KR100704369B1 - A method for actuation of an exhaust valve for an internal combustion engine and such an exhaust valve - Google Patents

Abstract

In order to control the exhaust valve, the spool 21 of the control valve is displaced longitudinally to connect the high pressure port 8 or the low pressure port 11 with the first pressure chamber 29 of the actuator in which the actuator piston can be displaced. do. The exhaust valve spindle 4 is displaced in the same movement as the longitudinal displacement of the spool 21. The spindle can be positioned between the fully open position and the fully closed position, and moves along the spool 21 between the closed and open positions of the exhaust valve.

Description

Exhaust valve for internal combustion engine and its operation method {A METHOD FOR ACTUATION OF AN EXHAUST VALVE FOR AN INTERNAL COMBUSTION ENGINE AND SUCH AN EXHAUST VALVE}

1 is a view of an exhaust valve according to the present invention.

2 to 4 are examples of continuous movements performed by the exhaust valve of FIG.

5 is a view showing an embodiment in more detail.
5A is a partially enlarged view of the left portion of FIG. 5.

Explanation of symbols for the main parts of the drawings

1: cylinder 2: exhaust valve

3: cover 4: spindle

5: combustion chamber 7: high pressure conduit

8: high pressure port 10: low pressure conduit

11: low pressure port 13: piston

14: spring chamber 15: pneumatic conduit

21: spool 24: housing

29: first pressure chamber 30: wall

38: shoulder 40: second pressure chamber

41: channel

The present invention relates to a method of operating an exhaust valve for an internal combustion engine in which the exhaust valve is opened by a spool of a control valve displaced in a longitudinal direction to connect the first pressure chamber and the high pressure port of the actuator, wherein the actuator piston is configured to open the exhaust valve. And the control valve spool is longitudinally displaced to connect the first pressure chamber and the low pressure port when the exhaust valve is closed.

Such exhaust valves are known from US Pat. No. 3,209,737 wherein the control valve is electrically operated by a solenoid valve and operated by a cam on the camshaft. The control valve continuously connects the first pressure chamber with the high pressure port while opening the exhaust valve and continuously connects with the low pressure port when closed. Thus, the movement of the exhaust valve is controlled according to the time interval between the pressure acting on the actuator piston and the degree of hydrostatic pressure, and the actuator piston has an open area and a closed area. In practice, the control valve has one position each for closing and opening the exhaust valve, so that the control action occurs at the start of each opening and closing movement when the actuator piston starts to move the spindle, so that the movement Continues while in the open position. In operation, a change in hydrostatic pressure may occur, causing the speed of the spindle motion to fluctuate. The exhaust valve is controlled to properly move at a particular engine load, such as maximum load, and its opening speed does not change with the rotational speed of the engine, and consequently, the exhaust valve is not opened at the optimum time at the load of the other engine. The braking action of the spindle during the final part of the closing motion is done by throttling the hydrostatic flow through the gap formed by the pin on the spindle pushed into the bore of the stationary housing.

It is an object of the present invention to provide a method for more accurate control of an exhaust valve, including control during operation.

In view of the above, the present invention provides a displacement of the spindle of the exhaust valve in a proportional relationship such that the ratio of the displacement of the control valve spool to the longitudinal displacement of the spindle of the exhaust valve is equal to 1: 1 while displacing the control valve spool in the longitudinal direction. And the spindle can be positioned at a selected position between the fully open position and the fully closed position, wherein the spindle of the exhaust valve moves along the positional movement of the control valve spool between the open and closed positions of the exhaust valve. It is done.

If the spindle is displaced proportionally in the longitudinal direction with the spool, adjusting the spool is transmitted to the corresponding movement of the exhaust valve. Therefore, there is a direct correlation between the current position of the control valve spool and the current position of the exhaust valve spindle, so that the adjustment movement of the exhaust valve is only affected by the adjustment of the spool, and the time or hydrostatic pressure when the spool is in a specific position It is not affected by change. While the spindle is between the positions of the terminal, the spool directly controls the movement of the spindle, while the spool places the spindle in an intermediate position. Since the spindle of the exhaust valve further moves along the positional movement of the spool of the control valve, the exhaust valve can be moved as desired in the engine cycle regardless of the engine's current rotational speed.

Preferably, since the throttling operation causes energy loss, the last part of the operation of closing the exhaust valve is actively controlled by the control valve instead of braking the spindle by throttling. If the control valve brakes the spindle by controlling the final part of the closing motion, the amount of energy passing from the high pressure hydrostatic flow to the actuator of the exhaust valve is reduced. By eliminating the need for relevant parts with good precision to form the throttle spacing, the design of the actuator can be simplified.

