JPH11159314A - Structure and method for controlling valve for reversible diesel engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a less-complicate and profitable structure for controlling a valve for a reversible diesel engine with a space-saving small size. SOLUTION: A structure for controlling a valve for a reversible diesel engine comprises a control shaft 2 provided with at least one fuel cam 4 positively and reversely running in two directions to control fuel injection and at least one valve cam 3 to control the valve for the diesel engine. The valve cam 3 controls opening of the valve 5. A means different from the valve cam 3 is provided to control closing the valve 5.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

FIELD OF THE INVENTION The present invention is reversible and rotatable in both directions and has at least one fuel cam for controlling fuel injection and at least one valve cam for controlling valves of a diesel engine. The present invention relates to a configuration for valve control of a reversible diesel engine, comprising a control shaft and the valve cam controlling opening of the valve.

The invention further provides that the control shaft is rotatable in two directions and has at least one fuel cam to control fuel injection and at least one valve cam to control the valves of a diesel engine. Further, the present invention relates to a method for controlling a valve of a reversible diesel engine, which comprises rotating the whole body at the time of reverse rotation and controlling opening of a valve by a valve cam.

[0003] The present invention further relates to any one of claims 1 to 7
The invention relates to a reversible diesel engine, characterized in that it is provided with an arrangement according to claim 1 or is operated according to a method according to claim 8 or 9, in particular with a large two-cycle diesel engine.

[0004]

2. Description of the Related Art In a reversible diesel engine, particularly a large diesel engine used in shipbuilding or the like, control of fuel injection and control of cylinder valves (at least one of an exhaust valve and an intake valve) are performed by a control shaft. . The control shaft is one per cylinder to control fuel injection.
There is one fuel cam and one valve cam per valve to control the valves. The control shaft is driven by a crankshaft. Both the fuel cam and the valve cam drive a driver such as an injection pump for injecting the associated fuel or a lifting pump for hydraulically driving the valve.

In general, since the angular displacement between the fuel cam fixed on the control shaft for the exhaust valve and the valve cam is different in both rotation directions (forward rotation and backward rotation), both rotations of the reversible engine are different. There is a need for a suitable method of providing the same conditions for fuel injection in the direction and the associated actuation of the valve. For example,
If the fuel cam and the valve cam for the exhaust valve are arranged such that the top of the valve cam for the exhaust valve is delayed by 145 degrees in crank angle from the top of the fuel cam in the forward rotation, the rotation direction is reversed, that is, the backward rotation. In this case, the top of the valve cam for the exhaust valve is delayed by 215 degrees in crank angle from the top of the fuel cam. As a result, the link between fuel injection and actuation of the exhaust valve (referred to as the motion cycle of the piston in the cylinder) is:
It does not match the connection at the time of forward rotation. This allows
The operation of the engine will be greatly impaired during backward rotation.

It is therefore proposed in DE-A 31 28 332 to rotate the fuel cam with respect to the control shaft for reverse rotation. There, the fuel cam is repositioned between two positions with respect to the angular position on the control shaft, while the exhaust valve cam remains in the same position with respect to the control shaft in both directions of rotation. This method ensures that the control time is ideal for both directions of rotation. The reversal of the fuel cam is accomplished by a hydraulic rotating device that rotates the fuel cam relative to the control shaft from a position for forward rotation to a position for backward rotation (and vice versa).

Although this embodiment has been found to work perfectly, the device is rather complex and costly.
Since each rotating device can only rotate two fuel cams, in addition to the supply line required in each case, at least one such rotating device is used to control the control shaft for each cylinder of the engine. Need to be supplied above. Furthermore, these reversing devices require more space. On the one hand the fuel cam and on the other hand the housing housing the control shaft such as the pump housing needs to be larger.

