CN1392339A - Fuel supply device for IC engine - Google Patents

Abstract

The invention relates to a fuel supply device for an internal combustion engine. Each cylinder of the internal combustion engine has a plurality of fuel injection valves (3), wherein each of these fuel injection valves (3) has at least one leading to a fuel injection hole (17) and can be connected A flow channel (18) of a pressure pipe (9) that can be supplied with fuel by means of a pressure source, the flow channel passes through at least one valve seat (38) that can be pressed against the valve seat (38) under the action of a spring (45) and reaches a predetermined fuel pressure. When the closing body (35) can be lifted from the relevant valve seat (38) by the fuel, this internal combustion engine can obtain good part load characteristics in a simple manner. For this reason, at least one of at least one part of the fuel injection valve (3) The closing body (35), which is penetrated by the flow channel (18), can be pressed against the associated valve seat (38) by means of an associated control piston (46), wherein the closing body (35) is exerted by the control piston (46). ) is greater than the force exerted by the fuel on the closing body (35) at normal opening pressure, but less than the force exerted on the closing body (35) by the maximum allowable fuel pressure.

Description

Internal combustion engine fuel supply device

technical field

The present invention relates to a fuel supply device for an internal combustion engine, especially a large two-stroke diesel engine, which includes fuel injection valves configured for cylinders, preferably each cylinder has a plurality of fuel injection valves, wherein each of these fuel injection valves has at least one channel leading to The fuel injection hole can also be connected to a flow passage of a pressure pipe that can be supplied with fuel by means of a pressure source. The flow passage passes through at least one valve seat that can be pressed against the valve seat under the action of a spring and can be pumped by the fuel from the relevant pipe when the predetermined fuel pressure is reached. The closed body with the valve seat lifted.

Background technique

Such a device is known from EP0744007B1 of the applicant. In this known arrangement it is not possible to deactivate the injection valves individually. Consequently, all injection valves are active even during partial load operation. At lower loads, this results in lower injection pressures and thus poor fuel atomization and incomplete combustion. The result is not only erratic operation, but also an undesired accumulation of residual oil which can lead to severe wear. Devices of the known type have proven to be insufficiently reliable.

Contents of the invention

Proceeding from this, it is therefore the object of the present invention to improve a device of the type mentioned in the introduction by means of simple and economical measures in such a way that at least some existing injection valves can be optionally deactivated.

According to the invention, the measure taken for this purpose is that at least one closure body, which is penetrated by the flow channel in at least one part of the existing fuel injection valve, can be pressed against the relevant valve seat by means of an associated control piston, wherein by The force exerted by the control piston on the closing body is greater than the force exerted on the closing body by the fuel at normal opening pressure, but less than the force exerted on the closing body by the maximum allowable fuel pressure.

In this case, the oil injection can advantageously be stopped by holding the closing body against the associated valve seat with pressure from the control piston and thus closing off the flow in the flow channel. It is thus advantageously possible to deactivate some of the injection valves at part load, so that a comparatively high injection pressure is achieved at the remaining injection valves and thus a good atomization of the fuel is achieved, which leads to complete combustion and prevents undesired accumulation . The disadvantages of the known devices, which have already been described in the introduction, can therefore be completely avoided by taking the measures according to the invention. Due to the fact that the force exerted by the control piston on the relevant closing body is lower than the force exerted on the closing body by the maximum permissible fuel pressure, it is also ensured that mechanical damage to components in the fuel system due to an impermissible pressure increase is avoided, which is critical for operation. Safety plays a beneficial role. If the control piston is not supplied with pressure medium, the fuel injection valve according to the invention works like a conventional fuel injection valve. This ensures that there is no risk of explosion in the event of failure of the loading device associated with the control piston. The measures according to the invention therefore ensure a high degree of reliability and safety. Another advantage is that the device according to the invention can also be used to vary the opening pressure of the closing body. The measures according to the invention therefore also lead to a high degree of versatility.

