KR100847853B1 - Device for controlling the connection to be displaced temporary of two unit which can be pressurized with pressure medium with pressure medium source - Google Patents

Abstract

The present invention includes a control valve arrangement that forms a connection between a pressure medium source and a pressurizable unit, and includes two units that can be pressurized with a pressure medium. A device for controlling the sequential displacement connection with a pressure medium source, said control valve device interacts with and slides a pilot control valve 19 and a pilot control valve controllable by an engine signal. A main control valve 20 formed of a sliding valve, which is connected to an inlet 23 connectable to a pressure medium source and to pressurizable units. Two outlets (24, 25), the outlet being separated from the inlet (23) when the main valve slider (22) is in its intermediate position and the load is light The main valve slider 22 is alternately connected to the inlet 23 by corresponding deflection in the intermediate position, and a controller associated with the main valve slider 22 is the main valve slider 22. ) A displacement device (cylinder-piston unit; 27) which is activated when the pilot control valve 19 is controlled and deactivated when there is no engine signal to deflect the intermediate position (cylinder-piston unit); 33), the centering device can be penetrated by the displacement device being activated, and the main valve slider 22 can be moved to the intermediate position by the centering device when the displacement device is deactivated. This results in higher stability.

2-stroke large diesel engine, pressure medium, control valve, injection pump, actuator

Description

DEVICE FOR CONTROLLING THE CONNECTION TO BE DISPLACED TEMPORARY OF TWO UNIT WHICH CAN BE PRESSURIZED WITH PRESSURE MEDIUM WITH PRESSURE MEDIUM SOURCE}

1 is a schematic illustration of a two-stroke large diesel engine comprising a control device according to the invention for controlling actuators of two injection pumps associated with different cylinders.

FIG. 2 shows a practical embodiment of the control valve shown in FIG. 1, including the main valve slider in an intermediate position. FIG.

3 shows the device according to FIG. 2 with the main valve slider biased to one side.

4 shows a control valve according to the invention with a main valve slider in an intermediate position and an associated centering device.

Figure 5 shows the device according to figure 4 with the main valve slider biased to the left;

6 shows the device according to FIG. 4 with the main valve slider biased to the right.

The invention relates to two engines, in particular two-stroke large diesel engines, in particular mainly connected to different cylinders and hydraulically actuated, which control the sequential displacement of the two units which can be pressurized into the pressure medium by the pressure medium source. An apparatus for sequentially activating a dispensing apparatus, comprising a control valve arrangement forming a connection between a pressure medium source and a pressurizable unit. The control valve device includes a pilot control valve controllable by an engine signal and a main control valve which interacts with the pilot control valve and is formed as a slide valve, and receives a main valve slider which interacts with the associated control device and is displaceable. The housing of the control valve has one inlet connected to the pressure medium source and two outlets associated with the pressurizable units, the outlet being separated from the inlet when the main control valve is in its intermediate position and the load reduced And the main valve slider is correspondingly deflected in the intermediate position so as to be alternately connected to the inlet, the control device associated with the main valve slider comprising a displacement device controllable by the pilot control valve to deflect the main valve slider from the intermediate position. And the displacement device is provided with a pilot control valve When it is activated and deactivated when the engine signals.

Devices of the kind mentioned at the outset are described in particular in DE 103 25 067 B3. In these well known devices, the main valve slider is biased to one side when the corresponding engine signal is transmitted to the pilot control valve. Unless there is a corresponding engine signal, the main valve sliders remain in their original positions or are moved to opposite final positions, respectively, by means of a readjusting device. There is no device to automatically readjust the main valve slider to its intermediate position when there is no engine signal.

Thus, a case may occur in which the unit arranged after the control valve is operated undesirably. Devices of the kind presented here can be utilized, for example, to control the fuel injection and exhaust valve actuation of the cylinder, so there is a risk that the fuel injector and exhaust valve actuation device may be undesirably operated. If the devices of the kind presented here are used to control the fuel injection of two different cylinders, this can be particularly fatal. The known devices are thus proved to be insecure and inadequate in reliability.