[0008]

SUMMARY OF THE INVENTION Based on this prior art, it is an object of the present invention to propose a simple arrangement for valve control of a reversible diesel engine. In the reversible diesel engine, the size of the control shaft is designed to be very space-saving, and almost the same valve control is possible in both rotation directions of the control shaft for fuel injection. Since the configuration in the apparatus and the assembly is simple, the configuration can be realized relatively easily and inexpensively. It is a further object of the present invention to propose a method for controlling at least one of an exhaust valve and an intake valve of a reversible diesel engine.

[0009]

SUMMARY OF THE INVENTION With respect to the apparatus and method,
It is intended that the subject-matter of the invention satisfying the objects have the features of the independent claims.

According to the invention, a valve cam on the control shaft controls the opening of the valve. On the other hand, the closing of the valve is controlled by means different from the valve cam. In this way, only one flank is needed for each direction of rotation, since something other than the second flank of the valve cam is provided as a means of controlling valve closure. Thus, while one flank is in forward rotation and the other flank is in backward (reverse) rotation, the valve opening is controlled in an ideal manner for fuel injection and until the desired time. A valve cam is provided. This allows
Due to the reverse rotation, it is not necessary to rotate the fuel cam or the valve cam alone. As a result, in the apparatus and its assembly, the ideal time continuity between the fuel injection and the valve driving is not hindered at all, and a great reduction in cost and complexity is achieved. Each cam is mounted directly on the control shaft, since no reverse rotation device is required for each cam. Thereby, each cam can be reduced in size. As a result, a housing for housing the driver, such as a pump housing, can be smaller and simpler.

The arrangement and method according to the invention are suitable for large two-cycle diesel engines used in shipbuilding and the like. Further advantageous measures and preferred embodiments of the arrangement and method according to the invention are given by the dependent claims.

[0012] The invention as defined in claim 1 is reversible and rotatable in both directions and has at least one fuel cam for controlling fuel injection and at least one valve cam for controlling a valve of a diesel engine. In a configuration for valve control of a reversible diesel engine comprising a control shaft having a valve cam and the valve cam controlling opening of the valve, means different from the valve cam are provided for controlling valve closing. Its gist is that it is a structure.

According to a second aspect of the present invention, both the fuel cam and the valve cam are fixed to the control shaft, and the opening of the valve is substantially the same in both directions of rotation of the crankshaft. (K
The valve cam is provided so as to be caused by the displacement W).

According to a third aspect of the invention, the contour of the valve cam has two effective vertices, and the first apex is displaced at the same angle as the apex of the fuel cam in each rotation direction. And two effective vertices are provided.

According to a fourth aspect of the present invention, the effective apex of the valve cam is displaced at substantially the same crank angle as the crank angle at the time of reverse rotation, and the profile of the valve cam has a bottom circle between the two effective apexes. Is characterized by having a different configuration.

According to a fifth aspect of the present invention, a lifting pump driven by a valve cam is further provided, and the lifting pump communicates with the valve via a hydraulic line to hydraulically drive the valve. And the means for controlling the closing of the valve comprises an overflow connection, which is provided in the lifting pump to relieve pressure in the hydraulic line. It is characterized by having a configuration.

The invention described in claim 6 is characterized in that the means for controlling the closing of the valve includes a limiting device for restricting release of the pressure in the hydraulic line. According to a seventh aspect of the present invention, a lifting pump driven by a valve cam and connected to the valve via a hydraulic line is provided for hydraulically driving the valve, and controls closing of the valve. The means for providing is characterized in that it comprises an electrically or electronically controlled valve for releasing the pressure in the hydraulic line.

According to another aspect of the invention, there is provided a method for controlling valves of a reversible diesel engine, wherein the control shaft rotatable in both directions includes at least one fuel cam for controlling fuel injection and at least one fuel cam of the engine. In a further method, comprising at least one valve cam for controlling the valve, the whole rotating as a unit when in reverse rotation, and in the same engine the opening of the valve is controlled by the valve cam. The gist of the present invention is to provide a method for controlling a valve of a reversible diesel engine, wherein the closing of the valve is controlled by means different from the valve cam.