Advantageous refinements and appropriate further developments of the main measure are specified in the subclaims. For example, the control piston can advantageously be acted upon by means of a hydraulic medium, and this effect can expediently be switched on or off by means of a valve which can be controlled by a controller as a function of the load. These measures provide a very simple construction and high operational reliability. At the same time, very short rest times are advantageously produced. In a large diesel engine, diesel oil is suitably used as a hydraulic medium. This ensures that the resulting mixing with the fuel in the event of a leak of the pressurized fluid is harmless.

Another advantageous measure can be that at least one group of control pistons is assigned a common oil supply circuit connected to the pressure source, provided with a preferably adjustable safety valve, from which some branch lines lead to Relevant control pistons are each provided with a valve that can be controlled by a controller in the branch line. These measures lead to a particularly simple and economical construction of a pressure medium preparation device assigned to all control pistons, which cooperates with the pressure source and the safety valve for limiting the pressure, thus also forming a particularly space-saving location device.

Advantageously, the spring associated with the closing body bears on the control piston. In this case, the spring force is changed by applying pressure to the control piston, so that it is not only possible to simply hold the closing body completely in its closed position by means of the measure according to the invention. Furthermore, to be precise, it is also possible to vary the spring pretension and thus the opening pressure of the closing body in a simple manner. This is appropriately the outlet-side closure which is adjacent to the spout.

The control piston assigned to the first closing body arranged in the inlet region of the fuel injection valve can advantageously be passed through by a guide pin protruding from the shoulder of the fixed support and passed through by the flow channel, the guide pin having a shaft Insertion into the closure body with freedom of movement. These measures provide a reliable axial guidance of the closing body and the associated control piston. At the same time, a very compact closing body-control piston assembly is thus formed which can be used instead of the closing body of the known device, so that it is possible to retrofit the known device easily.

Another advantageous measure can be that the guide pin is provided with a radial circulation hole which opens when the control piston is unloaded and which communicates with the return line. When the internal combustion engine is stopped but remains on standby, this circulation hole ensures fuel system ventilation and fuel circulation, which is especially advantageous when using warmed fuel, especially heavy oil, in order to avoid thermal shock and/or pipe blockage.

Advantageously, the controller can be designed so that at part load the control pistons of the fuel injection valves provided for each cylinder are alternately supplied with pressure at a predetermined rhythm. This makes it possible for the fuel injection valves assigned to each cylinder to be activated or deactivated alternately during partial load operation. This alternating changeover between activation and deactivation prevents the individual injectors from cooling down more severely and thus from shock effects when restarting operation. The same applies to solving the problem of carbon deposits in the nozzle. The above-mentioned measures therefore lead to an increased operational reliability.

Further advantageous refinements and suitable further developments of the main measures are described in the remaining subclaims and can be seen further from the following description of exemplary embodiments with reference to the drawings.

Description of drawings

The accompanying drawings indicate:

Fig. 1 is a schematic diagram of an internal combustion engine with an associated fuel supply system;

FIG. 2 is a longitudinal section through a first embodiment of a fuel injection valve according to the invention;

Figure 3 is an enlarged view of the control valve assembly of the fuel injection valve shown in Figure 2;

Fig. 4 is a schematic diagram of the pressure medium supply device and controller equipped with all fuel injection valve control valve assemblies;

Figure 5 is a horizontal section through the connecting flange of the fuel injection valve shown in Figure 2;

6 through a longitudinal section through a second embodiment of the fuel injection valve according to the invention; and

FIG. 7 is a modification of the device shown in FIG. 4 .

Examples

FIG. 1 schematically shows an internal combustion engine 1 , which may be a large two-stroke diesel engine, for example used as a marine power plant, comprising a plurality of cylinders 2 , only one of which is shown in FIG. 1 . Two fuel injectors 3 are provided per cylinder 2 , to which a common fuel injection pump 4 is always assigned. A common oil supply circuit is arranged for the fuel injection pumps 4 of all the cylinders 2. This oil supply circuit has a precursor branch line 5a and a return flow branch line 5b and is provided with a fuel tank 6, a preparation pump 7 and a pressure regulating valve 8. In the illustrated example, the oil supply circuit 5 is set at a pressure of 8 bar in the precursor branch line 5 a before the pressure regulating valve 8 , and the pressure in the return branch line 5 b after the pressure regulating valve 8 is 4 bar. The suction side of the fuel pump 4 is connected to the forward branch line 5a of the fuel supply circuit, and its return side is connected to the return branch line 5b of the fuel supply circuit. The inlet side of the fuel injection valve 3 is connected via a pressure line 9 to the fuel outlet of the associated fuel pump 4 , and the return side is connected via a return line 10 to the return branch 5 b of the fuel supply circuit 5 .