It is an object of the present invention, in view of the above problem, to improve the apparatus of the kind mentioned at the outset in a simple and inexpensive way, in order to prevent the undesirable operation of the units arranged after the control valve, and thus to increase the stability. have.

The object is that the control device associated with the main valve slider comprises, in addition to the displacement device, a centering device which is permanently activated, the centering device can be penetrated by the activated displacement device and the displacement device is deactivated. This is achieved when the main valve slider can be moved to an intermediate position by the centering device.

These measures ensure that the main valve slider is automatically moved to an intermediate position in the absence of an engine signal to the pilot control valve, ie in the absence of a signal. The two outlets leading to the units arranged behind are separated and blocked from the inlet at the intermediate position, so the two units are reliably blocked. Since the centering device continues to be activated, preparation for loading of the centering device is continuously guaranteed. Nevertheless, the normal biasing of the main valve slider from the intermediate position is not restrained for normal operation of the units arranged behind it, such that the permanently activated centering device is preferably penetrated by the displacement device as soon as the displacement device is activated. This is because the size of. In this case, the engines of the centering device preferably serve as a brake organ to block the displacement device, so they can be handled with particular care when driving.

Preferred and improved forms of the measures are set out in the dependent claims.

The centering device may preferably comprise at least two cylinder piston units facing each other in association with the main valve slider, such that the displacement piston of the cylinder piston unit can be moved in engagement with the main valve slider. The piston can be permanently pressurized with the pressure acting on the inlet and is bounded by one associated pressure chamber. As a result of these measures, a permanently activated centering device is particularly simply implemented, in which the pressure acting on the inlet is likewise Because it exists forever.

In a further development of the above solutions, the displacement pistons of the centering device can be released from their associated pressure chambers until they reach a stopper, and the main valve slider can be held in an intermediate position at the stop position. Have a length. This confirmed that when the main valve slider was deflected to one side, the piston of the centering device was pushed back, while the pistons facing each other were kept in the stop position. Therefore, the force of the centering device pistons facing each other does not disappear, and the force for moving the main valve slider to an intermediate position can be reliably used when there is no force applied to the main valve slider by the displacement device.

At least one displacement piston of the centering device associated with one side of the main valve slider can preferably be divided radially, withdrawal by pressure in the associated pressure chamber, respectively, at each corresponding end of the main valve slider. It may have a pin that can be tailored. This approach enables reliable compensation for play. Thus, despite the mechanical stopper of the centering device piston, the main valve slider in the intermediate position is accommodated without play between the centering device pistons facing each other.

The displacement device comprises at least two cylinder piston units which are opposed to the main valve slider and which can be activated alternately, the reverse displacement piston of the cylinder piston unit being alternately bounded by a pressure chamber which can be pressurized by pressure. Is preferred. In this case, the surface of the displacement device piston which is bounded with the associated pressure chamber, respectively, is larger than the surface of the centering device piston, in particular doubled, so that the possibility that the displacement device can preferably penetrate the centering device may simply arise. . A flow path controllable by the pilot control valve and leading to the inlet is preferably associated with the pressure chamber, through which the pressure chamber alternately pressurizes to the pressure acting on the inlet when the pilot control valve is activated correspondingly. And the load can be reduced when not controlled.

In another preferred solution, at each end of the main valve slider, a plurality of, mainly two, cylinder-piston units each of the displacement device and the centering device are associated with each other, the cylinder-piston units being evenly distributed on the circumference and displaced equally with each other. Can be. These measures allow the force to be reliably pressed against the main valve slider in symmetry with the axis. This effectively prevents jams.

One shock absorber can be associated with each of the displacement pistons of the displacement device, so as to be particularly careful in driving.

Other preferred and improved forms of the above solutions are set forth in the remaining dependent claims, and will be more fully understood from the following description of the embodiments with reference to the drawings.

The main field of application of the invention is, for example, two-stroke large diesel engines which can be utilized as marine engines. This refers to an engine that operates at a relatively low speed and has a large piston stroke. Engines of this kind generally comprise a number of cylinders arranged in parallel. The basic structure and manner of operation of these engines are known.