According to a ninth aspect of the present invention, the valve is hydraulically opened by a lifting pump driven by a valve cam, the valve is closed by releasing the pressure of the hydraulic line, and the lifting is performed. The working piston of the pump is held in the region of the top dead center by the valve cam while the valve is closing the valve.

According to a tenth aspect of the present invention, there is provided an apparatus according to any one of the first to seventh aspects, or operated by the method according to the eighth or ninth aspect. The gist is a large two-cycle reversible diesel engine.

[0021]

BRIEF DESCRIPTION OF THE DRAWINGS The invention will be described in more detail hereinafter with reference to the drawings and embodiments with regard to the device and the method.
Schematics are not based on exact scale. Parts having the same or equivalent functions are denoted by the same reference numerals.

In the following description of the present invention, a specific feature of the embodiment is that it has a scavenging section extending in the longitudinal direction used in shipbuilding and the like, and includes, for example, a cylinder exhaust valve used as a valve to be controlled. Reference is made to a large stroke diesel engine. Of course, the present invention is suitable in a similar manner for controlling intake valves, but since it is sufficient to understand the teachings of the present invention, the description will be made only for one cylinder exhaust valve. In the following description, "fuel cam" and "valve cam" refer to the same cylinder. If there are multiple cylinders, each cylinder is provided with a fuel cam and a valve cam in the same manner as described.

FIG. 1 is a schematic diagram showing a first embodiment of a configuration according to the present invention for valve control of a reversible diesel engine. The entire configuration is indicated by reference numeral 1 as a whole. The arrangement comprises a reversible control shaft 2 as a whole. The control shaft 2 is rotatable in two directions and is driven by a crankshaft of a diesel engine in a known manner, and rotates in both directions in synchronization with the crankshaft. That is, during the transition from the forward rotation to the backward rotation, or vice versa, the entire control shaft 2 rotates only the reverse rotation angle with respect to the crankshaft, and then continues to rotate in synchronization with the crankshaft. Control shaft 2 for crankshaft
Is different between the forward rotation and the backward rotation. The inversion of the entire control shaft 2 is performed by a known method, and thus will not be described in detail here. For fuel cam,
It is possible to provide a reversible servomotor or the like in the control shaft gear which is designed in a manner similar to that described in DE-A 31 28 332. Since there is enough space in the control shaft gear, there is no problem in designing the motor so that the torque generated by the reversible servomotor can sufficiently reverse the entire control shaft 2.

A fuel cam 4 for controlling fuel injection into a combustion chamber of a cylinder (not shown) of a diesel engine
And a valve cam 3 for controlling a valve 5 such as an exhaust valve 5 of the same cylinder are provided on a control shaft. The fuel cam 4 drives a fuel injection pump (not shown) for transferring fuel to an injection nozzle of a cylinder by a known method.

The valve cam 3 drives a lifting pump 7 via a follower roller 6. The working piston 71 of the lifting pump 7 is guided into a sleeve 74 to define a working space 72. The working space 72 is connected to the exhaust valve 5 via a hydraulic line 8 to hydraulically drive the exhaust valve 5. When the working piston 71 of the lifting pump 7 is in the compression stroke,
When 1 moves upward in the figure, the hydraulic medium in the hydraulic line 8 is placed under pressure, and the pressure opens the exhaust valve 5. With the above method, the valve cam 3 controls the opening of the exhaust valve 3.

According to the present invention, means different from the valve cam 3 are provided to control the closing of the valve 5. In a first embodiment, these means comprise an overflow connection 73. The overflow connection 73 is provided in the lifting pump 7 for releasing the pressure of the hydraulic line 8. The overflow connection 73 connects the working space 72 of the lifting pump 7 to an annular groove 75 on the jacket surface of the working piston 71. At least one aperture 76 is provided in the sleeve 74 and opens into an annular passage 77 surrounding the outer wall of the sleeve 74. The annular passage 77 is connected to the outlet passage 78, and a hydraulic medium such as oil can flow out through the outlet passage 78. The annular groove 75 in the wall of the working piston 71 and the hole 76 in the sleeve 74 are relatively arranged so as to communicate only when the working piston 71 is located in the region of the top dead center. Top dead center means the reversal point of the working piston,
There, the amount of working space 72 is minimized.

