve, or working medium, for example for controlling a fuel injector, is supplied from the fluid space to the desired application under high pressure. The accumulator unit forms a common rail for supplying high pressure fluid to a plurality of used ones. For this reason, multiple radial bores can be envisaged. In the case of a fuel injection common rail system, fuel is distributed by a common rail to fuel injectors located in each cylinder via a fuel conduit. The fuel injector includes a fuel injection nozzle for supplying fuel to the combustion chamber of each cylinder.

  The present invention will now be described with reference to the accompanying drawings.

FIG. 1 shows the arrangement of a high pressure fluid supply for a fuel injection common rail system for a large internal combustion engine. FIG. 2 shows a cross section of the pressure accumulator unit along the longitudinal axis of the pressure accumulator unit. FIG. 3 shows a cross section taken along line BB in FIG. FIG. 4 shows a C-direction view of a radial bore manufactured by drilling. FIG. 5 shows a C-direction view of a radial bore manufactured by milling. FIG. 6 shows a cross-sectional view of the pressure accumulator unit along a plane perpendicular to the longitudinal axis of the pressure accumulator unit. FIG. 7 is a view of the radial bore from the outer peripheral surface of the pressure accumulator unit. FIG. 8 shows a cross-sectional view of an accumulator unit along a plane perpendicular to the longitudinal axis of another accumulator unit. FIG. 9 shows a cross-sectional view of an accumulator unit along a plane perpendicular to the longitudinal axis of another accumulator unit. FIG. 10 shows a cross-sectional view of an accumulator unit along a plane perpendicular to the longitudinal axis of another accumulator unit. FIG. 11 shows a cross-sectional view of an accumulator unit along a plane perpendicular to the longitudinal axis of another accumulator unit. FIG. 12 shows a cross-sectional view of an accumulator unit along a plane perpendicular to the longitudinal axis of another accumulator unit.

  FIG. 1 shows a fuel supply device 1 for a diesel engine having several cylinders, in particular a large diesel engine. Large diesel engine refers herein to an engine that can be used, for example, as a main or auxiliary engine in a ship or power plant for the production of power and / or heat. Fuel is supplied from the fuel tank 2 to the high pressure fuel storage 5 along the pipe 3 by the pump 4. The high pressure fuel storage unit 5 is configured as a 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 the timing of operation of the fuel injector 8 based on engine parameters such as engine load or engine speed. Further, the control unit receives an input from the pressure sensor 21 attached to 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 by controlling the rotational speed of the pump motor 24, for example.

  According to an alternative embodiment, a plurality of high-pressure pumps 4 can be provided. Each pump may include a control valve and a piston member (not shown). The piston member may receive guidance from the cam member of the engine camshaft. If necessary, each cam member includes a number of cams, so that when the high pressure pump 4 provides a constant volume flow rate per unit time to the accumulator unit 7, the pump dimensions are each kept smaller. As a result, the pressure impact caused by the pump to the accumulator unit is smaller.

  The accumulator unit 7 is in turn connected to the fuel injector 8 of each cylinder by an independent fuel injection conduit 9. The accumulator unit 7 is therefore connected to two or more fuel injectors 8.

  The fuel pressure in the accumulator unit 7 is at least 600 bar, typically 1000-2000 bar. The operation of the high-pressure pump 4 and the injection pressure used can be controlled according to the engine load, the operating speed or other parameters of the method thus known.

  FIG. 1 schematically shows a cylinder device 100 according to the invention with a fuel injection device according to the invention for an internal combustion engine which is a longitudinal scavenging crosshead large diesel engine in this embodiment. A cylinder apparatus 100 according to FIG. 1 includes a cylinder 101 in which a piston 103 is arranged so as to reciprocate between a top dead center position and a bottom dead center position along a longitudinal cylinder axis 107. Within the cylinder 101, a combustion chamber 104 is defined by a cylinder cover 102, a cylinder wall 105 of the cylinder 101 and a piston surface 106 of the piston 103. Here, only one charge cycle valve 109, which is an outlet valve, is provided in the gas exchange opening 110 of the cylinder cover 102, and the gas exchange opening 110 is connected to a turbocharger not shown in a manner known per se via a gas supply conduit 111. Connected to the assembly. The charge cycle valve 109 is a valve disk that cooperates in operation with the valve seat 113 of the gas exchange opening 110 in such a way that the combustion chamber 104 is sealed to the gas supply conduit 111 in the closed position of the charge cycle valve 109. 112, and in the open position of the charge cycle valve 109, the combustion gas may exit the combustion chamber 104 and be supplied to the turbocharger assembly.

