KR100513142B1 - A hydraulically actuated exhaust valve for an internal combustion engine - Google Patents

Abstract

The exhaust valve with the hydraulic actuator 13 has a valve member 25 journalably displaceable in the axial direction of the piston in the actuator piston 19. By the displacement in the actuator piston 19 in the axial direction of the piston, the positioning member 28 can change the volume of the positioning chamber 42 of the actuator piston 19. A hydraulic fluid channel 22 develops into the pressure chamber 21 of the valve opening 23, which is at least partly blocked by the valve member 25 by a displacement towards the valve opening.

Description

HYDRAULICALLY ACTUATED EXHAUST VALVE FOR AN INTERNAL COMBUSTION ENGINE}

The present invention relates to a hydraulically actuated exhaust valve for an internal combustion engine having a hydraulic actuator comprising at least one first actuator piston, wherein the first actuator piston is a hydraulic fluid that can be supplied and discharged through a hydraulic fluid channel. Coaxially aligned with the extension of the exhaust valve spindle to form a pressure chamber for movement in the cylinder, thereby allowing the exhaust valve to be opened and closed.

In this type of exhaust valve, the movement of the actuator piston is normally attenuated, thereby alleviating the closing movement of the valve. Operation of the engine can result in significant changes in valve spindle length from cold start to high temperature and / or due to valve wear. This unavoidable change in valve spindle length entails a significant risk of undesirable coarse valve closure, as the closing motion of the valve is not always relaxed constantly. Therefore, the prior art has provided various correction means for it.

PCT / DK98 / 00219 discloses an exhaust valve having an actuator comprising a first piston and a second piston, the first piston contacting the valve housing by attenuated movement during closing of the valve. Thus having a fixed starting position. To compensate for the change in length between the actuator piston and the movable seat surface of the valve, a gap compensator is inserted between the actuator and the valve spindle. The gap compensator transmits the maximum spindle force upon opening and closing the exhaust valve, so that it is a redundant component of considerable size.

DE 38 09 954 discloses a valve for an internal combustion engine in which the actuator piston is rigidly connected with the valve spindle, is moved into the compensator piston consisting of the cylinder wall and the bottom when the valve is closed and displaceable in the cylinder of the valve housing. In the opening of the valve and in the relaxation of the closing of the valve, the compensator piston has the same large force as the actuator piston and therefore requires the same dimensions as those pistons, which is a disadvantage, especially for large engines. . Another disadvantage is that the oil chamber above the compensator piston must be effectively filled in each closing of the valve.

It is therefore an object of the present invention to provide a hydraulically actuated exhaust valve which eliminates the above mentioned disadvantages and enables uniform attenuation of the closing movement of the valve.

In accordance with the above object, the exhaust valve of the present invention has a spring in which a valve member having an associated positioning member is journalably displaced in the first actuator piston in the axial direction of the first actuator piston, so as to be spaced apart from the actuator piston. Loaded, the positioning member can change the volume of the positioning member at the actuator piston by displacement in the actuator piston in the axial direction of the actuator piston, and with the fixed stop of the pressure chamber in the closed position of the exhaust valve. And a displacement of the valve member towards the valve opening causes the hydraulic fluid channel to develop into the pressure chamber of the valve opening that is at least partially blocked by the valve member.

In this way, the positioning member can define the position of the maximum extension at a given time with respect to the valve member of the actuator piston, which positioning member itself is held in place by a hydraulic actuator inherent in the positioning chamber. However, since the spring presses on the valve member and it acts on the positioning member, a small amount of hydraulic fluid always flows to or from the chamber, so that the hydraulic fluid inherent in the positioning member Affected, which inevitably causes certain leaks that cause the valve member to move very slowly from the actuator piston. Such leakage can occur between the surface of the actuator piston and the surface of the positioning member in sliding contact, thus it also aids in lubrication between the sliding surface stones.