It is also possible to vary the speed of the exhaust valve in a predetermined portion of the motion path between one engine cycle and the next engine cycle. For example, the speed of the exhaust valve can be increased at the start of the opening movement, in which case the opening of the valve is accelerated. As a result of the rapid acceleration of the spindle moving quickly from the closed position to the open position, a large outflow area of the desired level is quickly realized, reducing the degree of heating of the valve disc and the fixed valve seat. The possibility of speed change of the exhaust valve during engine operation makes it possible to continuously adjust the current operating state.

The method according to the invention offers the desired possibility of changing the desired position in which the spindle remains open, since the opening movement of the exhaust valve can be stopped in the open intermediate position before full opening is reached. When the engine is operating under partial load, the amount of exhaust gas is a small amount per engine cycle, and depending on the engine type, the rotation speed of the engine can be slower, providing more time to exhaust the exhaust gas. Both conditions result in a reduction of the runoff area. When the engine is operating at partial load, the exhaust valve can be moved to an intermediate position providing a reduced outflow area. The movement distance of the exhaust valve from the closed position to the intermediate position is shorter than the movement distance from the closed position to the fully open position. The consumption of the hydrostatic fluid is affected by the travel distance. When the travel distance is shortened, the consumption of the hydrostatic fluid is also reduced. Energy is required to compress the hydrostatic fluid, and energy decreases as the consumption of the hydrostatic fluid decreases.

Accurate controllability of the spindle movement can be used to ensure that the spindle is held in a ventilation position during the waiting time at the end of the closing movement, with the ventilation gaps between the seat surfaces of the exhaust valves appearing. The spindle is then moved to the fully closed position. By opening the exhaust valve near the fully closed position for a while, relatively cool air passes through the substantially cooled seat surface. As a result, the average temperature of the valve material is lowered to extend the life of the exhaust valve, and inexpensive material valve seat can be used. The durability of the valve seat is further enhanced so that the remaining particles are blown away by the powerful flow of aeration air which reduces the chance of leaving recesses.

The waiting time is appropriately 4 to 50 mW. This range is suitable for low or medium speed engines with large bores. If the waiting time is less than 4 kW, the desired cooling effect does not appear, and if the waiting time is more than 50 kW, the consumption of cooling air becomes too large.

Preferably, the spindle in the venting position is held on the seat surface at a mutual distance of 0.02 to 0.50 mm while allowing air to flow at the speed of sound through the vent gap, preferably 0.05 to 0.2, which reduces the amount of outflow air. Taking the mm range, the compression pressure remains unaffected.

 By moving the spindle to the substantially closed position at the final part of the closing motion and shortly afterwards in the opening direction, the possibility of leaving concave marks is reduced. By almost completely closing at first, the particles present between the valve seat surfaces are broken into dusty material, and when the spindle is subsequently opened for a moment, a strong aeration flow is generated that blows away the dusty material with exhaust gas. When the valve is then completely closed, no particles are present on the seat surface, and the formation of recesses is prevented.

 In order to limit the charge air discharge, the combined process of cooling and cleaning the seat surface can be limited in time, so that short time movement in the open direction and movement to the fully closed position are less than one tenth of the time the exhaust valve is opened. It takes place in a short time.

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an exhaust valve for an internal combustion engine, wherein the exhaust valve controls a hydrostatic pressure actuator having a valve spindle, an actuator piston associated with a fixed actuator housing having at least one first pressure chamber, and a first pressure chamber. And a control valve connectable with the high or low pressure port of the valve housing.

 A control valve housing having a high pressure port and a low pressure port is displaceable in the longitudinal direction, the longitudinal displacement of the control valve housing being proportional to the longitudinal displacement of the control valve spool between the open and closed positions of the exhaust valve spindle. By configuring the exhaust valve in a manner, more accurate control can be realized. When the spindle and housing are brought to the desired position defined by the current position of the control valve spool, by displacing the housing like the spindle, the control valve can not move hydrostatically in a simple manner.

Preferably, the control valve housing does not move longitudinally with respect to the displacement valve valve, so that when the control valve housing is displaced in the longitudinal direction, the housing and the spindle are displaced in the same movement.