Two cylinders 1 are shown in FIG. 1. Each cylinder 1 has a combustion chamber 2, which is bounded by a piston 3 moving up and down, which piston here via a crosshead 4. crankshaft; The combustion chamber 2 is supplied with air through an air admission slot (not shown) arranged in the cylinder case and controlled by the piston 3 moving up and down, and an injection valve 6 disposed in the cylinder cover region. Fuel is supplied through. In the example shown, two injection valves 6 are provided for each cylinder. Combustion gas generated during combustion is likewise discharged through an exhaust port (not shown) provided in the cylinder cover region, and an exhaust valve 7 is connected to the exhaust port.

An injection pump 8 is associated with the injection valve 6 of each cylinder 1. The injection pump comprises a pump chamber 10 bounded by the plunger 9, which can be supplied with fuel by the supply device in the direction indicated by the arrow 11. An actuator is connected to the plunger 10 in the form of a hydraulic unit 12, and the piston 13 of the hydraulic unit is connected to the plunger 9. Similarly, an actuator (not shown) may be associated with the exhaust valve 7 in the form of a hydraulic unit.

The hydraulic unit forming the actuator can be pressurized by a prestressed pressure medium through an associated pressure tube, the pressure medium being forced out of the pressure accumulator. The accumulator herein may refer to a so-called common rail 14 which penetrates all cylinders 1 or at least one group of cylinders 1. The common rail 14 is here pressurized by the pressure medium by a pump 15 which is driven by the crankshaft 5.

In order to control the pressurization of the so-called actuators, control valves are provided in the pressure tubes which are connected to the actuators. In order to limit the number of control valves that are absolutely necessary, a control valve common to actuators operating with parallax may be associated. Thus, for example, a control valve common to the actuators of the exhaust valve 7 and the injection pump 8 may be associated with each cylinder. In the embodiment based on FIG. 1, a common control valve device 16 is associated with the injection pump 8 of two different cylinders 1, the control valve device being connected to a common rail 14 via a pressure tube 17a. ) And through the pressure pipes (17b, 17c) and the associated actuators, through which the actuator can be alternately pressurized by the pressure. The cylinder 1 to which the control valve device 16 common to the injection pump 8 is linked is preferably cylinders as far apart from each other as possible in the ignition order. In this case, the parallax becomes large. The control valve device 16 is actuated by an engine signal and the engine signal is received by a suitable sensor and supplied to the control valve device 16 with a suitable input by signal line 18 (indicated by the dashed lines).

The control valve device 16 is, for example, as shown in FIG. 2, a pilot control valve 19 comprising an input for a signal line 18 and a main control valve 20 which interacts with and is formed as a slide valve. ). The main control valve has a housing 21 in the form of a block and a main valve slider 22 which is arranged to be displaceable in an associated housing bore. The housing 21 is via a pressure tube 17a, here an inlet 23 which can be connected with a source of pressure medium in the form of a common rail 14, and through the pressure tubes 17b, 17c surrounding the inlet, here two It has two outlets 24 and 25 connectable with a pressurized hydraulic unit in the form of an actuator of the injection pump 8. At the same time it may also be provided with an outlet 26 adjacent to these outlets and connectable with a pressure free tank. The inlet and outlet are connected via a bore with a peripheral groove in the area of the bore of the housing 21 which receives the main valve slider 22.

The main valve slider 22 has a ring surface which is separated from each other by a peripheral groove, the ring surface having an inlet 23 with outlets 24 and 25 which can be connected to an actuator which can be pressurized. To the tank side outlet 26 so that they can be opened and closed alternately. In the intermediate position of the main valve slider 22 based on FIG. 2 the inlet 22 is closed and thus separated from the outlets 24, 25. The outlets then open towards each adjacent tank side outlet 26. The main valve slider 22 can be deflected to one side from an intermediate position, as can be seen for example in FIG. 3. In the biased position of the main valve slider 22, which is based on FIG. 3, the inlet 23 opens towards an outlet, here an outlet 25, which is connected to a pressurizable actuator, which at the same time exits the adjacent tank side outlet. It is closed about 26. An outlet, which is connected to another actuator that can be pressurized, here outlet 24 is connected to the tank side outlet 26 while being separated from the inlet 23. As a result, the pressure load of the associated actuator is reduced.