When the exhaust valve is open, high pressure hydraulic fluid flows from the hydraulic fluid channel into the pressure chamber, so that the pressure in the pressure chamber rises, with the result that the actuator piston opens the exhaust valve. When the pressure in the hydraulic fluid channel falls again, the actuator piston is again pressurized, for example by a pneumatic spring disposed below and acting on the valve spindle. When the exhaust valve approaches its closed position, the valve member also approaches the valve opening and gradually closes. This raises the pressure in the pressure chamber above the actuator piston, and the closing movement is relaxed.

In relation to such closure, the position of the valve member in the actuator piston can be adjusted. If the actuator piston is at the same cylinder height as in the preceding closing or closer to the end wall of the cylinder, the positioning member is in contact with the stationary stop of the pressure chamber and pressurized to some extent so that the hydraulic fluid leaks. The volume of the positioning member will change again. On the other hand, when the actuator piston is further spaced from the cylinder end wall than in the prior closing, the positioning member is not in contact with the stationary stop. However, in one of the following cycles, contact will occur due to leakage from or to the chamber. In this way, the position of the positioning member and thus the position of the valve member of the actuator piston is always adjusted in relation to the current length between the actuator piston and the movable seat surface of the exhaust valve, which is independent of the length. Ensure even relief of valve closing movement.

Upon closure of the exhaust valve, the actuator piston is relaxed due to an increase in pressure in the pressure chamber above the piston, so that the valve member and the positioning member do not have to have a large braking force in the axial direction of the piston. Such members can be relatively small compared to the actuator piston. This also means that the positioning member does not have a very large mass and also does not have a large momentum when it comes into contact with the stationary stop of the pressure chamber. Thus, less wear occurs and the valve can be closed more uniformly.

In the first embodiment of the present invention, the valve member and the positioning member are formed completely integrally. This embodiment is very simple in both manufacturing and functioning, as a single member is mounted so that it can be displaced in the actuator piston. The above mentioned leakage between the positioning chamber and the pressure chamber is determined by the proper design of the gap between the valve and the positioning member and the actuator piston, so that the valve and the positioning member are pressurized at the closed position of the exhaust valve. Sufficient leakage may occur at the actuator piston for proper adjustment of the valve and positioning member position when in contact with the stationary stop of the chamber; on the other hand, upon increasing pressure in the hydraulic fluid channel during opening of the exhaust valve, the hydraulic fluid may Due to the influence of pressure on the upper surface of the valve member, which occurs for a short period of time until the valve member is displaced out of the hydraulic fluid channel so that it can freely enter and exit the pressure chamber, relatively little displacement of the valve and positioning member in the actuator piston May occur.

In another embodiment, the valve member is cylindrical, and also cylindrical and guided coaxially in a positioning member which is coaxially guided in the first actuator piston, the wall portion of which is directed out of the piston is fixed in the pressure chamber. With at least one passageway and an end surface abutable to the stop, the valve member has a lower collar having an upward contact surface for contact with a downward contact surface on the positioning member. When the exhaust valve is open, the valve member can be pressed into the actuator piston against the spring load, thus exposing the valve opening and the hydraulic fluid can flow through it into the pressure chamber. After the first displacement of the actuator piston, the valve member is pushed out of the actuator piston by some associated spring and pressurized again to some extent so that the valve member can contact the positioning member. Thus, the positioning member is hardly affected by the increase in the pressure of the hydraulic fluid channel upon opening of the exhaust valve, which is advantageous because in some cases such an increase in pressure can lead to an inappropriate displacement of the positioning member in the actuator piston. Can be. The passage in the outwardly facing wall portion of the piston allows hydraulic fluid to flow between the valve opening and the pressure chamber when the positioning member contacts the stationary stop, so that the end surface is positioned where it can block such flow. It can be formed as an annular stop without a crystal member.

The positioning chamber may be in communication with the pressure chamber through a flow passage having a non-return valve. As mentioned above, the presence of a constant leak causes the position of the positioning member and the valve member to change slowly with respect to the actuator piston. If the positioning member is in contact with the stationary stop of the pressure chamber, however, it may require a larger flow of hydraulic fluid than is possible through this leak. The check valve is advantageously closed by a ball, which can be oriented such that the ball is only lifted from the seat when the positioning member is in contact with the stationary stop.