  FIG. 2 shows a cross section of the pressure accumulator unit 7 along the longitudinal axis of the pressure accumulator unit 7. The accumulator unit 7 has a body 10 with an elongated fuel space for pressurized fuel. The fuel space has a cylindrical central bore 11. As shown in FIG. 6, the cross section of the central bore 11 is circular. The central bore 11 extends along the longitudinal axis of the pressure accumulator unit 7. Typically, the bore diameter is in the range of 20 to 100 mm. In addition, the main body 10 has a supply path (not shown in FIG. 2) from the pipe 3. This supply path opens into the fuel space. The pressurized fuel is led from the high-pressure pump 4 along the pipe 3 through the supply path to the fuel space. Furthermore, the main body 10 has a discharge path. The discharge path opens into the fuel space, and fuel is discharged from the fuel space through the discharge path and led to the injection nozzle of the fuel injector 8 (see FIG. 1). An independent discharge path is assumed for each injection nozzle, which is in fluid connection with the pressure accumulator unit 7. A radial bore 13 is assumed for each discharge path. The radial bore extends from the inner peripheral surface 15 of the central bore 11 to the outer peripheral surface 16 of the main body 10. Each radial bore 13 has a longitudinal axis 17.

  As high fuel pressure spreads through the fuel space, cracks and fractures due to material fatigue can propagate into the material of the body 10, particularly in the region of the radial bore 13 for the discharge path. In order to prevent such damage to the accumulator unit, the radial bore 13 has a width measured in a plane perpendicular to the longitudinal axis 14 of the accumulator unit 7. This width is larger at the inner peripheral surface 15 than at the outer peripheral surface 16, and continuously decreases from the inner peripheral surface 15 to the outer peripheral surface 16 as shown in FIGS. According to FIG. 3 or 6, the radial bore has a first outer wall 18 and a second outer wall 19.

  FIG. 3 shows a cross section taken along line BB in FIG. The radial bore 13 shown in FIG. 3 is manufactured by a drilling method. Drilling is performed by drilling the central radial bore 25 and the first and second side radial bores 26,27. The central radial bore 25 and the central drill holes 28 of the first and second side radial bores 26, 27 are the same on the outer peripheral surface 16 of the body 10. The first and second side radial bores 26, 27 are inclined with respect to the central radial bore 25. Accordingly, the first and second side drill holes 29, 30 of the first and second side radial bores 26, 27 only partially overlap the central radial bore 25 at the inner peripheral surface 15.

  FIG. 4 shows a C-direction view of a radial bore produced by drilling, which is basically the radial bore shown in FIG. The first and second side walls 31, 32 extend between the first and second outer walls 18, 19. Because of the circular shape of the drill, each of the central radial bore and the first and second side radial bores are cylindrical. Due to the fact that at the height of the inner peripheral surface 15 the central radial bore, the first and second side radial bores no longer completely overlap, the first and second side walls 31, 32 have protrusions and recesses. including. The thickness of the radial bore at the inner peripheral surface is defined as the maximum distance between the first and second side walls 31, 32. This maximum distance corresponds to the diameter of one of the central radial bore, the first and second side radial bores. Therefore, the thickness 23 of the bore 13 at the inner peripheral surface 15 is substantially equal to the thickness 23 of the bore 13 at the outer peripheral surface 16. In this embodiment, there is no place where the thickness on the inner peripheral surface 15 exceeds the thickness on the outer peripheral surface 16.

  FIG. 5 shows a C-direction view of the radial bore 13 manufactured 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. Therefore, the thickness 23 of the bore 13 at the inner peripheral surface 15 is substantially equal to the thickness of the bore 13 at the outer peripheral surface 16.