The fuel injection valve 3 can be fixed on the cylinder head of the respective associated cylinder 2 . As can be seen most clearly in FIG. 2 , the fuel injection valve 3 is provided with a flange 11 at the upper end for this purpose. One side of the flange 11 is provided with a threaded journal 12 for connecting the relevant pressure pipe 9 . On the opposite side, the flange 11 is provided with a threaded flange 13, on which an outer spray pipe 15 can be fixed by means of a lock nut 14, which has a downwardly protruding spray head 16, the spray head An oil injection hole 17 is arranged on the top, and the oil injection hole is fluidly connected to the pressure pipe 9 which can be connected on the threaded journal 12 via a flow channel which is generally indicated by 18 .

Parts that follow one another in the direction of flow from the threaded journal 12 to the spray head 16 are provided with suitable bores for forming the flow channel 18 .

Accordingly, the flow passage 18 passes through the flange 11 including the threaded journal 12, then through the control valve assembly generally indicated at 19 provided inside the sleeve 15, through the intermediate section 20, and then through the control valve assembly provided at the spray head. 16, the closure device indicated in its entirety by 21, then leads into the central opening of the spray head 16, from which the oil spray holes 17 originate.

In the example shown in FIG. 2 , the middle section 20 is provided with upper fixed and lower movable spring disks 22 , 23 for a valve spring 24 designed as a helical spring associated with the closure device 21 . The closing device 21 comprises a closing body 25 supported on a movable spring plate 23 provided with a bearing flange for this purpose, the closing body is guided in a central hole of a valve seat part 26 installed in the sleeve 15, the spray head 16 Connected to the seat portion 26 . The closing body 25 has a front pin 27 which is reduced compared to its guide surface, and which is provided with a conical sealing surface which can be brought into abutment against the associated valve seat surface 28 of the valve seat part 26 . The pin 27 has an axially grooved protrusion at the front, which protrudes through the region of the valve seat part 26 in contact with the spray head 16 and projects into the central bore of the spray head 16 . One end of the valve seat part 26 is supported on the spray head 16, and the other end is supported on the extension section 29 connected with the middle section 20. The extension section is provided with an axial direction that is inserted into the closed body 25 and belongs to the flow channel 18 with an axial movement freedom. The pin in the blind hole 30 is partially surrounded by the spring disk extension already mentioned above.

The closing body 25 can be placed on the pin 27 in contact with the seat surface 28 and, due to its small diameter, is surrounded by an annular cavity 31 , which communicates with the central blind hole 30 via an inclined hole 32 . Once fuel with sufficient pressure enters the annular chamber 31, the closing body 25 is lifted against the action of the valve spring 24, thereby lifting its sealing surface from the relevant valve seat surface 28 and releasing the pressure from the annular chamber 31 to the nozzle. The flow path of the oil hole 17, so the oil injection is carried out.

The control valve assembly 19 has a structure similar to that of the closure means 21 described above. As can be seen most clearly in FIG. 3, the control valve assembly 19 also includes a closure body 35 which is guided in the central bore of the associated valve seat part 36 and has a front pin 37 which has an annular conical shape. A sealing surface which can be brought into abutment against an associated valve seat surface 38 surrounding the lower outlet opening of the valve seat part 36 . As shown in Figure 2, the valve seat part 36 is supported on the middle section 20 with its lower end, and the upper end of the rear sleeve 40 rests on the support 39, and as Figure 2 also shows, the support 39 is inserted into the flange 11 in the relevant slot. The support 39 is provided with a guide pin 41 protruding downwards, which is inserted with axial freedom of movement into the central blind hole 42 of the closure body 35 belonging to the flow channel 18, and the lower end of the spring 45 designed as a pressure spring is supported on this closure body. . The blind hole 42 communicates with an annular cavity 44 surrounding the pin 37 via an inclined hole 43 . Here, too, closing body 35 can be lifted against the action of spring 45 assigned to closing body 35 by the fuel under pressure in annular space 44 .