The positioning member may be loaded by the separating spring in a direction spaced from the actuator piston. This may be an advantage when the valve member is guided in the positioning member, because excessive friction between these members causes the valve member to drag the positioning member with it into the actuator piston when the valve is opened. Because you can pull.

The actuator of the exhaust valve can be designed such that the volume of the positioning chamber can be increased by the positioning member in contact with the fixed stop of the pressure chamber.

In another embodiment, which is advantageous from a manufacturing point of view and shortened in the axial direction, the positioning member has a lower collar guided in the cylinder of the actuator piston, and the positioning chamber is disposed around the positioning member and downwards. Is an annular chamber formed by the collar of the positioning member and upward by the ceiling of the actuator piston.

The positioning member and the fixed stop of the pressure chamber are positioned prior to contact with the fixed stop by, for example, a circumferential cross-sectional tapered wall portion aligned on the positioning member that slides into the circumferential groove of the end wall of the pressure chamber. It can be designed so that the motion of the crystal member can be attenuated. In particular, in the case of large manufacturing dimensions in which the positioning member has a large mass, this enables more accurate positioning of the valve member, and consequently, a more uniform valve closing. This is also advantageous if the valve length is rapidly increased due to a rapid temperature increase since the positioning member must carry out a larger displacement of the actuator piston when in contact with the stationary stop.

In another embodiment, the volume of the positioning chamber can be reduced by contact of the positioning member to the stationary stop of the pressure chamber.

In an advantageous embodiment, the valve member region disposed in the actuator piston and facing away from the valve opening is exposed to a space disposed in the actuator piston and in communication with the pressure chamber through the opening of the actuator piston. In this way, the valve member is affected by the same hydraulic pressure in both axial directions during the closing of the exhaust valve, and the spring holding the valve member in its extended position can be made less rigid. Moreover, the positioning member can also be affected in this way by the hydraulic medium in both axial directions, and leakage from or into the positioning chamber can occur in the space of the actuator piston.

The valve opening advantageously becomes a cylindrical bore, and the valve member has a conical section which can be displaced into the valve opening, whereby the flow area of the valve opening is gradually reduced. This makes it possible to obtain an appropriate relaxation sequence for the exhaust valve.

The invention is now described in more detail in an embodiment manner with reference to the schematic accompanying drawings.

1 shows an exhaust valve 1 for a large two-stroke crosshead engine with a spindle 2, which spindle 2 is to be axially displaced in a spindle guide 3 mounted to the housing of the exhaust valve. It is journaled so that its lower end faces the combustion chamber of the engine cylinder (not shown) and is mutually connected to the lower part 6 fixed to the lower side of the housing 4 mounted to the cylinder cover (not shown). It has a valve disk 5 that acts. The valve disc 5 has a seat surface 7 which interacts with an opposing fixed seat surface 8 on the lower part 6. In the open position (not shown) of the valve, gas from the engine cylinder can flow out through the exhaust channel 9.

At the end of the spindle facing away from the disk 5, an actuator 11 is arranged, which comprises a housing 12, at the upper end of which a hydraulic actuator 13 is arranged, of which the valve housing 4 is arranged. There is a so-called pneumatic spring 14 in between. The exhaust valve 1 is opened by the hydraulic actuator 13, and hydraulic fluid is supplied through the connection 15 to the actuator 13. The hydraulic fluid can be supplied via an electronically actuated control valve that can selectively connect the connecting portion 15 with a high pressure conduit and a return for hydraulic fluid. The hydraulic fluid can also be supplied from a cam-driven pump cylinder. The exhaust valve 1 is closed by a pneumatic spring 14, which comprises a spring piston 16 mounted on the valve spindle 2 of the air cylinder 17. Instead of pneumatic springs, the entire actuator 11 can be designed as a double acting hydraulic actuator.