As a simple design, the actuator piston is integrally formed with the control valve housing. In another simple design, the upper portion of the valve spindle is integrally formed with the control valve housing. By allowing the actuator itself to be directly controlled by the control valve spool without any intermediate connecting member, the control of the exhaust valve is straightened without delay elements. High reliability is ensured by minimizing the number of control ports.

In one embodiment, the control valve spool is installed such that the fixed coil portion does not move longitudinally with respect to the movable magnet portion of the linear motor mounted coaxially in the extension of the exhaust valve spindle. The use of a linear valve for the adjustment of the control valve spool effectively achieves a simple design of the mechanical element, because the linear motor is based on the electrical signals from the control unit, regardless of the current position and speed of the moving part. Because it can be controlled. Optionally, the control valve spool can be moved by a cam on the camshaft, but it limits the possibility of freely changing the movement pattern of the exhaust valve during engine cycle during operation and also the mechanical synchronization process between the camshaft and the crankshaft of the engine. in need.

If a linear motor is used, the movable magnet portion of the linear motor preferably has a longer stroke distance than the maximum movement of the exhaust valve between the closed position and the fully open position. This offers the positive possibility of compensating for changes in the exhaust valve length due to wear, temperature changes, etc., and also provides more precise control because the characteristics of the linear motor can change in the region near the end position. to provide.

1 shows the top of a cylinder 1 of an internal combustion engine with a two-stroke or four-stroke engine with a large cylinder bore, such as a bore of at least 200 mm, characteristically a 240-1200 mm bore. The engine may be a two-stroke crosshead engine for propulsion of a ship that produces supercgarge and fixed power at constant pressure. The exhaust valve 2 is installed at the top of the cylinder of the cylinder cover 3. The cylinder is evacuated by non-uniform flow evacuation, such as a scavening air port located at the bottom of the cylinder. The exhaust valve may be located anywhere than the center of the cylinder cover, such as the side wall of the cylinder, and some exhaust valves may be installed in the same cover.

The exhaust valve comprises a spindle 4 with a valve disc having an upwardly annular seat surface that is in sealing contact with the downwardly fixed seat surface of the lid 3. In the closed position, the exhaust valve interrupts the connection between the combustion chamber 5 and the exhaust passage 6, and in the open position the spindle 4 is displaced downward in the longitudinal direction.

In the first embodiment shown in FIG. 5, the actuator 47 has an actuator housing 24 and an actuator piston designated 48. The actuator piston 48 has a first piston portion 32 having a second piston portion 34. The second piston part 34 is integrally formed with the top of the spindle 4 in the embodiment shown in FIG. 5. The control valve indicated by 49 has a control valve spool 21 and a control valve housing 45. The control valve housing 45 is integrally formed with the spindle 4 and the second piston part 34 in the embodiment shown in FIG. 5. To illustrate this, the vertical broken line a represents the transition between the second piston part 34 and the control valve housing 45, and the horizontal broken line b is on the one hand with the second piston part 34. FIG. 5A is an enlarged view of the left part of FIG. 5 showing the transition between the control valve housing 45 and on the other hand the transition between the lower part of the spindle 4 and the control valve housing 45. The high pressure conduit 7, in which high pressure hydrostatic flow of 100 to 500 bar, more specifically 150 to 300 bar, takes place is led to the high pressure port 8 of the control valve housing 45 (see the embodiment of FIG. 5). The low pressure conduit 10 connects the low pressure port 11 of the control valve housing to the outlet or restoring portion of the hydraulic fluid used. The outlet of the upper side of the lid 3 of the bottom of the outer valve housing 12 may be connected to the low pressure conduit 10 to eliminate fluid leakage. Low pressure conduits are arranged coaxially around the high pressure conduit, which has a length of several meters down the passage from the exhaust valve housing to the high pressure conduits running side by side to the engine, and the hydrostatic conduits to inject fuel with the hydrostatic fluid. It is especially useful for large engines that can supply drive. Coaxially positioning the low pressure conduit and the high pressure conduit results in less space consumption than the low pressure conduit and the high pressure conduit. Due to this coaxial arrangement in which the high pressure conduit is located inside the low pressure conduit, the low pressure conduit also acts as a protective film around the high pressure conduit in the event of a breakdown of the high pressure conduit. This is because when the high pressure conduit breaks, the liquid from the high pressure conduit flows out into the low pressure conduit rather than out of its periphery.