In the first embodiment, the means for controlling the closing of the valve 5 further comprises a limiting device such as a limiting valve 9. Restriction valve 9 is used to regulate the release of pressure in hydraulic line 8. Return passage 10 is restricted valve 9
And opens into the supply line 11 for the hydraulic medium. The supply line 11 is connected between a supply container (not shown) for the hydraulic medium and the opening of the hydraulic line 8 by a check valve 12.
To communicate through.

The fuel cam 4 and the valve cam 3 are fixed on the control shaft 2. As the opening of the valve is caused by the displacement of the crank angle with respect to the fuel injection,
The valve cam 3 is provided. The crank angle is substantially the same in both rotation directions of the control shaft 2. FIG. 3 is a sectional view showing this type of valve cam 3. Valve cam 3
Has a first flank 31 and a second flank 32. The valve cam 3 has an intermediate area 34 between the two flanks 31,32. The contour of the valve cam 3 extends substantially parallel to the bottom circle 33 in the intermediate region 34. Due to this intermediate region 34, the profile of the valve cam 3 has two valid vertices S1, S2, the transition region between the first flank 31 and the intermediate region 34, and the second flank 32 and the intermediate region, respectively. 34 and a transition region between them.
The “effective vertex” is on the contour of the valve cam 3 and the valve 5
When the opening stroke of the valve has just finished,
Is used to mean the point at which the follower roller 6 (FIG. 1) is placed in contact on the valve cam when it has just completely opened. When the follower roller 6 is at the effective apex, the working piston 71 of the lifting pump 7 is almost at its top dead center.

Two effective vertices are arranged so that in each case the first effective vertex S1 or S2 is displaced in the rotational direction by the same angle with respect to the vertex of the fuel cam 4 in either rotational direction. Thus, the valve cam 3 is designed. That is, the two effective vertices S1 and S2 are displaced from each other at a fixed angle, and the angle at which they are inverted is almost the same as this angle. In other words, the length of the intermediate region 34 is the inverted angle Almost comparable to

An operation method of the configuration 1 according to the present invention will be described below with reference to FIG. Due to the characteristics of a normal diesel engine, fuel injection should be at least as late as crank angle KW35.
It is presumed that it has already been completed. That is, it is considered that the driving body of the fuel pump reaches the top dead center at the crank angle KW of 35 degrees. The opening of the exhaust valve 5 is to occur at a crank angle of 180 degrees. According to conventional nomenclature, the crank angle KW is applied to represent the position of the piston within the cylinder of the engine. According to this, when the piston is located at its top dead center, the crank angle KW is 0 degrees, and when it is at its bottom dead center, the crank angle KW is 180 degrees.

FIG. 2 shows the arrangement of the cams 3 and 4 on the control shaft 2 in a linear representation. The crank angle KW during forward rotation is plotted on the V axis, and the crank angle KW during backward rotation is plotted on the R axis.
In both rotation directions, the top of the fuel cam 4 is disposed at a crank angle KW = 35 degrees. When the rotation direction is reversed, the reversal angle at which the control shaft 2 rotates is substantially equal to twice the angular distance that the top of the fuel cam 4 has moved from the top dead center of the piston (crank angle = 0 degrees). That is, in the specific example, the reversal angle is 70 degrees.
(This reversal angle can be further reversed.) Since the first effective vertex S1 of the valve cam 3 during forward rotation is arranged at a crank angle KW = 180 degrees, the first effective vertex S1 is the fuel cam 4 Has an angular distance dl of 145 degrees. The intermediate region 34 of the valve cam has a reversal angle 70
It has a length d2 corresponding to degrees. As a result, during the forward rotation, the second effective vertex S2 of the valve cam 3 becomes the crank angle KW
= 250 degrees. In the forward rotation (V axis), the angular distance d3 of the valve 3 to the fuel cam 4 reaches around 145 degrees.