2 shows an actuator piston (coaxially aligned with an extension of the valve spindle 2, coaxially with an extension of the valve spindle 2 such that the spindle 2 is rotatably connected with the piston 19 about its axis). 19) is shown. The actuator piston 19 can be displaced in the hydraulic cylinder 20 of the actuator housing 12, and a pressure chamber 21 is formed in the cylinder 20 above the piston 19. The hydraulic fluid channel 22 has a cylindrical bore shaped valve opening disposed in the end wall 24 of the cylinder 20 opposite the hydraulic connection 15 outside the actuator housing 12 to the top of the actuator piston 19. 23). The valve opening 23 is coaxially disposed in the cylinder 20 and can be gradually interrupted from the flow, and the valve member 25 disposed in the actuator piston 19 and projecting therefrom is a piston in the cylinder 20. It has an upper conical section 26 which can slide into the opening 23 upon displacement of 19. The valve opening 23 and the valve member 25 can also be of another design allowing a gradual closure of the flow; For example, the upper surface of the valve member may have a longitudinal recess with a cross section that is cut diagonally or decreases downward.

Under its conical section 26, the valve member 25 has a cylindrical outer surface 27 which can be displaced longitudinally at the positioning member 28, which also has a cylindrical bore 29 of the actuator piston 19. It has a cylindrical outer surface 41 which can be displaced longitudinally in. At its lower end, the valve member 25 has a collar 30 projecting outwardly, the upper surface of which is in contact with the lower surface of the positioning member 28, at the position shown in FIG. The valve member 25 has an inner coaxial bore 31 which is closed upward by the top wall 32. One end of the compression spring 33 is in contact with the upper wall 32, and the other end is in contact with the bottom of the recess in the lower wall 40 of the inner space 34 of the actuator piston 19. The space 34 of the piston 19 communicates with the pressure chamber 21 of the cylinder 20 via one or more passages 35 of the actuator piston 19. At its lower end, the positioning member 28 has an outer cylindrical wall 38 having a larger diameter than the collar 30 of the valve member 25 and which can slide in the cylindrical bore 37 of the actuator piston 19. Has a collar 36 with. The collar 36 of the positioning member 28 is affected at its lower surface by one end of the compression spring having a larger diameter than the collar 30 of the valve member 25, the other end of which is a piston ( It is in contact with the lower wall 40 of the space 34 of 19.

The upper surface of the collar 36 of the positioning member 28 defines an annular positioning chamber 42 formed by the cylindrical outer surface 41 and the cylindrical bore 37 downwards. Upwardly, the positioning chamber 42 is formed by a circumferential top wall 43 connecting the walls of the two cylindrical bores 29, 37 of the actuator piston 19. In the bore 29 and / or the bore 37, the positioning member 28 guides with a constant gap so that hydraulic fluid can flow by leakage between the positioning chamber 42 and the pressure chamber 21. do. If more leaks are needed, a separate leak channel can be formed in the actuator piston 19. The check valve 44 in the flow passage of the actuator piston allows hydraulic fluid to flow from the pressure chamber 21 to the positioning chamber 42. At the top, the positioning member 28 protrudes to some extent from the actuator piston 19, and in the closed position of the exhaust valve 1 shown in FIG. 2, a fixed stop on the end wall 24 of the cylinder 20. It has an upper surface 45 that abuts portion 46. A recess 47 is formed in the circumferential wall portion of the positioning member 28 that protrudes from the piston 19, and the recess is an exhaust valve 25 during the opening or closing of the exhaust valve 1. When moving to some extent into the piston 19, hydraulic fluid passes between the channel 22 of the housing 12 and the pressure chamber 21. In the presented embodiment, the recesses 47 divide the surface 45, but they do not need to be continuous to the surface 45, and the surface 45 may extend as a complete circumferential surface.

When the exhaust valve 1 is opened, the pressurized hydraulic fluid is supplied to the hydraulic channel 22 so that the valve member 25 is displaced from the position shown in FIG. 2 to the position shown in FIG. The hydraulic fluid can then freely flow into the pressure chamber 21 and the valve spindle 2 is displaced downwards, lifting the valve disc 5 from the fixed seat 8.