In the illustrated embodiment, the pneumatic spring piston 13 is fixed to the spindle 4 and displaceably positioned in the pneumatic spring cylinder 50 so that the pneumatic spring chamber 14 is positioned below the piston, and also the pneumatic conduit ( Compressed air from 15 is provided. The pneumatic spring acts continuously on the spindle 4 with the upward force in the direction of the closed position.

The electronic control unit 16 connected to the associated cylinder receives data from the signaling device 17 when opening and closing the exhaust valve. This data is concentrated on the entire engine and is dependent on the current engine load at which the engine is operating in one of several determined operating modes required for the exhaust valve in a special case deviating from the standard operating mode or an operating signal determined by another control unit. Data about the current angular position of the crankshaft for the purpose of operating at the opening and closing times in the control unit 16 based on the data received from other signal sources 18 as possible data and possible information.

Via the signal wire 19, the control unit 16 transmits a setting signal to the exhaust valve as necessary while the spindle is moving between the closed and open positions, and via the wire 20, the control unit transmits the spindle itself. The position signal can be received at or from a sensor measuring the current position of the spindle on a member connected to the spool 21 of the control valve 49.

An electromechanical transducer 22 converts the electrical signal from the control unit into the linear displacement amount of the spool 21 of the control valve 49. The spool and the spindle are displaced proportionally in the longitudinal direction at a predetermined ratio such as 1: 4.

Since the spool and the spindle can be positioned at a selected intermediate position, by displacing the spindle 4 in the longitudinal direction proportional to the position of the spool, the control unit 16 allows the spindle at any time of its movement through the electromagnetic transducer 22. Can be accelerated or stopped. The selected position may be a predetermined intermediate position or a position regularly calculated by the control unit based on the current operating mode of the engine and / or the measurement of a series of operating movements of the exhaust valve. In FIG. 2, an example of a series of motions is shown in a graph showing the downward displacement l of the spindle as a function of time t. At point (a), the exhaust valve is completely closed and the longitudinal displacement of the control valve spool has just begun so that the actuator exerts an opening force on the spindle which initiates the operation of the spindle and this process is uniformly up to point (b). The closing force at which the spool is sufficiently decelerated at point (b) to close the pneumatic spring is substantially sufficient to stop the spindle 4 at the fully open position lmax at point (c). When the transducer 22 begins to displace the spool in the direction of the starting point, the spindle remains stationary until the closing movement starts at point (d). When the spindle is approaching the closed position, the control unit 16 stops at the point (e) a short distance from the closed position between the seat surfaces, for example with a 0.3 mm vent. You can slow down the spool. At such small intervals, the air flowing outward is at the speed of sound, which entails a powerful cooling effect, and the flow volume of air is very small because the interval is so narrow. The cooling action can be performed on the piston 23 without significant loss of compression force of the combustion chamber. Atmosphere which can be freely adjusted by the control unit in relation to the experimental value of the relationship between the current operating mode and the need for cooling or can be adjusted based on the actual measurement of the sheet material temperature suitably carried out by a temperature sensor installed in the fixed valve seat. After time passes, the exhaust valve is completely closed at point (f).

If the cylinder needs to be emptied rapidly or if it is necessary to operate strongly with scavening air, the control unit 16 can wait longer before the speed of the spindle 4 is lowered and instead, A strong deceleration process can be made from point (b ') shown. In a corresponding manner, the broken line shows that the closing movement can be accelerated as desired due to a temporary change in the operating state by moving the spool quickly in the direction of the starting point until the valve is closed at the point (f ').

Figure 3 shows a series of closing procedures in which the spindle is first moved to the closed position at the point (f ") and immediately reopened to the vented position indicated by (e). As described above, thereby, between the closing valve seats The valve seat is not exposed to strong forces until the combustion pressure begins to act on the valve disc, and the temporary valve closure does not exert such a large impact on the seat material to form recesses. After the proper waiting time has passed, the spindle 4 is displaced to the fully closed position as shown at point (f "').

When the engine is running at partial load, only a small volume of gas is needed for exhaust per revolution of the engine. Thus, the spindle does not need to be moved to the fully open position. As shown in Fig. 4, by the control unit 16 decelerating and stopping the spool, the spindle 4 is moved downward by a very small distance, thereby reducing the consumption of hydrostatic flow. If the control unit receives a warning signal that the amount of hydrostatic fluid in the high pressure conduit 7 is abnormally small, a shorter opening action may be selected.

In the following description of other embodiments of the present invention, the same reference numerals as described above may be used for structures performing the same function.