In forward rotation, fuel injection occurs first. This fuel injection is controlled by the fuel cam 4, and the top of the fuel cam at that time has a crank angle K
It is arranged at W = 35 degrees. As the control shaft 2 continues to rotate, the follower roller 6 (FIG. 1) comes into contact with the first flank 31 of the valve cam 3. Thus, the working piston 71 of the lifting pump 7 is moved upward with reference to FIG. As the working piston 71 makes a stroke movement, the pressure of the hydraulic line 8 increases, and the opening of the valve 5 is started. Follower roller 6 is the first effective vertex S1 of valve cam 3 (crank angle KW = 180 degrees)
Is reached, the exhaust valve 5 is completely opened and the working piston 71 of the lifting pump 7 is located in the region of its top dead center. Thereby, communication between the annular groove 75 and the hole 76 is established, and the hydraulic medium is supplied to the overflow connecting portion 7.
3, annular groove 75, hole 76, annular passage 77 and outlet passage 7
It flows out of the working space 72 via 8. As a result, the pressure in the hydraulic line 8 decreases (pressure release), and the valve 5 is closed. In that case, the closing stroke and the closing time can be controlled by controlling and adjusting the limiting valve 9. The hydraulic medium that has passed through the restriction valve 9 returns to the return passage 1
0 flows into the supply line 11. Thus, by releasing the pressure in the hydraulic line 8, the valve 5 closes. While the valve 5 is closed, the working piston 71 of the lifting pump 7 is held by the valve cam 3 in the region of its top dead center. That is, the follower roller 6 moves on the intermediate area 34 of the valve cam 3. When the follower roller 6 finishes rotating and passes through the second effective vertex of the valve cam 3, the working piston 71 moves downward in FIG. 1 by a load such as a spring (not shown) and by a known method. As a result, when the pressure in the hydraulic line 8 is reduced to such an extent that the check valve 12 is opened, the hydraulic medium is sucked from the supply line 11 into the hydraulic line 8. As the control shaft 3 continues to rotate further, the top of the fuel cam 4 becomes the crank angle KW.
= 395 degrees (corresponding to crank angle KW = 35 degrees), and fuel injection occurs.

In the specific example, in the backward rotation (R axis in FIG. 2), first, the entire control shaft 2 is rotated at a reversal angle of 70 degrees with respect to the crankshaft. As a result, the top of the fuel cam again reaches the crank angle KW = 35 degrees. As the control shaft 2 continues to rotate, the follower roller 6 abuts the second flank 32 of the valve cam 3 and the opening of the valve 5 occurs in the same manner as previously described. In the valve 5, the follower roller 6 is positioned on the second effective vertex S2 of the valve cam 3 (KW
= 180 degrees), it is completely opened. The closing of the valve 5 is performed in the same manner as described above.

As a result, the first flank 31 of the valve cam 3 controls the opening of the valve 5 during forward rotation and the second flank 32 during backward (reverse) rotation. In both directions of rotation, the closing of the valve 5 is controlled by means different from the valve cam 3, that is, by reducing or releasing the pressure in the pressure line 8. For control of the valve, one flank 31 of the valve cam 3 per rotation direction
Or only 32 are needed, so two flank 3
1 and 32 are spaced apart from each other, and the angular distance d1 of the effective vertex S1 or the angular distance d2 of S2 of the fuel cam 4 that first comes into contact in the respective rotational directions is independent of the rotational direction of the control shaft 2. This allows
For a diesel engine, ideal driving behavior is guaranteed with forward and backward rotation, especially with regard to the cooperation of fuel injection and valve actuation.