When the valve is closed, the pressure in the hydraulic channel 22 is reduced, hydraulic fluid is pushed back from the pressure chamber 21 into the channel 22, and a pneumatic spring 14 presses the valve spindle upwards. The spring 33 now presses the valve member 25 to its extended position of the piston 19.

During the opening and closing sequence, some hydraulic fluid leaks from the positioning chamber 42 to the pressure chamber 21 through the above-mentioned leak, and the springs 33 and 39 are directed to the positioning member 28 with upward force. affect. The spring 39 may be omitted. Irrespective of the slow upward movement of the actuator piston 19, the positioning member 28 is held in the piston by the volume of hydraulic fluid inherent in the positioning chamber 42, and the valve 1 is being closed. Since the collar 30 of the valve member 25 contacts the positioning member 28 due to the influence from the spring 33, the valve member 25 is connected to the movable seat surface 7 of the valve disc 5. Retained at a constant distance in relation to, the relaxation of the closing movement starts when the movable seat surface 7 is at a constant distance from the stationary seat surface 8. For example, if the length of the valve spindle 2 increases due to heating, the positioning member 28 will be pressed to some extent into the actuator piston 19 upon final closing of the exhaust valve 1, The upper surface 45 of 28 abuts the stationary stop 46 of the pressure chamber 21. Accordingly, a constant hydraulic fluid will flow from the pressure chamber 21 into the positioning chamber 42 through the check valve 44, and then the positioning member 28 will be maintained in the new position. On the other hand, when the length of the spindle decreases, the positioning member 28 adapts itself to the new position due to the slow upward movement mentioned above, thereby achieving a uniform and accurate closing of the exhaust valve.

The check valve 44 can be oriented so that the ball moves in the axial direction of the piston 19, but it is advantageously otherwise oriented in the radial direction of the piston, so that the ball is positioned in the positioning member 28. By firmly contacting the seat except when it is displaced by contact with the fixed stop 46 of the pressure chamber 21, the ball is lifted from the seat, allowing hydraulic fluid to pass through the check valve. . Other types of check valves may also be used.

4 shows an implementation of a hydraulic actuator 13 in which the actuator has a multistage piston having a first piston 19 and a second piston 48 that is longitudinally displaceable from the first piston 19. Give an example. The second pressure chamber 49 above the second piston 48 communicates with the first pressure chamber 21 via the channel 50 of the first piston 19, which is of the piston 19. The arrangement of the valve member 25 corresponds to the piston 19 of the embodiment shown in FIG. The movement of the first piston 19 is limited by the contact of the protrusion 51 to the stationary stop 52 in the first pressure chamber 21 after the first displacement of the piston.

Figure 5 shows another embodiment of the positioning member 28, which positioning chamber 42 is defined by the positioning member 28 and also by the actuator piston 19 radially outward. Although formed as an annular chamber, the annular chamber in the axial direction is defined by the actuator piston 19 downwardly by the positioning member 28. In this way, when the upper surface 45 of the positioning member 28 is in contact with the stationary stop 46 of the pressure chamber 21, positioning is caused by displacement of the positioning member 28 in the piston 19. In contrast to the embodiment of FIG. 2 where the volume of the chamber 42 is increased, the positioning chamber 42 may be reduced in volume by displacement of the positioning member 28 in the piston 19. In this embodiment, the check valve 44 shown in FIG. 2 can be omitted, so that hydraulic fluid leaks between the positioning member 28 and the actuator piston 19 when the volume of the positioning chamber 42 decreases. It should be noted that

6 shows another embodiment of the positioning member 28. The positioning member 28 forms positioning chambers 42a and 42b, respectively, above and below the radial projection on the member 28, one of which chamber 42a being of its volume at the aforementioned contact. Is increased, and the volume of the other chamber 42b is reduced. Under certain circumstances, this will allow more stable positioning of the positioning member 28. Furthermore, in this embodiment the positioning member 28 is reduced in cross section upward and slides into the annular groove 54 of the end wall 24 of the pressure chamber 21 upon the final closing of the valve 1. It should be noted that by forming the upper wall section 53, the movement of the positioning member 28 is attenuated before the positioning member 28 is brought into contact with the stationary stop 46 disposed below the groove 54. do.