One end of the spring 45 is supported on the closing body 35, and the other end is supported on the control piston 46 assigned to the closing body 35. The control piston is passed through by the pin 41 of the support 39 and surrounded by the sleeve 40 of the valve seat part 36, so forming An accurate guiding device. The spring 45 is weaker than the valve spring 24, so that the valve seat part 36 is already lifted from the relevant valve seat surface 38 when the fuel pressure is low, and thus fuel can enter the region of the closing component 21.

In the closed position shown in FIG. 3 , the closing body 35 bears with its sealing surface on the relevant seat surface 38 of the valve seat part 36 , and the control piston 46 surrounds the rear piston surface on one of the bearings 39 in the opposite position. On the shoulder surface of pin 41. In this case, the closing body 35 and the control piston 46 are spaced apart from each other, so that a gap 47 is formed in the regions of the opposite end faces. The pin 41 of the support 39 is provided in the region of this gap 47 with a radial bore 48 of smaller diameter starting from the central bore of the support 39 belonging to the flow channel 18 . The radial bore 48 leads into a gap 47 which leads into the region of the annular chamber associated with the spring 45 formed by the closing body 35 and the groove on the peripheral side of the control piston 46 in a bore 49 surrounded by the sleeve 40 of the valve seat part 36 . The bore 49 communicates via a transverse bore 50 with the interior 51 of the outer sleeve 15 , which communicates via the bore system 52 shown in FIG. 2 with the associated return line 10 . The radial bore 48 therefore communicates with an associated return line. When the control piston 46 is lifted, ie when it is in the position shown in FIG. 3 , the circulation hole 48 allows fuel to circulate. This allows the fuel system to be ventilated and prevents unwanted cooling during stand-by-betrieb.

By means of the control piston 46 , the associated closing body 35 can be pressed against the valve seat surface 38 against the action of the fuel present in the annular space 44 and thus held in the closed position. In this way, the injection valve 3 concerned can be deactivated.

To this end, the control piston 46 can be filled with pressure medium in the region of its rear piston face facing away from the associated closing body 35 . Here, a working chamber is formed which is bounded by the piston surface, the shoulder surface of the bearing 39 lying opposite, the pin 41 of the bearing 39 and the sleeve 40 of the valve seat part 36 . A hydraulic medium is suitably used as pressure medium, which is less compressible than a pneumatic pressure medium. In the case of a diesel engine, diesel oil can be used as pressure medium, so that any leakage fluid that may flow out of the above-mentioned working chamber can be taken up by the circulating fuel oil without problems.

The pressure medium is prepared by the preparation device shown in FIG. 4 . It comprises an oil supply circuit with a forward branch line 54 a and a return branch line 54 b, for which an oil tank 55 as well as a preparation pump 56 and an adjustable pressure valve 57 are assigned to the oil supply circuit. Branch lines 58 whose number corresponds to the number of fuel injection valves 3 per cylinder 2 start from the above-mentioned fuel supply circuit, here are two branch lines 58 , which lead to the pressure of each fuel injection valve 3 per cylinder 2 respectively. Media imports. For this reason, as shown by the dotted line in FIG. 4 , the branch line 58 also diverges into branch lines whose number is consistent with the number of cylinders. In each branch line 58, upstream of the branching point, a controllable shut-off valve 59 is provided. Here it can be an electromagnetic slide valve. The shut-off valve 59 can be controlled by means of a controller 60 including a computer, as indicated schematically by a signal line 61 .

The pressure that can be generated by means of the pump 56 should be such that the pressure-loaded control piston 46 can exert a force on the associated closing body 35 that is greater than the force exerted on the closing body 35 by the spring 45 during normal fuel injection operation. That is to say greater than the force exerted by the fuel on the closing body 35 at a normal opening pressure. The upper limit of the force exerted on the closing body 35 is defined by the pressure valve 57 . The pressure valve is adjusted so that there is no mechanical damage to the components due to excessive fuel pressure, which means that the closing body 35 is lifted from the relevant valve seat 38 before the weakest component can be mechanically damaged, and thus the fuel The system is unloaded upstream of seat 38 .

