RU2557828C1 - Valve control device - Google Patents

Abstract

FIELD: engines and pumps.

SUBSTANCE: device includes a cam having a possibility of interacting with a valve stem so that opening and closing of the valve is provided at turning of the cam: a drive having a possibility of providing cam rotation. The device differs by the fact that it includes two storage elements for storage of mechanical energy, which can receive energy from the cam and transfer energy to the cam so that when one of the storage elements stores mechanical energy, the other storage element transfers mechanical energy to the cam.

EFFECT: reducing energy losses; improving efficiency and quick action of the valve control device.

11 cl, 6 dwg

Description

Technical field

The invention relates to the field of engine building and, in particular, to the field of devices for controlling valves of a gas distribution system of internal combustion engines (ICE). Also, the present invention can be used in various hydraulic and pneumatic systems for controlling valve operation.

State of the art

A device for controlling a valve is known, which is an electromechanical valve actuator (US patent No. 5765513, F01L 9/04, 06.16.1998), intended for use as an intake or exhaust valve of an internal combustion engine. An electromechanical valve actuator comprises a valve having a stem and a head that can open and close a channel for supplying fuel or a channel for releasing fuel combustion products, springs, including spring return valves to their original position, and a linear actuator containing electromagnets acting on the armature in the form of discs connected to the valve stem. The disadvantage of this electromechanical drive is the low efficiency, as well as low speed.

The closest analogue of the present invention is the gas distribution mechanism of an internal combustion engine (USSR author's certificate No. 1636570, F01L 9/04, 1984), which comprises a valve having a stem and a head that can open and close the fuel supply channel or the exhaust channel products of fuel combustion, a return spring that returns the valve to its original position after turning off the electric drive, and a linear electric drive having two electromagnets acting on two disk anchors connected to the rod valve. In the initial position, the valve described in this copyright certificate is open under the influence of a return spring. When power is applied to the winding of one of the two electromagnets, the electromagnet to which the power is supplied draws the corresponding armature and moves the valve stem connected to the armature, so that the valve head closes the fuel supply channel. To increase the speed of the gas distribution mechanism, the electromagnets operate alternately, which increases the available time for attenuation of transient induction phenomena.

The disadvantage of this solution is the low efficiency (efficiency) and low performance.

Low efficiency the closest analogue is due to the reciprocating nature of the movement of the movable elements of the valve during operation of the gas distribution mechanism. During operation of the gas distribution mechanism, the valve can be in one of two stable positions, open or closed, and in these positions the valve must be fixed for a certain period of time. In this solution, when the windings of the electromagnets are de-energized, the valve return spring biases the valve stem with the head and opens the channel for supplying the fuel mixture. In the open position, the valve is fixed by the force of the return spring.

When one of the two electromagnets is turned on, the movable part of the gas distribution mechanism, which includes the valve stem with a head, two disk anchors and a common central rod, moves linearly, and the valve return spring is compressed. The mechanical work of the electromagnet is converted into the potential energy of the return spring, which is compressed, as well as into the kinetic energy of the moving part of the gas distribution mechanism, the linear speed of which increases as it moves under the influence of electromagnetic forces. In the open position of the valve, the linear velocity of the moving part of the gas distribution mechanism is completely extinguished, since the valve head rests on a fixed housing, and all the kinetic energy of the moving part of the gas distribution mechanism, which arose due to the operation of the electromagnet, is converted into losses, that is, into heat.

The time to return the valve to the open position in the gas distribution mechanism must be limited. In order for the force of the return spring to overcome the decreasing force of attraction of the armature by the electromagnet after disconnecting the electromagnet winding and to accelerate the moving part of the gas distribution mechanism to the required speed, due to the set valve switching time, a significant force of the return spring is needed. The potential energy of the spring accumulated during compression of the spring due to the operation of the electromagnet, when the valve is returned to the open position, is converted into kinetic energy of the moving part of the gas distribution mechanism. In the final, open, position of the valve, the movable part of the valve timing mechanism comes into contact with the fixed body, and the moving speed of the movable part is also completely extinguished. In this case, the kinetic energy of the moving part of the valve timing mechanism accumulated due to the operation of the electromagnet will also be converted to heat.