  However, the thickness on the inner peripheral surface 15 may be slightly larger than the thickness on the outer peripheral surface 16 in at least one place. An advantageous distribution of stress can also be observed when the bore thickness 23 deviates from the thickness at the outer circumference to 15% or less, preferably 10% or less, particularly preferably 5% or less.

  FIG. 6 shows a cross-sectional view of the pressure accumulator unit 7 along a plane perpendicular to the longitudinal axis 14 of the pressure accumulator unit 7. The width 22 of the radial bore 13 includes first and second outer walls of the radial bore in a plane that includes the central axis 17 of the radial bore 13 and is disposed perpendicular to the longitudinal axis 14 of the accumulator unit 7. Measured as the distance between 18 and 19. The width is larger at the inner peripheral surface 15 than at the outer peripheral surface 16, and continuously decreases from the inner peripheral surface 15 to the outer peripheral surface 16. The reduction in width occurs gradually and is therefore almost linear (linear, linear). In the cross section shown in FIG. 6, the decrease is shown as a straight line.

  FIG. 7 is a view of the radial bore from the outer peripheral surface of the pressure accumulator unit. The width 22 of the radial bore 13 at the inner peripheral surface 15 is at least twice the width of the radial bore 13 at the outer peripheral surface 16.

  In a further embodiment shown in FIG. 8, the flat surface 32 can be machined on the outer peripheral surface 16. Therefore, a part of the main body 10 of the pressure accumulator unit 7 can be removed. Thereby, the outer peripheral surface 16 of the body 10 is flattened at the position of the radial bore 13. Advantageously, the maximum thickness of the part is not more than 30% of the distance between the inner and outer peripheral surfaces, preferably not more than 25% of the distance, particularly preferably not more than 15%. The maximum thickness is the distance from the unprocessed outer peripheral surface to the flat surface before machining, measured at a 90 degree angle from the flat surface. In other words, the maximum thickness is the shortest distance between the flat surface and the parallel surface forming the tangent plane to the raw outer peripheral surface.

  The bore may also be recessed on the outer peripheral surface 16. Two examples of such recesses are shown in FIGS. Such a recess can be used to attach an adapter element for a high-pressure conduit leaving the radial bore 13. According to FIG. 9, the recess 34 has a conical shape. According to FIG. 10, the recess 35 is cylindrical. Advantageously, the depth of the recess is not more than 30% of the distance between the inner and outer peripheral surfaces, preferably not more than 25% of the distance, when the recess is machined directly into the raw outer peripheral surface. Particularly preferably, it is 15% or less.

  When it is assumed that the concave portion is combined with the flat surface as shown in FIGS. 9 and 10, the combination of the depth of the portion removed to obtain the flat surface 32 and the depth of the concave portions 34 and 35 is It should be 30% or less of the distance between the peripheral surface 15 and the outer peripheral surface 16, preferably 25% or less, particularly preferably 15% or less of the distance.

  In the embodiment according to FIG. 11, a cross section through the body 10 of the accumulator unit 7 is shown. The outer peripheral surface 16 need not be concentric with the inner peripheral surface 15. Accordingly, the central bore 11 has a longitudinal axis 36 that does not coincide with the longitudinal axis 14 of the body 10 of the pressure accumulator unit 7. As shown in FIG. 11, the longitudinal axis 14 can be parallel to the longitudinal axis 36, but the torsional shape such that the longitudinal axis 14 and the longitudinal axis 36 are disposed at an angle relative to each other, for example. Form a staggered arrangement.

  In FIG. 12, a section through the body 10 of the accumulator unit 7 of a further embodiment is shown. In this case, the outer peripheral surface is a square. The inner peripheral surface 15 is a circle. Alternatively, at least one of the outer peripheral surface 16 and the inner peripheral surface 15 may have a polygonal cross section such as a triangular, rectangular or hexagonal cross section.

  From the above, the present invention should not be construed as being limited in any way to the illustrated embodiments. The present invention may be implemented in many different embodiments within the spirit of the invention and the appended claims. The reference numerals in the figure are the same for parts having the same function.