When the control piston 46 pressing down on the closing body 35 is loaded, the circulation bore 48 is covered by the control piston 46 so that no fuel circulation takes place. This ensures that the required high injection pressure is achieved at the active injection valve.

By appropriately applying pressure to the control piston 46 of the fuel injection valve 3, this fuel injection valve can be optionally deactivated. Therefore, when the load on the engine 1 is low, one of the two injection valves 3 per cylinder 2 can always be deactivated, so that the fuel can be delivered even when the fuel demand is low. Accurate dosing ensures high injection pressure and thus good atomization of the fuel, resulting in complete combustion. Thus, by appropriately controlling the valves 59 by the computer of the control device 60 , below a defined partial load, only one injection valve 3 per cylinder 2 is always activated, while the remaining injection valves 3 are deactivated. Accordingly, the computer of the controller 60 is provided with an appropriate entry 62 for the load signal. In order to obtain as uniform a thermal load as possible for all injection valves 3 even in partial load operation of the above-mentioned type and to avoid deposits in the injection holes 17, the injection valves 3 of each cylinder 2 are switched alternately at approximately two-minute intervals. activation or passivation. For this purpose, a program stored in the computer of the controller 60 is correspondingly equipped.

The supply of pressure medium required for actuating the control piston 46 takes place, as shown in FIG. 4 , via the flange 11 of the injection valve 3 . For this purpose, as can be seen from FIG. 5 , the flange 11 is provided with a radial hole 63 to which the branch line 58 can be connected. In the example shown, there are two radial bores arranged in pairs, one of which can always be plugged. This double layout of the radial holes 63 facilitates the routing of the pipelines. The radial bore 63 opens into an annular groove 64 in the region of the recess provided for the bearing 39 in the flange 11 . As shown in FIGS. 2 and 3 , the groove 64 communicates with a bore system 65 which leads on the bearing side to the working chamber associated with the control piston 46 . The flange 11 is also provided with a connecting hole 66 associated with the return line 10 , which communicates with the above-mentioned hole system 52 for the fuel return on the support side.

In the exemplary embodiment described above, a control piston 46 is assigned to the upper closing body 35 of each fuel injection valve 3 . However, it is also conceivable that additionally or as an alternative thereto, a suitable control piston is assigned to the lower closing body 25 for optionally pressing down the closing body 25 against the effect of the fuel pressure, as shown in FIG. 6 . The basic structure of the assembly according to FIG. 6 corresponds to that of the example shown in FIG. 2 . Therefore, mainly only the differences will be described below, wherein the same symbols as above are used for parts that correspond to one another.

In the embodiment according to FIG. 6 , a control piston 70 is assigned to the closing body 25 of the closing device 21 arranged in front of the spray head 16 . Here, the closing spring associated with the upper closing body 35 bears against a suitable shoulder of the support 39, which has an extension surrounded by said shoulder and inserted into the closing body 35, the latter can be provided with a loop holes.

The control piston 70 assigned to the lower closing body 25 here forms an upper support for the valve spring 24 assigned to the closing body 25 , the valve spring 24 here being suitably designed as a disk spring with a steep spring characteristic. The valve seat part 36 assigned to the upper closure body 35 is here provided with a concentric extension 72 surrounded by a shoulder 71, whose lower end abuts against the extension 29 provided with a guide pin inserted in the hole of the closure body 35 Above, the extension 29 rests itself with an upper flange on the valve seat part 26 assigned to the closing body 25 .