The left and right movement of the main valve slider 22 is caused by an engine signal that is correspondingly deformable by the pilot control valve 19. In this case, for deflection of each of the main valve sliders 22, an engine signal is required which can be converted into the appropriate command by the pilot control valve 19. The main valve slider 22 then moves left and right according to the period of the associated engine signal. The main valve slider 22 should be automatically moved to the intermediate position for reasons of stability unless proper engine signal is transmitted to the input of the pilot control valve 19. In the intermediate position, the outlets 24, 25, which are connected to the associated actuators, are here separated from the inlet 23, which communicates with a pressure source in the form of a common rail 14. In order to effect deflection to one side of the main valve slider 22 and readjustment to an intermediate position, a control device associated with the main valve slider 22 is provided.

The control device comprises a displacement device for deflecting the main valve slider 22 from an intermediate position according to a signal transmitted by the signal line 18 to the pilot control valve 19, and a signal is removed from the signal line 18. The momentary main valve slider 22 consists of a centering device for automatically placing it in an intermediate position.

In order to form the displacement device, at least two hydraulic cylinder-piston units 27 facing each other in connection with the main valve slider 22 are provided, the cylinder-piston units being displacements bounded by the pressure chamber 28. With one piston 29 each, the displacement pistons interact with the front face of the corresponding main valve slider 22. In the illustrated embodiment, the displacement piston 29 has a press pin 30 that touches the front face of the adjacent main valve slider 22, as can be seen in FIGS. 2 and 3. The cylinder-piston units 27 associated with both ends of the main valve slider 22 can be activated alternately. That is, the left cylinder-piston unit 27 is activated while the right cylinder-piston unit 27 is deactivated, and vice versa, in order to displace the main valve slider 22 to the right.

For activation of the cylinder-piston unit 27, the pressure chamber 28 is pressurized by the pressure medium present at the inlet 23 of the housing 21. To this end, a flow path that can be vertically controlled by the pilot control valve 19 is provided in accordance with a signal connected to the inlet 23. Pilot control valve 19 comprises an electronic part 19a comprising an inlet for signal line 18 and a mechanical part 19b that can be affected by the electronic part, the mechanical part being an electromagnetic slide valve. (electromagnetic sliding valve) is formed. The electromagnetic slide valve has one inlet and two outlets alternately connected to the inlet like the main control valve 20, and the slider of the slide valve is controllable by the electronic unit 19a according to the connected engine signal. Can be displaced by command.

A flow path provided for pressurizing the pressure chamber 28 of the two cylinder-piston units interacting in the reverse direction with the main valve slider 22 is connected to the inlet 23 and placed at the inlet of the pilot control valve 19. Branch 31a and branch lines 31b, 31c branching from the outlet of the pilot control valve 19 and leading to each of the two cylinder-piston units 27, the branching lines 31b, 31c may be alternately connected to the branch line 31a. Like the main control valve 20, the pilot control valve 19 may have additional outlets (not shown) leading to the tank without pressure, which further allow for load reduction of the branch lines 31a to 31c. .

In principle, for the formation of the displacement device, it is sufficient that one cylinder-piston unit 27 is connected to each front face of the main valve slider 22. In the illustrated embodiment, two cylinder-piston units 27 which are displaced by 180 ° from each other are associated with each front surface of the main valve slider 22. This ensures the application of a force symmetrical with the axis of the main valve slider 22, and with this, jamming of the main valve slider 22 is prevented.

In one end position of the main valve slider 22, the main valve slider contacts the front front of the displacement device and the mechanical stopper, as can be seen in FIG. 3. As can be seen from the right side of FIG. 3, the same applies to the displacement piston of the cylinder-piston unit 27 being activated at this time. In order to prevent severe impact of the main valve slider 22 and the associated mechanical load, a shock absorbing device 32 which restrains the readjustment movement can be associated with the displacement pistons 29. The shock absorber may be a compression spring that contacts the rear face of the displacement piston 29 away from the slider. As can be seen from the left side of FIG. 3, the compression springs are pressed during the retraction movement of the associated displacement springs 29.