FIG. 4 is a sectional view showing another example of the valve cam 3. In this alternative example, the profile of the valve cam 3 is different from the bottom circle 33 and is not parallel to the bottom circle 33 and has a minimum range between the two effective vertices S1 and S2, that is, in the intermediate region 34. Thereby, the amount of hydraulic medium that needs to flow out to close the valve 5 can be reduced. The operating piston 71 of the lifting pump 7 is slightly moved downward in the downward direction as viewed in FIG. However, since the movement of the working piston 71 is very small, the working piston 71 is held in the top dead center region during closing of the valve 5 so that the hydraulic medium can flow out through the overflow connection 73.

It is clear that the fuel cam 4 and / or the valve cam 3 need not be designed symmetrically. Two flank 3 of valve cam 3
1, 32 have different designs in terms of gradient, length, etc. The same can be said for the flank of the fuel cam 4.

FIG. 5 is a schematic diagram showing a second embodiment of the present invention. The main difference between the second embodiment and the first embodiment is the means for closing the valve 5. Otherwise, the first
The description of the specific example is similarly applied to the second specific example.
In the second embodiment, a lifting pump 7 ′ driven by the valve cam 3 and connected to the valve 5 via the hydraulic line 8 is provided for driving the valve 5. The means for controlling the closing of the valve 5 comprises an electrically or electronically controlled valve 20 for releasing the pressure in the hydraulic line 8. The electrically or electronically controlled valve 20 is either directly controlled or pre-controlled.

The hydraulic line 8 leads from the lifting pump 7 ′ to the electro-mechanical valve 20, and then from the electro-mechanical valve 20 to the exhaust valve 5. At the position of the valve 20 shown schematically in FIG. 5, the lifting pump 7 ′ is connected to the exhaust valve 5,
The hydraulic medium opens the exhaust valve 5 as long as sufficient pressure works. To close the exhaust valve 5, the valve 20 is arranged in a position as shown schematically on the right side of the valve 20. From the outlet of the valve 20 of the hydraulic line 8 to the exhaust valve 5
Is connected to the return passage 10, which means that the hydraulic medium flows out of the indicated part of the hydraulic line 8 via the return passage 10 in a controlled manner. Thereby, the pressure of the exhaust valve 5 is released, and the valve 5 is closed.

The return passage 10 is connected to a supply line 11 for hydraulic medium or a supply container 13 for hydraulic medium.
Directly connected to The operation of the valve 20 is performed by a method of a control pulse reaching the valve 20 from the control unit 60 via the signal line 50.

A measuring device for measuring the angular position of the control shaft 2 is provided so that the exhaust valve 5 is closed at a desired time, that is, at a desired crank angle KW. The measuring device includes an angle sensor 30 and the like connected to a control unit 60 via a signal line 40. Control unit 60
Determines that the exhaust valve 5 should be closed based on the signal transmitted from the angle sensor, immediately outputs a control pulse signal, and the control pulse signal drives the valve 20 via the signal line 50. I do.

In this second embodiment, an electrically or electronically controlled valve 20 is used to control the closing of the exhaust valve 5, while the opening of the exhaust valve 5 is effected by the valve cam 3. Of course, there may be other measuring devices that output a signal, and based on the signal, the control unit 60 recognizes that the closing of the exhaust valve 5 needs to occur. Means such as a proximity sensor, a position sensor, an inductive sensor, and a photodiode can be employed, and the position of the working piston 71 of the lifting pump 7 ′ or the angular position of the valve cam 3 can be detected by them.

[0042]

As described in detail above, the present invention makes the device and its assembly simple and economical. Furthermore, the control shaft, the cams and the housing surrounding them can be designed to be small and space-saving. Furthermore, an ideal rotation behavior is possible in both forward and backward rotation of the control shaft.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a main part of a first specific example of a configuration according to the present invention.