FIG. 7 shows a plurality of cylindrical pistons 56 distributed over the valve member 25, journaled to the cylinder 57 of the actuator piston 19 and displaceable in the axial direction of the actuator piston 19. Another embodiment of the positioning member 28 is jetted. The piston 56 is upwardly affected by the compression spring 39 and forms a positioning chamber 42 in its cylinder 57. On its lower side, the piston 56 abuts the collar 30 of the valve member 25, on its upper surface, it is an upwardly extending push rod that is guided to a limited likelihood of leakage through the upper wall of the actuator piston 19. By having 57, the upper end of the push rod 57 can abut the fixed stop 46 of the pressure chamber 42 when the valve 1 is closed, so that the volume of the positioning chamber 42 Increases. Instead of a plurality of pistons 56, a single annular piston having a cross section corresponding to the piston 56 shown in Fig. 7 and having a plurality of push rods 57 may be used.

8 shows one embodiment of an actuator 13 in which the valve member 25 and the positioning member 28 are designed integrally. The design of the two members 25, 28 shown in FIG. 8 is almost the same as the design of the embodiment shown in FIG. 2, but the other designs of the aforementioned members 25, 28 differ from the valve member 25 and positioning as an integral member. It may be used for the member 28. In the operation mode for this embodiment, since the two members 25 and 28 are integrated, the positioning member 28 with the valve member 25 into the actuator piston 19 during opening of the exhaust valve 1. Same as mentioned above, except that it is simply displaced. Since the hydraulic fluid leaks from the pressure chamber 21 to the positioning chamber 42 relatively slowly, the hydraulic volume of the positioning chamber 42 is intended to hold the positioning member 28 in place, and therefore the valves in the actuator piston. The above-mentioned displacement of the positioning member occurs, but since its volume is increased, a vacuum is formed in the positioning chamber 42. This displacement will quickly become substantially equal when the valve member leaves the valve opening and is no longer affected by the downward large force. The sequence during closing of the exhaust valve is as described with respect to the embodiment of FIG. 2, but the valve and positioning members 25, 28 themselves act upon the actuator piston when contacted on the stationary stop 46 of the pressure chamber 21. It is noted that it may be displaced in 19), and that the exhaust valve is placed in its closed position for a suitable period of time to allow a constant amount of hydraulic fluid to leak into the positioning chamber 42.

The embodiments presented can be combined in a variety of ways, in which a system having a valve member 25 and a positioning member 28 is incorporated into another valve actuator with one or more pistons without departing from the scope of the invention. Can be.

By the above-described configuration, a hydraulically actuated exhaust valve is provided that enables uniform damping of the closing motion of the valve.

1 is a longitudinal sectional view of a hydraulically actuated exhaust valve;

2 is a partial longitudinal cross-sectional view of a hydraulic actuator for exhaust valve according to the present invention.

FIG. 3 is a view of the actuator of FIG. 2 during opening of the exhaust valve. FIG.

4 is a partial longitudinal cross-sectional view of an embodiment of an actuator having two stages.

5 to 7 show another embodiment of the positioning member of the actuator.

Figure 8 shows another embodiment of the valve and the positioning member.

<Explanation of symbols for main parts of drawing>

1: exhaust valve 2: spindle

3: spindle guide 4: housing

13: hydraulic actuator 19: actuator piston

20: hydraulic cylinder 23: valve opening

25 valve member 28 positioning member

42: positioning chamber

Claims (12)