Thus, with the reciprocating nature of the movement of the valve timing mechanism, each time the valve is switched, the kinetic energy of the moving portion of the timing mechanism is converted to heat. The kinetic energy of the moving elements of the device is generated due to the operation of electromagnets, in other words, due to the power of the power source, and, therefore, the efficiency gas distribution mechanism will be low.

It should be noted that, based on the general design of the valve, the movement of the valve stem with the head has a reciprocating nature, while it is not necessary that the movement of other movable elements of the electric drive of the valve stem (disk anchors and a common central shaft) also has a reciprocating nature . In addition, significant compression of the armature from the side of the electromagnets is necessary to compress the valve return spring and provide the specified valve switching time. To obtain the necessary force of magnetic attraction, the disk armature of the electromagnet must have a sufficient area and cross section. As a result, the mass of disk anchors of electromagnets during the implementation of the design of this solution can be several times the mass of the valve stem. Low efficiency This decision is due to the fact that the reciprocating movement during operation of the valve performs not only the valve stem with the head, but also the elements of the electric drive, i.e. disc anchors and a common central core.

The low speed of the device in accordance with this decision is due to an increase in the mass of the movable part of the gas distribution mechanism due to disk anchors of electromagnets. As noted above, the mass of the disk anchors significantly exceeds the mass of the valve stem. The increase due to the disk anchors and the common central rod of the mass of the movable part of the gas distribution mechanism, which must be accelerated from zero speed to a speed that provides a predetermined valve switching time, does not allow to obtain a high efficiency valve actuator. The use of two, as in this solution, or a larger number of electromagnets cannot significantly increase the speed of the gas distribution mechanism, since the number of movable disk anchors increases, and hence the mass of the moving part. Due to the large weight of the moving part of the gas distribution mechanism and the fact that the switching frequency of the valves of the gas distribution mechanisms is up to several hundred hertz, it is extremely difficult to ensure the normal functioning of the gas distribution mechanism of the internal combustion engine with the reciprocating nature of the movement of the armature of the electromagnets, during which the movement starts when the valve is switched from zero speed of all moving elements and ends with a complete stop of all moving elements Including armature.

Thus, the objective of the present invention is to increase the efficiency devices for controlling the valve and its speed.

Disclosure of invention

This problem is solved thanks to the device for controlling the valve of the gas distribution system of the internal combustion engine of the present invention, comprising a cam configured to cooperate with the valve stem, so that the valve is opened and closed when the cam is rotated, an actuator configured to rotate the cam, and characterized the fact that it contains two storage elements for storing mechanical energy, made with the possibility of receiving energy from the cam and transmitting energy Energy cam so that when one of the storage elements stores mechanical energy, the other storage element transfers mechanical energy to the cam.

This embodiment of the device for controlling the valve provides a technical result in the form of reducing energy losses, as a result of which the efficiency is increased and the speed of the valve control device. By reducing the kinetic energy loss of the moving elements of the valve, an increase in efficiency is achieved. and the performance of the proposed device for controlling the valve relative to the closest analogue.

According to yet another embodiment of the present invention, in the valve control device, the storage elements are springs or magnetic springs.

According to another embodiment of the present invention, in the valve control device, the circumferential surface of the cam comprises at least one portion located at a constant distance from the axis of rotation of the cam.

According to another embodiment of the present invention, in a valve control device, one of the storage elements is connected to a valve stem.

According to another embodiment of the present invention, in the valve control device, the springs or magnetic springs are aligned.

According to another embodiment of the present invention, in the valve control device, the storage elements cooperate with the cam via levers.