FIG. 2 is a diagram illustrating a cam arrangement according to the invention, a method of operating the arrangement and / or a method according to the invention.

FIG. 3 is a sectional view of a valve cam.

FIG. 4 is a sectional view of another example of the valve cam.

FIG. 5 is a schematic diagram of a second specific example of the present invention.

[Explanation of symbols]

2 ... control shaft, 3 ... valve cam, 4 ... fuel cam, 5 ... exhaust valve, 6 ... follower roller,
7, 7 '... lifting pump, 8 ... hydraulic line, 9 ...
Limiting device, 10 ... return passage, 11 ... supply line, 12 ...
Backflow prevention valve, 20 ... valve, 71 ... working piston,
73 ... Overflow connection

Claims (10)

[Claims] At least one fuel cam (4) for controlling fuel injection and at least one valve cam (3) for controlling a valve (5) of a diesel engine. ) And the valve cam (3).
Controls the opening of the valve (5) in a reversible diesel engine, in which a means different from the valve cam (3) is provided for controlling the closing of the valve (5). A configuration for valve control of a reversible diesel engine, characterized in that: 2. The fuel cam (4) and the valve cam (3) are both fixed to the control shaft (2), and the opening of the valve (5) is substantially the same in both rotation directions of the control shaft (2). 2. The arrangement according to claim 1, wherein the valve cam (3) is arranged to be caused by a displacement of the crank angle (KW) for a certain fuel injection. 3. The profile of the valve cam (3) has two effective vertices (S1, S2), and the first vertex (S1 or S2) is in each rotation direction with the vertex of the fuel cam (4). The configuration according to claim 1 or 2, wherein the two effective vertices (S1, S2) are disposed so as to be displaced at the same angle. 4. An effective vertex (S1, S1) of the valve cam (3).
2) is displaced at substantially the same crank angle as the crank angle at the time of reverse rotation, and the profile of the valve cam (3) is 2
Between the effective vertices (S1, S2), the base circle (3
4. The configuration according to claim 3, which is different from 3). 5. The apparatus further comprises a lifting pump (7) driven by a valve cam (3), and the lifting pump (7) hydraulically drives a valve (5) by connecting a hydraulic line (8). And the means for controlling the closing of the valve (5) is provided with an overflow connection (73), and the overflow connection (73) is connected to the hydraulic line (8). Arrangement according to any of the preceding claims, wherein a pressure is released in the lifting pump (7). 6. The arrangement according to claim 5, wherein the means for controlling the closing of the valve comprises a limiting device (9) for regulating the release of the pressure in the hydraulic line (8). 7. A lifting pump (7) driven by a valve cam (3) and connected to the valve (5) via a hydraulic line (8) for hydraulically driving the valve (5). What is provided and the valve (5)
The means for controlling the closure of the valve (2) are electrically or electronically controlled to release the pressure in the hydraulic line (8).
The configuration according to any one of claims 1 to 4, comprising (0). 8. A method for controlling a valve of a reversible diesel engine, the control shaft being rotatable in both directions comprising at least one fuel cam (4) for controlling fuel injection and a valve (5) of the diesel engine. ), At least one valve cam (3) is provided, and when the engine is rotated in the reverse direction, the whole unit rotates. In the same engine, the opening of the valve (5) is controlled by the valve cam (3). In which the closing of the valve (5) is controlled by means different from the valve cam (3). 9. The valve (5) is hydraulically opened by a lifting pump (7, 7 ′) driven by a valve cam (3), and the valve (5) reduces the pressure of a hydraulic line (8). To be closed by releasing,
The working piston (7) of the lifting pump (7, 7 ')
9. The method according to claim 8, wherein 1) is held in the region of the top dead center of the piston by a valve cam (3) while closing the valve (5). 10. A reversible diesel engine, characterized in that it has the configuration according to claim 1 or is operated by the method according to claim 8 or 9, in particular in a two-stroke cycle. Large diesel engine.