Control piston 70 comprises a flange 73, and it acts on the upper end of valve spring 24 and can be supported on the shoulder 71 that upper valve seat part 36 is in the opposite position, on flange 73 is connected an inserting upper valve seat at the rear. Sleeve 74 in part 36 circumferential side grooves, and stretches out from flange 73 downwards a sleeve 75 that is passed by extension section 72 of upper valve seat part 36, installs and guides valve spring on sleeve 75 24. The lower end of the sleeve 75 is inserted into the movable lower spring disk 23 as a guide pipe section, and the spring disk 23 abuts against the closing body 25 with an extension. In this case, the flange 73 of the control piston 70 actually forms the upper spring plate associated with the valve spring 24 , which, in contrast to the embodiment shown in FIG. 2 , is likewise movable in the axial direction.

In order to actuate the control piston 70 , pressure medium can be supplied to the control piston in the rear region of its flange 73 . To this end, the upper seat part 36 is provided with a hole system 65 that extends from the rear end face of the seat part 36 against the support 39 to the shoulder 71 provided for the flange 73 and is provided in the support 39. Connected oil supply hole 76. Through this oil supply hole, the surface of the flange 73 which acts as the piston surface of the control piston 70 and the surface opposite to the shoulder 71 can be loaded with pressure medium. Under appropriate loading, a working chamber is formed bounded by the aforementioned piston face of the flange 73, the shoulder 71, the sleeve 74 and the sleeve 75.

The preparatory device provided for feeding the control piston 70 with pressure medium can correspond to the design shown in FIG. 4 in simple cases, ie only when the time-dependent passivation of the lower closing device 21 is involved. However, according to a preferred embodiment, the pressure medium preparation device can be designed such that, in addition to the possible passivation of the lower closing device 21, the variable adjustability of the opening pressure of the lower closing body 24, that is to say, when the closing body 25 changes from The adjustability of the pressure when the valve seat is lifted is also adjustable during normal operation. Figure 7 shows an embodiment suitable for this pressure medium preparation device.

The basic structure of the device shown in FIG. 7 corresponds to that of the device according to FIG. 4 . Therefore, only the differences are described below, wherein the same symbols are used for mutually corresponding parts.

FIG. 7 shows an embodiment in which three fuel injection valves 3 are assigned to each cylinder 2 , which can be activated or deactivated by actuating a shut-off valve 59 , which can be controlled by a controller 60 , and which is provided in the fuel supply line. In this respect there is agreement with the device according to FIG. 4 . In addition, in the arrangement according to FIG. 7, a control mechanism 77 is provided in the region of the supply circuits 54a, b (from which the branch lines 58 for the injection valves originate), by means of which The desired pressure can be adjusted in the oil supply circuits 54a, b. The control mechanism 77, which can be designed as an adjustable throttling mechanism, is properly arranged in the return branch line of the oil supply circuit 54a, b.

The control mechanism 77 can likewise be controlled by the controller 60 , as indicated schematically by the signal line 78 . Here, the computer of the control unit 60 is designed so that during normal injection operation, that is to say in a phase in which all three injection valves 3 are active, the shut-off valve 59 can be controlled in such a way that the branch line 58 is opened, And the control mechanism 77 is controlled in such a way that there is a desired pressure in the oil supply circuit 54a, b, which is lower than the pressure required to keep the closing body 25 in the permanently closed position. This achieves that the closing body 25 is lifted from the relevant valve seat only when the force exerted on the closing body 25 by the fuel pressure exceeds the force exerted on the closing body 25 by the pressure medium acting on the control piston 70 .

Of course, it is also conceivable to combine the pressure medium preparation device according to FIG. 7 with the device according to FIG. 2 in order to be able to adjust the opening pressure of the upper closing body 35 .

Claims (16)