In addition, a method for controlling a valve of a gas distribution system of an internal combustion engine is proposed, including actuating a drive for turning a cam to a first equilibrium position corresponding to a first extreme position of the valve, while simultaneously storing energy by a first storage member for storing mechanical energy, stopping the drive when the cam reaches the first equilibrium position with holding the cam drive in this position, actuating the drive for initial cam rotation and from the first equilibrium position towards the second position of equilibrium, the valve according to the second extreme position the drive.

further cam rotation due to the energy stored by the first storage element in the direction of the second equilibrium position, while simultaneously storing energy by the second storage element for storing mechanical energy, actuating the drive to rotate the cam to the second equilibrium position while simultaneously storing energy by the second storage element mechanical energy, the drive stops when the cam reaches the second equilibrium position with the drive holding the cam in this position.

According to yet another embodiment of the present invention, the valve control method further includes actuating the actuator for initially turning the cam from the second equilibrium position toward the first equilibrium position, disengaging the actuator, turning the cam further due to the energy stored by the second storage member in the direction of the first position equilibrium, while simultaneously storing energy with a second storage element for storing mechanical energy, actuating the drive for I turn the cam to the first equilibrium position while simultaneously storing energy with the first storage element, stop the drive when the cam reaches the first equilibrium position while holding the cam drive in that position.

According to another embodiment of the present invention, in a method of controlling a valve at engine start-up, actuating the actuator to rotate the cam to the first equilibrium position includes alternating rotations of the cam by the actuator from the initial position clockwise and counterclockwise with an increasing angle of rotation.

Brief Description of the Drawings

Figure 1 shows an axial section of a gas distribution system of an internal combustion engine comprising a valve control device in accordance with one embodiment of the present invention, with the valve open;

figure 2 shows the profile of the circumferential surface of the cam;

figure 3 shows an axial section of a gas distribution system of an internal combustion engine containing a valve control device according to one embodiment of the present invention with a cam position corresponding to the open position of the valve;

figure 4 shows an axial section of a gas distribution system of an internal combustion engine containing a valve control device according to one embodiment of the present invention when switching between cam positions corresponding to open and closed valve positions;

5 shows an axial section of a gas distribution system of an internal combustion engine comprising a valve control device according to an embodiment of the present invention with a cam position corresponding to a closed valve position;

6 shows an axial section of a gas distribution system of an internal combustion engine comprising a valve control device according to one embodiment of the present invention when switching between cam positions corresponding to the closed and open valve positions.

The implementation of the invention

One embodiment of the valve control device of the present invention is described in detail below. However, it will be apparent to those skilled in the art that the present invention is not limited to the embodiment below, and may be changed without departing from the scope of the invention limited by the claims.

Figure 1 shows an axial section of a gas distribution system of an internal combustion engine comprising a valve control device in accordance with one embodiment of the present invention. The system comprises a housing 1, in which a channel 2 is provided for supplying the fuel mixture to the cylinder of an internal combustion engine. Figure 1 shows the initial position of the valve, in which the valve head 3 is shifted to the open position, and the channel 2 is open. The valve has a stem 4 and a thrust disk 5. The valve control device comprises a storage element 6 for storing energy, which in the present embodiment is a return spring and rests with one end on the housing 1 and the other end in the thrust disk 5. In the embodiment shown in FIG. 1 position, the return spring 6 is compressed under the influence of the rotary lever 7 on the thrust disk 5. The lever 7 contains a roller 9, which is pressed against the cam 11 by means of the return spring 6 acting through the thrust disk 5 on the rotary lever 7, the end of which is fixed to mpensatore 8, fixed in the housing 1. The compensator 8 used in this case in order to compensate for any gaps between the roller and the cam lever and the lever and the valve. The compensator 8 presses the pivot arm 7 against the thrust disk 5, while the force of the compensator 8 is much less than the force of the return spring 6. In the present embodiment, the cam is mounted on the shaft 10, which is rotatable by a drive (not shown). However, in other embodiments, the cam may be coupled to the actuator in any other suitable manner.