FIG. 5 shows the top of the spindle 4 integrally provided with both the second piston part 34 of the actuator and the control valve housing 45. The left half of FIG. 5 shows the control valve 49 and the actuator 47 at the starting point at which the exhaust valve is closed, and the right half shows the open position. The spindle 4, in a pressure-sealed form, has a downward tubular shield 27 shield for the transducer 22 installed coaxially with the spindle 4 and an actuator housing with an end cover 26 at the top. Passed into the lower section 25 of the central bore of (24). The converter can be a lint of a linear motor type (trade name) made by Sulzer Electronics AG of Switzerland, and a model name P01-23 x 160 with a maximum stroke of at least 140 mm. The transducer has a movable magnet part 31 which is displaceable in the form of a stationary coil part and a magnet on the rod, and at the bottom of the rod the control valve spool 21 in the control valve 49 is directed to the movable magnet part 31. It is arranged not to displace in the longitudinal direction.

In the actuator housing 24, the end bottom 28 for the first pressure chamber 29 is fixed, and the annular wall 30 at the top of the spindle 4 is shielded with the cylindrical inner surface 37 of the end bottom. Between the cylindrical outer surface on 27 protrudes upward in the form of a pressure seal. The actuator piston 48 has a first piston part 32 having an upward first opening zone 33 formed by the outer and inner diameters of the annular piston part, and a second piston part having an upward opening zone 35. (34). In the starting position, the first piston portion abuts the upwardly annular surface of the second piston portion and the entire open area is pressure-sealed and the outer surface of the first piston portion 32 which slides along the inner surface of the chamber in a pressure-sealed fashion. In correspondence with the region of the annular zone formed by the outer surface of the wall 30 sliding along the cylindrical inner surface 37 of the end bottom.

During the downward movement of the actuator piston, the first piston portion 32 rests against the shoulder 38 on the inner surface of the actuator housing, whereby the second piston portion starts to move. While the open motion is maintained, the open area is formed of an annular zone formed by the outer surface of the wall 30 and the outer surface of the second piston portion 34 which slides along the inner surface 36 of the actuator housing in a pressure sealed manner. Reduced to the area.

The actuator piston is in pressure-sealed form an outer surface of the spindle 4 that slides along the lower region 25 of the actuator housing 24 and an outer surface of the second piston portion 34 that slides along the inner surface 36. It is further provided with a closed area 39 corresponding to the area of the annular zone formed by. The closed region is located in the second pressure chamber 40.

The high pressure conduit 7 is connected to the actuator housing of the second pressure chamber 40 and the channel 41 is led to the high pressure port 8. The low pressure conduit 10 is connected to the cavity of the actuator housing above the end bottom 28 and the channel 42 connects the cavity to the low pressure port 11. The spool 21 of the control valve is in the form of a pressure seal with the middle section of a small diameter and the inner side of the cylindrical bore of the control valve housing 45 formed directly in the upper section of the spindle 4, as in the illustrated embodiment. It has two cylindrical end sections that abut. Via the small channel 43, the control port 46 is in continuous communication with the first pressure chamber 29. In the neutral position of the control spool, the two end zones of the spool block high and low pressure ports. When the spool 21 is displaced downward with respect to the actuator piston, the high pressure port 8 is exposed so that fluid flows into the first pressure chamber and the actuator piston with the spindle 4 is displaced downward until the high pressure port is closed again. do. When the spool 21 is displaced upward with respect to the actuator piston, the low pressure port is exposed so that the actuator piston with the spindle 4 is displaced upward until fluid flows out of the first pressure chamber and the low pressure port is closed again. Thus, the actuator piston is controlled to strictly follow the positional movement of the spool 21.

Under this control, the open and closed area of the actuator piston is quite large, leaving extra force for the adjustment of the spindle 4, allowing for quick and precise adjustment. Since extra force is allowed, the size of the piston region can be calculated based on the minimum adjustable pressure of the high pressure conduit 7, so that a change in the pressure of the conduit only results in an increase in the extra force.

When the actuator performs the adjusting motion, the fluid flows through the actuator and cools the actuator. In the embodiment of FIG. 5 where the control piston housing is integrally coupled with the actuator piston, the channel 43 extends radially from the control port 46 to the first pressure chamber 29 so that the control port 46 can be removed from the control port 46. The channel 43 to the first pressure chamber 29 has a minimum length, providing the advantage that the control connection between the spool adjustment and the movement of the actuator piston is directly inelastic and minimizes the loss of power.