A hydraulic fluid having a hydraulic actuator 13 comprising at least one first actuator piston 19, the first actuator piston 19 being capable of being supplied and discharged through the hydraulic fluid channel 22. Hydraulic actuation for the internal combustion engine allowing the exhaust valve 1 to be opened and closed by moving coaxially aligned in the extension of the exhaust valve spindle 2 to form the pressure chamber 21 for movement in the cylinder 20. In the exhaust valve, A valve member 25 having an associated positioning member 28 is journalably displaced in the first actuator piston 19 in the axial direction of the first actuator piston 19 so as to be spaced apart from the actuator piston 19. Spring-loaded, the positioning member 28 can change the volume of the positioning chamber 42 at the actuator piston 19 by displacement in the actuator piston 19 in the axial direction of the actuator piston, and exhaust In the closed position of the valve 1, the fixed stop 46 of the pressure chamber 21 can be brought into contact, and the displacement of the valve member toward the valve opening 23 causes the hydraulic fluid channel 22 to become a valve member ( A hydraulically actuated exhaust valve (1) for an internal combustion engine, characterized in that it develops into the pressure chamber (21) of the valve opening (23) at least partly blocked by 25). 2. The hydraulically actuated exhaust valve (1) according to claim 1, characterized in that the valve member (25) and the positioning member (28) are formed completely integrally. 2. The valve member (25) according to claim 1, wherein the valve member (25) is cylindrical, and also cylindrical and guided coaxially in a positioning member (28) coaxially guided in the first actuator piston (19), the piston The wall portion facing out of 19 has an end surface 45 and at least one passage 47 which can abut a fixed stop 46 of the pressure chamber 21, the valve member 25 being A hydraulically actuated exhaust valve (1) for an internal combustion engine, characterized by having a lower collar (30) having an upward contact surface for contact with a downward contact surface on the positioning member (28). 4. The hydraulically actuated exhaust valve (1) according to claim 3, characterized in that the positioning chamber (42) communicates with the pressure chamber (21) via a flow passage having a non-return valve (44). One). (Correct) The check valve 44 is closed by a ball, and the valve 44 has a ball from the seat when the positioning member 28 contacts the fixed stop 46. A hydraulically actuated exhaust valve (1) for an internal combustion engine, characterized in that it is just oriented to be lifted. (Correct) The hydraulically actuated exhaust valve (1) according to claim 3, wherein the positioning member (28) is loaded by a separating spring (39) in a direction spaced from the actuator piston (19). (Correct) The volume of the said positioning chamber 42 is in contact with the fixed stop 46 of the pressure chamber 21 in any one of Claims 1-6. A hydraulically actuated exhaust valve (1) for an internal combustion engine, characterized by an increase in time. (Correct) The positioning member 28 according to any one of the preceding claims, wherein the positioning member 28 has a lower collar 36 which is guided in the cylinder 37 of the actuator piston 19, and the position The determination chamber 42 is disposed around the positioning member 28 and is formed in an annular shape formed by the collar 36 of the positioning member 28 downwardly and by the upper limit of the actuator piston 19 upwardly. A hydraulically actuated exhaust valve (1) for an internal combustion engine, characterized by a chamber. (Correcting) The fixed stop 46 of the positioning member 28 and the pressure chamber 21 according to any one of claims 1 to 6 is, for example, the stage of the pressure chamber 21. Positioning member 28 prior to contact with stationary stop 46 by a circumferential cross-sectional tapered wall portion 53 aligned on positioning member 28 slid into circumferential groove 54 of subwall 24. Hydraulically actuated exhaust valve (1) for an internal combustion engine, characterized in that it is formed to be attenuated. (Correct) The internal combustion according to claim 1, wherein the volume of the positioning chamber 42 is reduced by the contact of the positioning member 28 with the fixed stop 46 of the pressure chamber 21. Hydraulically actuated exhaust valve for engine (1). (Correct) The valve member 25 area | region of any one of Claims 1-6 arrange | positioned at the said actuator piston 19 and facing away from the valve opening 23 is arrange | positioned at the actuator piston 19. And exposed to the space 34 in communication with the pressure chamber 21 via the opening 35 of the actuator piston 19. (Correct) The valve opening 23 according to any one of claims 1 to 6, wherein the valve opening 23 is a cylindrical bore, and the valve member 25 is a conical section 26 which can be displaced into the valve opening 23. ), The hydraulically actuated exhaust valve (1) for an internal combustion engine, characterized in that the flow area of the valve opening is gradually reduced.