  The tension in the basic body of the pressure reservoir of a common rail system, caused by high pressure differences or through dynamic pressure fluctuations in the system, is clearly reduced in a simple manner using the present invention. obtain. In particular, in the region of the through bore, where the medium under high pressure can be drawn, the increase in stress on the walls of the pressure reservoir is greatly reduced. In this way, for a given fatigue strength of the material from which the basic body of the pressure reservoir is made, the range of allowable internal pressure and dynamic pressure fluctuations can be greatly increased and / or, for example, basic Since the body wall can be made thin, the external dimensions, in particular the diameter, of the pressure reservoir can be reduced. Thus, not only a significant increase in space in the operating state and a considerable reduction in weight up to several hundred kilograms, the pressure reservoir can be manufactured considerably cheaper.

Claims (15)

A central bore having an accumulator unit for supplying high pressure fluid to a plurality of fluid injectors, the accumulator unit having an outer peripheral surface and extending substantially along a longitudinal axis of the accumulator unit; A high pressure fluid supply device for a common rail system for a large internal combustion engine, wherein 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 is larger on the inner peripheral surface than the outer peripheral surface, and continuously from the inner peripheral surface to the outer peripheral surface, preferably for at least half of the distance between the inner peripheral surface and the outer peripheral surface. Decreased,
The radial bore has a first outer wall and a second outer wall;
The width includes a central axis of the radial bore and the first outer wall and the second outer wall of the radial bore in a plane disposed perpendicular to the longitudinal axis of the accumulator unit. Measured as the distance between
High pressure fluid supply device. The continuous decrease is substantially linear;
The high-pressure fluid supply apparatus according to claim 1. The width of the radial bore at the inner peripheral surface is at least twice the width of the radial bore at the outer peripheral surface;
The high-pressure fluid supply apparatus according to claim 1 or 2. The central bore has a circular cross section;
The high-pressure fluid supply apparatus according to any one of claims 1 to 3. The pressure of the high-pressure fluid is in the range of 600 to 2000 bar;
The high-pressure fluid supply apparatus according to any one of claims 1 to 4. The radial bore has a thickness of approximately the same size as the width at the outer peripheral surface at the outer peripheral surface;
The high-pressure fluid supply apparatus according to any one of claims 1 to 5. The radial bore has a thickness that deviates from the thickness of the outer peripheral surface to 15% or less, preferably 10% or less, particularly preferably 5% or less at the inner peripheral surface.
The high-pressure fluid supply apparatus according to any one of claims 1 to 6. The high-pressure fluid is fuel;
The high-pressure fluid supply apparatus according to any one of claims 1 to 7. The high-pressure fluid is servo oil or water.
The high-pressure fluid supply apparatus according to any one of claims 1 to 8. A piston, wherein the piston is arranged to reciprocate between a top dead center position and a bottom dead center position along a longitudinal cylinder axis, wherein the combustion chamber has a cylinder cover; The high pressure fluid supply device according to any one of claims 1 to 9, wherein the high pressure fluid supply device according to any one of claims 1 to 9, is surrounded by a cylinder wall of the cylinder and a piston surface of the piston, and a fuel injector is provided for injecting fuel into the combustion chamber. Including,
Internal combustion engine. Said internal combustion engine is a crosshead engine, in particular a crosshead large diesel engine, a trunk piston engine, a two-stroke or four-stroke internal combustion engine, a dual fuel engine operable in diesel or Otto mode, or a gas engine,
The internal combustion engine according to claim 10. Milling said radial bore;
A method for manufacturing the high-pressure fluid supply apparatus according to any one of claims 1 to 9. Drilling the radial bore;
A method for manufacturing the high-pressure fluid supply apparatus according to any one of claims 1 to 9. The drilling is performed by drilling a central radial bore and at least one further side radial bore, the drill holes of the central radial bore and the side radial bore being the same on the outer peripheral surface And inclined with respect to the central radial bore hole on the inner peripheral surface,
A method for manufacturing the high-pressure fluid supply apparatus according to claim 13. The milling or drilling step is performed from the outer peripheral surface of the accumulator unit to the inner peripheral surface, and the accumulator unit includes the central bore.
A method for manufacturing the high-pressure fluid supply apparatus according to any one of claims 12 to 14.