The outlet channel 44 may maintain a state where no leaking fluid is present in the space below the first piston portion 32. The embodiment of FIG. 5 need not be used with pneumatic springs on the spindle 4. If a pneumatic spring is used, the first closed region 39 may be omitted, and it should be taken into account that the pneumatic spring has a closing force when determining the size of the region.

The above method of maintaining the exhaust valve in the final stage, cooling the ventilating position and smashing any particles can also be used in connection with other actuators, such as cam-controlled actuators, but the above-described embodiment has It is particularly suitable for using the method.

The embodiment shown in FIG. 5 can also be modified. For example, the actuator piston can be manufactured separately and can be detached from the spindle 4 and can be bolted, screwed or dowels inserted into the bore through both parts, or means for mechanical fixation in the axial direction. By its extension. In the actuator itself, the control valve housing may be formed as a separate member that is inserted into and fixed to the bore of the actuator piston. For example, the fixing operation is performed by a bore of a piston having an outer surface of the conical shaped housing and a corresponding conical surface in which the housing is compressed and abuts and the parts can be contracted or screwed together.

Claims (14)

The exhaust valve is opened by the spool 21 of the control valve 49 which is displaced in the longitudinal direction to connect the first pressure chamber 29 of the actuator housing 24 and the high pressure port 8, and the actuator piston 48. Is displaced with the spindle 4 of the exhaust valve toward the open position of the exhaust valve, and the control valve spool 21 has a length so as to connect the first pressure chamber 29 and the low pressure port 11 when the exhaust valve is closed. In the method of operating the exhaust valve (2) for an internal combustion engine displaced in a direction, The spindle 4 of the exhaust valve is displaced proportionally in the longitudinal direction with the longitudinal displacement of the control valve spool 21, the spindle can be located at a selected position between the fully open and the fully closed position, the spindle of the exhaust valve (4) is a method of operating an exhaust valve for an internal combustion engine, characterized in that it moves along the positional movement of the control valve spool (21) between the closed position and the open position of the exhaust valve. Method according to claim 1, characterized in that the final part of the closing movement of the exhaust valve is actively controlled by the control valve (49). 2. A method according to claim 1, wherein the speed of the exhaust valve at a given portion of the path of motion is varied between one engine cycle and the next. 2. A method according to claim 1, wherein the opening movement of the exhaust valve is stopped in the open intermediate position before reaching the fully open position. 3. The spindle (4) according to claim 2, wherein during the final part of the closing movement, the spindle (4) is held for a waiting time in the ventilation position in which there is a ventilation gap between the surfaces of the seat of the exhaust valve, and then the spindle is moved to the fully closed position. Method characterized by done. 6. Method according to claim 5, characterized in that the spindle (4) is held in the venting position for a waiting time of 4 to 50 kPa. 6. Method according to claim 5, characterized in that in the vented position the spindle (4) is kept at a mutual distance of 0.02 to 0.50 mm on the seat surface. 8. The spindle 4 according to claim 3, during the final part of the closing movement, the spindle 4 is moved to the substantially closed position, immediately afterwards briefly in the opening direction, and then to the fully closed position. Method characterized by done. delete In the hydrostatic actuator 47 with the valve spindle 4, the fixed actuator housing 24 with at least one first pressure chamber 29 and the associated actuator piston 48, in the control valve housing 45 An exhaust valve for an internal combustion engine comprising a control valve 49 for connecting a first pressure chamber with a high pressure port 8 or a low pressure port 11, The control valve housing 45 with the high and low pressure ports can be displaced in the longitudinal direction so that the longitudinal displacement of the control valve housing is a displacement proportional to the longitudinal displacement between the open and closed positions of the exhaust valve spindle 4. An exhaust valve, characterized in that. 11. Exhaust valve according to claim 10, characterized in that the control valve housing (45) does not move longitudinally with respect to the displacement of the exhaust valve spindle (4). 11. The exhaust valve according to claim 10, wherein the control valve housing (45) is integrally formed with a portion (34) of the actuator piston (48) and an upper portion of the valve spindle (4). 13. The control valve spool (1) according to any one of claims 10 to 12, wherein the fixed coil portion of the linear motor is connected to the movable magnet portion (31) of the linear motor provided coaxially at the extension of the exhaust valve spindle (4). 21) exhaust valve, characterized in that is installed so as not to move in the longitudinal direction. 14. The exhaust valve according to claim 13, wherein the movable magnet portion (31) of the linear motor has a stroke distance greater than the maximum movement of the exhaust valve between the closed and fully open positions.

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