To form the centering device, another cylinder-piston unit 33 (shown in dashed lines in FIGS. 2 and 3) facing each other in relation to the main valve slider 22 and interacting with the main valve slider in the reverse direction, , Shown separately in FIGS. 4 to 6). Here too, in principle, one cylinder-piston unit 33 on each side is sufficient. However, it is preferable that two cylinder-piston units 33 are provided on each front surface of the main valve slider 22. This cylinder-piston unit 33 is displaced 180 ° against the cylinder-piston unit 27 of the displacement device and 90 ° toward the cylinder-piston unit 27, so that the entire cylinder-piston unit 27, 33 ) Are evenly distributed on the circumference. This prevents jam.

The cylinder-piston unit 33 includes one displacement piston 35 each delimiting the pressure chamber 34, which displacement pins 36 can engage the adjacent front face of the main valve slider 22. ). The centering device formed by the cylinder-piston unit 33 is always activated. Therefore, the pressure chamber 34 is permanently pressurized by the pressure. In addition, the pressure chamber 34 of the cylinder-piston unit 33 is connected to the ring groove of the inlet 33 to the housing 21 which is connected to the inlet via the non-blocking flow paths 37a and 37b. . However, the displacing force that can be exerted on the main valve slider 22 by the cylinder-piston unit 33 can be exerted on the main valve slider 32 by the cylinder-piston unit 27 forming the displacement device. Less than the displacement force. The permanently activated centering device can thus be penetrated by the cylinder-piston unit 27 of each activated face of the displacement device. Further, the pressure surface of the displacement device displacement piston 29 bordering with the associated pressure chamber 28 is larger than the pressure surface of the centering device displacement piston 35 bordering with the associated pressure chamber 34, respectively, Especially twice as big.

As a result of looking at the force relationship described above, it is confirmed that the main valve slider 22 is displaced as soon as the cylinder-piston unit 27 of the displacement device connected to one side is pressed by the pressure. This is the case when the corresponding engine signal is exposed. As long as the cylinder-piston unit 17 of the displacement device is activated, ie there is no corresponding engine signal, the main valve slider 22 is automatically activated by the cylinder-piston unit 33 of the centering device which is permanently pressurized by pressure. It is moved to the intermediate position on which the base of FIG. In this intermediate position the inlet 23 is blocked and the outlets 24, 25 are separated from the inlet 23. This disconnects the units connected to the outlets 24, 25 in the embodiment shown in the injection pump 8. Thus, in the embodiment according to FIG. 1, there is no possibility of undesirable injection.

The displacement piston 35 and the pressurizing pin 36 of the cylinder-piston unit 33 connected to the displacement piston are respectively connected to the main valve slider 22 by the pressure permanently exposed to the associated pressure chamber 39. It is permanently pressurized with a directing force. The resulting movement of the displacement piston 35 towards the main valve slider 22 is limited by a mechanical stopper as can be seen in FIGS. 4 to 6. The displacement piston having a ring surface delimiting the associated pressing pin 36 is in braking position when it impinges on the associated housing side shoulder 38.

As can be seen in FIG. 4, the length of the pressure pin 36 of the displacement piston 35 corresponds to the pressure pin 36 of the cylinder-piston unit 33 facing each other when the main valve slider is in the intermediate position. In the braking position of the displacement piston 35 to be in contact with each corresponding front of the main valve slider 32. As soon as the main valve slider 22 is deflected to one side, for example as it is deflected to the left in FIG. 5, the displacement piston 35 of the left cylinder-piston unit 33 comes out of the associated discharge stopper, and each associated pressure chamber It becomes possible to enter into 34. On the contrary, here the displacement piston 35 of the cylinder-piston unit 33 on the right side is kept in the braking position. The right front side of the main valve slider 22 then emerges away from the adjacent pressurizing pin 36 as shown in FIG. 5. In this situation, if the displacement device is deactivated and no further force is applied to the main valve slider 22, the main valve slider 22 is automatically activated by the left cylinder-piston unit 33 of the centering device, which can be returned earlier. It is returned to the intermediate position, and in the intermediate position, the pressing pin 36 of the entire cylinder-piston unit 33 of the centering device contacts the main valve slider.