1. A fuel supply device for an internal combustion engine, especially a two-stroke large diesel engine, which includes a fuel injection valve (3) configured for the cylinder (2), preferably each cylinder (2) has a plurality of fuel injection valves (3), wherein, Each of these fuel injection valves (3) has at least one flow channel (18) leading to the fuel injection hole (17) and can be connected to a pressure pipe (9) that can be supplied with fuel by means of a pressure source. The flow channel passes through at least one Closing bodies (25, 35) which can be pressed against the valve seats (28, 38) under the action of springs (24, 45) and which can be lifted from the relevant valve seats (28, 38) by the fuel when a predetermined fuel pressure is reached , characterized in that at least one closing body (25, 35) through which the flow channel (18) penetrates at least one part of the fuel injection valve (3) can be pressed against the associated control piston (46, 70) by means of an associated On the valve seat (28, 38), where, in order to keep the fuel injection valve (3) in the permanently closed position, the force exerted by the control piston (46, 70) on the closing body (25, 35) is greater than that in the part The force exerted on the closing body (25, 35) by the fuel pressure during load operation is smaller than the force exerted on the closing body (25, 35) by the maximum allowable fuel pressure. 2. The device according to claim 1, characterized in that the control piston (46, 70) can be loaded by means of a preferred hydraulic medium, wherein this loading can be controlled by a load-dependent control piston (60) Valve (59) is switched on and off. 3. The device according to claim 2, characterized in that, for a diesel engine, the control piston (46, 70) can be loaded with diesel as pressure medium. 4. According to the described device of one of the preceding all claims, it is characterized in that: for at least one group of control pistons (46,70) is equipped with a common connection with the pressure source (56), is provided with a preferably adjustable safety The oil supply circuit (54) of the valve (57), some branch lines (58) lead to the relevant control pistons (46, 70) from the oil supply circuit (54), and a valve (59) is respectively established in the branch line, and the valve (59 ) can be controlled by means of a controller (60) having an inlet (62) for a load-dependent signal. 5. The device according to one of the preceding claims, characterized in that the controller (60) for controlling the valve (59) contains a programmable computer. 6. According to the described device of one of the preceding claims, it is characterized in that: the pressure medium preparation device allocated for the control piston (70) is arranged in such a way that the opening pressure of the relevant closing body (25) can be changed adjustable. 7. The device according to claim 6, characterized in that when the fuel injection valve has a plurality of closing bodies (25, 35) arranged one behind the other through which the flow channel (18) passes, the outlet-side closing body (25) ) The opening pressure is variably adjustable. 8. The device according to claim 6 or 7, characterized in that a pressure stabilizing mechanism (77) adjustable by means of a controller (60) is provided in the oil supply circuit (54). 9. According to the described device of one of the preceding all claims, it is characterized in that: the spring (24,45) that is designed as a compression spring for the closing body (25,35) is supported on the attached closing body (25, 35). 35) on the control piston (46, 70). 10. The device according to any one of the preceding claims, characterized in that the control piston (46) assigned to the first closing body (35) located in the inlet area of the fuel injection valve (3) is controlled by a A guide pin (41) projects from a shoulder of the fixed bearing (39) and is inserted into the closing body (35) with axial freedom of movement. 11. The device according to claim 10, characterized in that the control piston (46) is surrounded by a sleeve (40) containing a valve seat part (36) assigned to the valve seat (38) of the closing body (35). 12. The device according to one of claims 10 or 11, characterized in that: the guide pin (41) is provided with a radial circulation hole (48) that opens when the control piston (46) is unloaded; and the valve seat portion (36) The lumen through which the sleeve (40) surrounding the control piston (46) communicates communicates with a return line (10). 13. According to the described device of one of the preceding claims, it is characterized in that: the controller (60) assigned to the control piston (46, 70) is arranged like this, that is, there are a plurality of oil injections for each cylinder (2) The internal combustion engine of the valve (3) can only unload the control piston (46) of a part of the fuel injection valve (3) provided for each cylinder (2) at partial load, while the remaining fuel injection valves (3) The control piston (46) can be loaded with pressure. 14. The device according to claim 13, characterized in that the controller (60) assigned to the control piston (46, 70) is arranged such that, at partial load, the set value for each cylinder (2) The control piston (46) of the fuel injection valve (3) can be alternately pressure-loaded and unloaded according to a predetermined rhythm. 15. The device according to claim 14, characterized in that the control pistons (46, 70) provided for each cylinder (2) can be alternately pressure-loaded and unloaded in a rhythm of at most two minutes. 16. Have the device according to one of the described structures of the preceding claims, characterized in that: in order to improve the fuel injection pressure, the force exerted by the control piston (70) on the closing body (25) is less than that of closing the closing body (25) The force to maintain a continuous closed position.

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