A rod 12 is placed on the other side of the cam 12. A thrust disk 13 is mounted on the rod 12, and another storage element 14, which in the present embodiment is also a spring, rests on one housing end 1 and the other on the thrust disk 13. The swing arm 15 is made so that one of its ends interacts with the thrust disk 13, and its other end is fixed in the compensator 16, mounted in the housing 1. The lever 15 contains a roller 17, which is pressed against the cam 11 by means of a spring 14 at a point diametrically opposite to the interaction point the cam 11 and the roller 9. The compensator 16 in this case is used to compensate for all the gaps between the lever roller and the cam, as well as the lever and valve.

Moreover, it is obvious to the specialist that the storage elements 6 and 14 can interact with the cam 11 in any other suitable way, for example directly, i.e. the storage elements 6 and 14 can be pressed directly to the cam 11. In other embodiments, the storage elements 6 and 14 for storing mechanical energy can be made in the form of magnetic springs or other suitable elements. In the present embodiment, the storage elements are arranged in parallel. In various embodiments, the storage elements may be coaxial or non-coaxial, as well as parallel or non-parallel.

Figure 2 shows the profile of the circumferential surface of the cam 11. The circumferential surface of the cam 11 has four zones. In the first zone, the radius Rmax of the cam 11 is maximum. In a second zone substantially diametrically opposed to the first zone, the radius Rmin of the cam 11 is minimal. Moreover, the centers of circles with radii Rmax and Rmin in the present embodiment coincide with the center of the shaft 10. Between the first zone and the second zone on the cam 11 are two transition zones in which the radius gradually decreases from Rmax to Rmin.

Figure 3 shows the position of the cam 11 corresponding to the open position of the valve in the gas distribution system of figure 1.

The roller 9 of the pivot arm 7 rests on the circumferential surface of the cam 11 in its first zone, which has a maximum radius Rmax. In this case, the center of the roller 9 is located at the maximum distance from the center of the shaft 10. The pivot arm 7 acts on the stop disc 5, as a result of which the stop disc 5 is shifted down together with the stem 4 and valve head 3 and the channel 2 for supplying the fuel mixture is open. In this position, the fuel mixture through the open channel 2 can enter the cylinder of the internal combustion engine. In this case, the valve return spring 6, resting on the housing 1, is compressed as much as possible and creates the greatest pressure on the thrust disk 5, which is applied to the cam 11 through the pivoting lever 7 and the roller 9. Since the pressure force of the roller 9 is applied to the circumferential surface of the cam 11 in the first zone , then the pressure force of the roller 9 on the cam 11 has a radial direction and passes through the center of the shaft 10. In this case, the force of the valve return spring 6 exerts pressure on the circumferential surface of the cam 11 in the radial direction through the stop disc 5, the pivot arm 7 and roller 9. The length of the compressed valve return spring 6 in this position of the valve control device is minimum, and the mechanical energy stored by spring 6 is maximum.

At a point that is substantially diametrically opposed to the contact point of the roller 9 and cam 11, in the second zone of the cam 11, which has a minimum radius Rmin, the cam 17 is supported by a roller 17 mounted on the pivot arm 15. The pivot arm 15 is mounted in the compensator 16 mounted in the housing 1. At the free end of the pivoting arm 15, a thrust disk 13 mounted on the rod 12 exerts pressure under the action of a compressed spring 14, which abuts against the stationary housing 1 with one end and abuts against the thrust disk 13 with the other end. Since the force is yes If the roller 17 is applied to the circumferential surface of the cam 11 in the second zone, then the pressure force of the roller 17 passes through the center of the shaft 10. The length of the compressed spring 14 in this position of the valve control device is maximum, and the mechanical energy stored by the spring 14 is minimal.

A device for controlling a valve operates as follows. When the cam 11 is rotated by the drive counterclockwise at a speed ω, as shown in FIG. 3, the roller 9 of the pivot arm 7 and the roller 17 of the pivot arm 15 begin to run around the circumferential surface of the cam 11. It should be noted that in other embodiments, the cam may rotate clockwise.