In order to ensure this kind of stable contact and to exclude each play, the displacement piston 35 and the pressing pin 36 of the displacement piston are divided radially and in succession accommodating an extension pin 39. With axial bore. As can be seen from the left side of FIG. 6, when the associated displacement piston 35 is in the braking position and the main valve slider 22 is far from the displacement piston, the extension pin is released by the pressure of the associated pressure chamber 34, It comes in contact with the front of the main valve slider 22.

The housing 21 of the main control valve 20 has a side cover 40 which closes the bore associated with the main valve slider 22, which covers the cylinder-piston unit 27, which is located in the displacement device or the centering device. It is preferred to include the pressure chambers 28, 34 of 33). The flow paths 37a and b associated with the pressure chamber 34 preferably run completely inside the housing 21 and the cover 40. As long as the pilot control valve 19 is mounted directly to the housing 21 of the main control valve 20, as in the illustrated embodiment, this also applies to the flow paths 31a, 31b, 31c associated with the pressure chamber 28 of the displacement device. The same applies.

The pilot control valve 19 may be formed as a switch (on / off) or a proportional control valve. When formed as a switch, the main valve slider 22 is always moved to the corresponding end position in case of one-side deflection. When formed as a proportional control valve, the main valve sliders 22 can each be moved to the desired deflection position. In this way, the operation of the associated actuators can proceed preferably. In the illustrated embodiment, the respective preferred injection profiles can be realized with this. The corresponding control edges of the main valve sliders 22 are formed correspondingly, which creates the possibility of further influence. In the example shown, the intermediate ring surface of the main valve slider 22 associated with the inlet 23 has a side chamfer 41, wherein the chamfer here has a slight amount before the main injection begins. Perform pre-injection.

When using a proportional control valve, a closed loop may be provided. Each position of the main valve slider 22 is then identified and fed to the pilot control valve as an actual value, which performs the theoretical value-actual value comparison and performs the necessary calibration. Can be. In order to detect the position of the main valve slider 22, a position receiving sensor 42 (FIGS. 2 and 3), which operates mainly in contact with the main valve slider, is associated with the signal line ( 43 is connected to the associated inlet of the pilot control valve 19.

According to the present invention, an engine, in particular mainly linked to different cylinders and hydraulically actuated, in particular a two-stroke large diesel engine, controls a connection in which two units which can be pressurized into the pressure medium by means of a pressure medium are sequentially displaced. The device for sequentially displacing the two injection devices is improved in a simple and inexpensive way, which prevents the undesirable operation of the units arranged after the control valve, thus reliably increasing the stability.

Claims (17)

