FI123116B - The control valve - Google Patents

Description

The control valve

FIELD OF THE INVENTION The invention relates to a control valve for controlling a pressurized medium to an actuator according to the preamble of claim 1, which actuator is arranged to dampen vibrations of the associated process device.

Background of the Invention

Vibrations and vibrations in paper machines and paper finishing equipment are quite a significant problem. These devices have a plurality of sources of vibration, and some of the most prominent are rollers and cylinders, which comprise a large mass rotating at considerable speed. The vibrations and vibrations of the rollers and cylinders cause marks on the paper being manufactured.

Vibrations and vibrations in the multi-roll calenders used in paper finishing produce so-called "vibrations". barring phenomenon. It can occur for many reasons. It may be caused by irregularities in the paper to be calendered, mechanical vibration generated by the calender itself, its actuators or surrounding machines, or by the asymmetry of the outer surface of the calender rolls. 25 Because all calender rollers are in contact with each other, the vibration moves from one roll to another and eventually the rolls repeat a vibration pattern with multiple ™ waves. The rolls cause the calendering paper to have MD thickness 9 variations, whereby paper quality objectives are generally not achieved.

In addition, the rollers cause extra vibration to the calender and noise.

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The moving and rotating parts of the paper machine and paper finishing equipment also cause vibrations in the foundations of these machines. These oscillations adversely affect the driving situation and may cause permanent changes in the support S. In addition, vibrations caused by different machine parts / devices located on the same base cause the vibrations to interact, resulting in periodic or chaotic vibration behavior of the whole machine.

Various solutions have been proposed for eliminating and reducing vibrations in paper machines and 5 paper finishing devices. Fl patent 110713 discloses a damping device for damping a vibration of a pair of tracks in nip contact. The damper is mounted between the roller bearing housings or between the roller bearing housings and the machine frame. The damping device has two mutually interlocking coupling members, of which at least one of the side surfaces of the at least one coupling member is exerted by a hydraulic actuator to force the coupling members against each other.

Fl patent 85166 discloses a solution for damping the vibrations of a roll of a nip forming roll, wherein the rolls are supported by a hydraulic roller damper. The damping device has a piston-cylinder device to which a hydraulic pressure medium is supplied and discharged. The rollers of the pair of rollers provide mutual movement of the piston cylinder device and flow of pressure medium. The damping of the vibrations is accomplished by amplifying said pressure medium flow and choking the resultant amplified flow.

EP 819638 discloses a solution for damping the vibrations of a press roll roller. In the solution, a pressure cylinder is fitted to the bearing housing, the thrust lines of which have a throttle to suppress the movement of the cylinder. The pressure cylinder may be a pressure roller loading cylinder which is suitably throttled.

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CT) 9 Mineral materials processing equipment such as crushers, screens, sieves and conveyors also exhibit a wide range of vibrations due to the operation of these machines. For example, the

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feeding material into the crusher will cause shocks and vibrations to the entire S crusher. Vibrations and vibrations of mineral material processing equipment are now suppressed by springs and large hydraulic cylinders.

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The problem with all of the above-mentioned vibration damping solutions is the long response time of the hydraulic actuators used therein to the observed vibrations. Because the vibration dampener does not react quickly enough to vibrations, vibrations cause problems in the equipment and manufacturing process before the situation is corrected. There may also be a situation where the vibration dampener is constantly '' late '' due to its long response time. In this case, despite continuous actuator control, the damping is never achieved at a sufficient level. The reason for the long response times of actuators is eg. the structure of the actuator and the resulting operational delays, but the major factor is the slow response times of the devices controlling the pressurized medium to the actuators.

The pressurized medium may be directed to the actuators by various means, most of which various valves are used. Fig. 1 is a cross-sectional view of a valve which can be connected to actuators according to the preceding examples, for controlling the actuating medium for actuating them.

The control valve has a magnet 1, which is surrounded by a valve body 2. One side of the magnet is connected to the valve cover 3. A coil 4 is arranged around the magnet core 1a, which is supplied with electric current through a conductor 5 to form a magnetic field. A bore 6 is concentricly formed through the valve cover 3 and the magnet core 1a for a valve adjusting member, g, spindle 7 which moves in its longitudinal direction. The valve spindle 7 is provided with a suitable shoulder system 8, whereby at various positions of the spindle the fluid flow is directed between the inflow channel 9 and the outflow channel 10. The magnet 1 is partially in contact with the linear actuator, i.e. the voice coil 11. The voice coil 11 formed 30 of the body 11a and the winding 11b wrapped around it. Wires 12 are connected to the voice coil for carrying an electric current through the coil of the voice coil. A conical connecting member 13 of rigid structure connects

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§ The spool 11 and the spindle 7. The connecting member 13 is connected at its larger diameter end to the spool 11 and the smaller diameter end to the valve spindle 7.