Figure 3 shows the operation phase of the valve control device, in which the cam 11 is in the equilibrium position (ω = 0) corresponding to the open position of the valve, and is held in this position by the actuator. In this case, the roller 9 interacts with the first zone of the cam 11, and the roller 17 interacts with the second zone of the cam 11. The pressure forces of the roller 9 and the roller 17 on the cam 11 pass through the center of the shaft 10. Next, the cam drive 11 is actuated for the initial rotation of the cam 11 from the equilibrium position corresponding to the open position of the valve, in the direction of the equilibrium position corresponding to the closed position of the valve.

Figure 4 shows the operation stage of the valve control device, in which the cam 11 moves from the equilibrium position corresponding to the open position of the valve to the equilibrium position corresponding to the closed position of the valve. After the initial rotation of the cam 11 by the drive, the drive is turned off, and the further rotation of the cam 11 is due to the energy stored by the spring 6. In this further rotation, counterclockwise in the present embodiment, the roller 9 begins to roll along the circumferential surface of the cam 11, which corresponds to the transition zone from Rmax to Rmin. When moving the roller 9 on the circumferential surface of the cam 11, from a point with a radius of the cam Rmax to points with a smaller radius, the length of the valve return spring 6 increases due to the energy stored by it, and its stored energy decreases accordingly. In this case, the rod 4 with the head 3 begin to move together with the thrust disk 5 in the direction of the housing 1, gradually closing the channel 2 for supplying the fuel mixture to the cylinder. The pressure force of the roller 9, created by the valve return spring 6 through the thrust disk 5 and the pivot arm 7, to the cam 11 in the transition zone from Rmax to Rmin does not pass through the center of the shaft 10, but is shifted towards the cam 11. The pressure force of the roller 9 on the cam 11, in addition to the radial force passing through the center of the shaft 10, creates a tangential force acting on the cam 11 and directed in the direction of rotation of the cam 11. The tangential force increases the speed of rotation of the cam 11. Part of the stored energy of the compressed valve return spring 6 when moving the roller 9 along the transition zone of the circumferential surface of the cam 11, on which the radius of the cam 11 decreases from Rmax to Rmin, is converted into the kinetic energy of rotation of the cam 11.

At the same time, the roller 17, pressed against the surface of the cam 11 by the spring 14 through the stop disc 13 and the pivot arm 15, moves along the surface of the cam 11 in the transition zone from Rmin to Rmax. In this case, the spring 14 is compressed, and its potential energy increases. The pressure force of the roller 17 on the cam 11 also creates a tangential force, but in this case, this force is directed against the direction of rotation of the cam 11 and reduces the speed of rotation of the cam 11. Thus, the kinetic energy of rotation of the cam 11 partially transfers into the potential energy of the compressed spring 14.

Since the processes of expanding the valve return spring 6 and compressing the spring 14 occur simultaneously, when the cam 11 is rotated from the open position shown in Fig. 1, counterclockwise, the potential energy of the return spring 6, decreasing when the spring 6 is stretched, is partially converted to the potential energy of the spring 14, which is compressed.

Further, when the stored energy of the spring 6 is exhausted, the cam drive 11 is actuated to further rotate the cam 11 to an equilibrium position that corresponds to the closed valve position shown in FIG. 5. In this case, the roller 17 continues to roll along the circumferential surface of the cam 11 in the direction of increasing its radius from Rmin to Rmax, and the lever 15, turning, presses the thrust disk 13, displacing the rod 12 and compressing the spring 14. The potential energy of the spring 14 increases. In turn, the spring 14 through the thrust disk 13, the pivot arm 15 and the roller 17 creates a braking force on the cam 11 and the shaft 10, reducing their kinetic energy. That is, the kinetic energy of the cam 11 partially transfers into the potential energy of the spring 14, which thus stores energy. The potential energy of the spring 14 will increase when the cam 11 is rotated counterclockwise until the radius of the cam 11 increases at the point of contact of the roller 17.