A control valve arrangement forming a connection between a pressure medium source and a pressurizable unit, said control valve arrangement comprising a pilot control valve 19 and said pilot control valve controllable by an engine signal; The main containing a main control valve 20 which interacts and is formed as a slide valve and which receives a main valve slider 22 which is interactable and displaceable with an associated controller. The housing 21 of the control valve has one inlet 23 connected to the pressure medium source and two exits 24, 25 connected to the pressurizable units, the outlet being the main When the control valve 22 is in the intermediate position, it is separated from the inlet 23 to reduce the load and the main valve slider 22 correspondingly deflects in the intermediate position so that And a control device associated with the main valve slider 22 includes a displacement device (cylinder-piston unit 27) for deflecting the main valve slider 22 from an intermediate position. Is activated when the pilot control valve 19 is controlled and deactivated when there is no engine signal, and the device controlling the connection in which the two units which can be pressurized by the pressure medium source to the pressure medium are displaced sequentially, in particular mainly An apparatus for activating two injectors 6 of an engine, in particular a two-stroke large diesel engine, which is linked to another cylinder 1 and is hydraulically operable, The control device associated with the main valve slider 22 includes a centering device (cylinder-piston unit; 33) which is permanently activated in addition to the displacement device (cylinder-piston unit; 27), the centering device being activated Can be penetrated by the displacement device (cylinder-piston unit) 27, and when the displacement device (cylinder-piston unit 27) is deactivated, the main valve slider 22 is moved to an intermediate position by the centering device. Apparatus, characterized in that. The method of claim 1, The centering device has two or more cylinder-piston units 33 facing each other in association with the main valve slider 22 and of the cylinder-piston unit that can engage the main valve slider 22. A reverse displacement piston (35) bounds with one pressure chamber (34) associated with each other so as to be permanently pressurized by the pressure acting on the inlet (23). The method of claim 2, The displacement piston 35 of the centering device may exit from each associated pressure chamber 34 until it reaches a stopper, and in the stop position the main valve slider 22 is moved to an intermediate position. Apparatus characterized by having a maintainable length. The method according to claim 2 or 3, One or more displacement pistons 35, mainly the displacement pistons 35 of the centering device associated mainly with one side of the main valve slider 22, are divided radially, and are drawn off by pressure in the associated pressure chamber 34, respectively. And a pin (39) that is retractable and can be fitted to each associated end of the main valve slider (22). The method according to any one of claims 1 to 3, The displacement device has at least two cylinder-piston units 27 which face each other in association with the main valve slider 22 and which can be activated alternately, the reverse displacement piston 29 of the cylinder-piston unit Alternately limits the pressure chamber 28 which can be pressurized by the pressure, and the flow paths 31a, 31b, 31c controllable by the pilot control valve 19 and leading to the inlet 23 are connected to the pressure chamber. And the pressure chambers 28 are alternately pressurized by the pressure acting on the inlet 23 respectively through the flow path when the pilot control valve 19 is correspondingly activated and the pilot control valve The apparatus characterized in that the load can be reduced when there is no control of (19). The method of claim 5, The centering device (cylinder) which the surface of the displacement piston 29 of the said displacement device (cylinder-piston unit) 27 which is bounded with the said pressure chamber 28 respectively connected is bounded with the pressure chamber 34 which is respectively linked. -A device characterized in that it is larger than the surface of the displacement piston (35) of the piston unit (33), in particular twice as large. The method according to any one of claims 1 to 3, At each end of the main valve slider 22, a plurality of cylinder-piston units 27 of two displacement devices, respectively, and a plurality of cylinder-piston units 33 of two centering devices, respectively, respectively, Device in which the entire cylinder-piston unit (27 and 33) are evenly distributed on the circumference and are evenly displaced from each other. The method according to any one of claims 1 to 3, And the main valve slider (22) contacts the mechanical stopper in its final position. The method according to any one of claims 1 to 3, And a shock absorber (32) associated with each of the displacement pistons (29) of the displacement device (cylinder-piston unit). The method of claim 9, The shock absorber (32) is formed by a spring contacting the pressure chamber side end of the displacement piston (29). The method according to any one of claims 1 to 3, The housing (21) has a side cover (40) for closing a bore associated with the main valve slider (22), the cover comprising the pressure chamber (28, 34). In claim 11, A flow passage (31a, 31b, 31c and 37a, 37b, 37c) associated with the pressure chamber (28, 34) running in the housing (20) and the cover (40). The method according to any one of claims 1 to 3, A position receiving sensor (42) is associated with said main valve slider (22), said position receiving sensor interacting with said pilot control valve (19). The method of claim 13, The pilot control valve (19) is characterized in that it is formed as a proportional control valve (proportional valve). The method of claim 14, The main valve slider (22) is characterized in that it has at least one chamfer (41) in the region of the control edge associated with the inlet (23). Method according to one of the preceding claims, for controlling the fuel injection device (6) of different cylinders in a two-stroke large diesel engine. A method according to any one of claims 1 to 3, for controlling the operation of the injection device (6) and the exhaust valve (7) of a cylinder in a two-stroke large diesel engine.

Images