As a result, the cam drive 11 drives the cam 11 to the equilibrium position corresponding to the closed valve position shown in FIG. 5. In this position, the valve stem 4 with the valve head 3 is shifted to the position closest to the center of the cam 11, and the valve head 3 is adjacent to the housing 1 and closes the channel 2 for supplying the fuel mixture. The spring 14 in this case has a minimum length, and the potential energy stored by the spring 14 is maximum. The length of the return spring 6 of the valve is maximum, and its potential energy is minimal.

In the equilibrium position of the cam 11 corresponding to the closed position of the valve, the cam drive 11 stops turning the cam and holds it in the indicated position.

Next, the cam drive 11 is actuated to initially rotate the cam 11 from the equilibrium position corresponding to the closed position of the valve, in the direction of the equilibrium position corresponding to the open position of the valve.

Figure 6 shows a device for controlling a valve during the transition of the cam 11 from the equilibrium position corresponding to the closed position of the valve to the equilibrium position corresponding to the open position of the valve. After the initial rotation of the cam 11, the drive is turned off and the further cam 11 is driven by the energy stored by the spring 14. With this rotation, the roller 17 starts rolling along the transition zone of the circumferential surface of the cam 11, in which the radius of the cam 11 decreases from Rmax to Rmin. The distance from the center of the roller 17 to the center of the shaft 10 begins to decrease. The spring 14 through the rod 12 with the thrust disk 13, the pivot arm 15 and the roller 17 create pressure on the circumferential surface of the cam 11. In the transition zone of decreasing the radius of the cam 11 from Rmax to Rmin, the pressure force of the roller 17 on the cam 11 has a tangential component that is directed to the side rotation of the cam 11 and increases the speed of rotation. As the cam 11 rotates, the length of the spring 14 increases, and the potential energy of the spring 14 decreases, partially transforming into the kinetic energy of rotation of the cam 11.

As the radius of the cam 11 increases at the point of contact of the roller 9 and cam 11, the swing arm 7 exerts pressure on the return spring 6 through the thrust disc 5, compressing it. As the return spring 6 is compressed, the kinetic energy of the cam 11 rotation is partially converted to the potential energy of the spring 6. When the spring 6 is compressed, the thrust disk 5 together with the stem 4 and valve head 3 are shifted down and gradually open the channel 2 for supplying the fuel mixture. The fuel mixture supply channel 2 is fully open when the contact point of the roller 9 and cam 11 has passed the entire transition zone in which the radius of the cam 11 increases from Rmin to Rmax.

Further, when the stored energy of the spring 14 is exhausted, the cam drive 11 is actuated to further rotate the cam 11 to an equilibrium position that corresponds to the open position of the valve shown in FIG. 3. In this position, the length of the return spring 6 will be minimum, and its potential energy will be maximum.

As a result, the cam drive 11 drives the cam 11 to the equilibrium position corresponding to the closed position of the valve, and holds the cam 11 in this position. The position of the valve control device in this case corresponds to the position shown in FIG. With further rotation of the cam 11, the steps of the valve control device described above are repeated.

As can be seen from the description of the operation of the valve control device, energy is exchanged between the valve return spring 6 and the spring 14 as the shaft rotates. Thus, the energy is stored alternately by springs 6 and 14, which in the present embodiment serve as storage elements for storing mechanical energy.

As noted above, in the closest analogue of the present invention, all the movable elements of the gas distribution system, including the anchors of the electromagnets, perform reciprocating movements. Thus, the energy of the power source, which is spent on increasing the kinetic energy of the armature of the electromagnets each time the valve is switched, is converted into heat and is irreversibly lost.

Due to the design of the valve control device of the present invention, each time the valve is switched, it is sufficient for the cam drive 11 to “shift” the cam 11 from the initial equilibrium position and “bring” the cam 11 to the final equilibrium position, with the intermediate cam moving due to the energy stored in the storage elements for storing mechanical energy. This design of the device for controlling the valve allows to increase the efficiency devices due to the conservation of kinetic energy in the system, which in known devices is converted into losses.

In one embodiment, an apparatus for controlling a valve of a gas distribution system of an internal combustion engine may comprise more than two storage elements for storing mechanical energy. Moreover, when at least one of these storage elements will store mechanical energy coming from the cam, at least one of the remaining storage elements will transmit mechanical energy to the cam.

In one embodiment, when the internal combustion engine is off, the position of the cam 11 corresponds to the intermediate position shown, for example, in FIG. 4. When starting the internal combustion engine, the cam drive 11 begins to alternately rotate the cam 11 from its initial position clockwise and counterclockwise with a gradually increasing rotation angle until the cam 11 reaches the working equilibrium position corresponding to the open, and in some cases implementation of the closed position of the valve. This is done to reduce energy costs for bringing the cam from the initial position to the working equilibrium position. This decrease is due to the fact that during alternate movements clockwise and counterclockwise with a gradually increasing angle of rotation, the movement occurs not only due to the cam drive, but also due to storage elements for storing mechanical energy.

Although the present invention has been described by way of example of a specific embodiment, various changes and modifications are possible within the scope of the present invention defined by the claims.

Claims (11)

1. A device for controlling a valve of a gas distribution system of an internal combustion engine, comprising
a cam configured to interact with the valve stem, such that opening and closing of the valve is provided when the cam is rotated,
a drive configured to provide cam rotation,
characterized in that it contains
two storage elements for storing mechanical energy, configured to receive energy from the cam and transmit energy to the cam in such a way that when one of the storage elements stores mechanical energy, the other storage element transfers mechanical energy to the cam. 2. The device according to claim 1, in which the storage elements are springs or magnetic springs. 3. The device according to claim 1, in which the circumferential surface of the cam contains at least one portion located at a constant distance from the axis of rotation of the cam. 4. The device according to claim 1, in which one of the storage elements is connected to the valve stem. 5. The device according to claim 2, in which the springs or magnetic springs are aligned. 6. The device according to claim 1, in which the storage elements interact with the cam via levers. 7. A method of controlling a valve of a gas distribution system of an internal combustion engine, including
actuating the actuator to rotate the cam to the first equilibrium position corresponding to the first extreme position of the valve, while simultaneously storing energy with the first storage element for storing mechanical energy,
stopping the actuator when the cam reaches the first equilibrium position while holding the cam in this position, actuating the actuator to rotate the cam from the first equilibrium position in the direction of the second equilibrium position corresponding to the second extreme position of the valve,
drive shutdown
further rotation of the cam due to the energy stored by the first storage element, in the direction of the second equilibrium position, while simultaneously storing energy by the second storage element for storing mechanical energy,
actuating the drive to rotate the cam to a second equilibrium position while simultaneously storing energy with a second storage element for storing mechanical energy,
the drive stops when the cam reaches the second equilibrium position while holding the cam in this position. 8. The method according to claim 7, further comprising
actuating the drive for the initial rotation of the cam from the second equilibrium position towards the first equilibrium position,
drive shutdown
further rotation of the cam due to the energy stored by the second storage element, in the direction of the first equilibrium position, while simultaneously storing energy by the second storage element for storing mechanical energy,
actuating the drive to rotate the cam to the first equilibrium position while simultaneously storing energy with the first storage element,
the drive stops when the cam reaches the first equilibrium position while holding the cam in this position. 9. The method according to claim 7 or 8, in which the first extreme position of the valve corresponds to the open position of the valve, and the second extreme position of the valve corresponds to the closed position of the valve. 10. The method according to claim 7 or 8, in which the first extreme position of the valve corresponds to the closed position of the valve, and the second extreme position of the valve corresponds to the open position of the valve. 11. The method according to claim 7, in which when starting the engine, actuating the drive to rotate the cam to the first equilibrium position includes alternating rotations of the cam by the actuator from the initial position clockwise and counterclockwise with an increasing angle of rotation.

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