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The valve spindle 7 is moved back and forth in the desired direction in the bore 6, whereby the shoulder assemblies 8 in the spindle are positioned in the respective movement relative to the valve inlet channel 9 and outflow channel 10, thereby allowing pressurized fluid to flow in and out of the valve. The movement of the spindle 7 is accomplished by applying an electric current to the coil of the voice coil 11 which causes the voice coil 11 to move linearly. The connecting member 13 moves in accordance with the motion of the voice coil while moving the valve spindle 7. The operation and movement of the voice coil in the magnetic field is well known to those skilled in the art and is not further described herein.

The valve described above is functional in itself but has some significant drawbacks. The valve in question, as noted above, is of a complex construction. This makes it difficult to choose from. This increases the cost of manufacturing the valve and makes it an expensive component for the user. Because of the complex structure, servicing and replacing the valve once it is broken is difficult, if not impossible.

20 The valve has a slow response, ie the valve stem responds slowly to control commands. This is because the valve stem is heavy, which slows its movement. This also slows the flow of pressurized medium from the valve outlet port. Only when the spindle has moved to the correct position can the medium flow be brought into compliance with the control command, which can take several milliseconds at worst. The valve's slow step response ^ causes the actuator to run slowly.

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BRIEF DESCRIPTION OF THE INVENTION 1 ^

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The object of the present invention is thus to provide

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a valve for directing the pressurized medium to the actuator, which avoids the above problems and enables the actuator to be positioned more quickly and accurately.

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To accomplish this purpose, the control valve according to the invention is essentially characterized in what is set forth in the characterizing part of independent claim 1.

Other dependent claims disclose some preferred embodiments of the invention.

The invention is based on the idea that a control valve is used to supply the pressurized fluid to the actuator, wherein a coil is arranged around the control device for controlling the volume flow of the pressurized medium in order to move the control member in a magnetic field. Ts. the adjusting member is directly connected to its moving element.

The adjusting member is formed at least partially internally into a hollow cylindrical body 15. The valve has at least one outflow chamber for the pressurized medium. The medium flows into the outflow chamber either from the flow chamber or from the duct through the flow guide. The adjusting member is positioned relative to the flow guide so that it is capable of controlling the volume flow rate of the medium passing through the flow guide. The coil arranged on the outer surface of the adjusting member 20 is surrounded by a pressurized medium.

The valve has a magnet, in which a magnetic field is formed by the electric current supplied. The magnet used in the valve is shaped and the coil arranged on the outer surface of the actuator member is disposed relative to the magnet so that the magnetic flux density is highest around the actuator ™ coil. This causes the movements of the adjusting member 9 to be fast and precise and the positioning of the adjusting member in the correct position c \ i is easy and fast, g 30 Q_

The magnet can be either a permanent magnet or an electromagnet. The electromagnet can be supplied with either direct current or alternating current.

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In order to move the actuator in a magnetic field, an electric current is applied to the winding arranged around the actuator 35. Alternating current is supplied to the coils, whereby the direction of movement of the actuator relative to the flow controller can be controlled in both directions.

If desired, at least one spring can be attached to the adjusting member, which 5 holds the adjusting member in place when not guided. More than one piece of springs is connected to the adjusting member and are disposed symmetrically about it with respect to the adjusting member. The spring can also be used as a support structure for the electric conductors of the coils formed around the regulating member, thereby improving the durability of the conductors.

The stiffness of the spring can influence the speed of the valve's step response. If a fast step response is required, a loose spring with a low specific oscillation frequency is selected. For a slower step response, a rigid spring with a high specific oscillation frequency is selected. The need for rigid spring power in steering is less than that of a loose spring. The appropriate spring for each application can be calculated by amplitude resonance as follows: 20 f = {π J— m V m 2 m 2 (1) where f = frequency 25 k = spring constant m = total mass of spindle and spring ^ B = damping factor

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c \ j The spring is not necessary for the operation of the control valve. However, the force exerted by the spring g 30 is significantly less than that caused by the voice coil

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force.

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m § The pressurized medium controlled by the control valve may be a liquid or ° gaseous medium. It is advantageous to apply 35 feedback to the valve control, but the actuator connected to the valve can also be controlled proportionally without feedback.

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The number of outflow channels may vary depending on the application and may be from 1 to 20 pieces. Preferably there are 2 to 5 of them.

A single valve according to an embodiment of the invention functions as a 2/2 valve having two connection openings and two spindle positions. According to another embodiment, a single valve may also be formed to conform to a 4/2 valve. The valves can also be connected to each other to provide a variety of operating options.

The combination of the actuator and the element moving it brings with it numerous advantages.

15 The valve no longer needs a separate, heavy spindle, which means that the entire valve is smaller in size and lighter in weight, making it easier to install with actuators. Of course, the regulating member itself is also lighter, which makes it faster to move and thereby also to control the flow of the medium. In practical experiments, the response time of the actuator has been measured up to 0.1 ms / response times. In addition, it has been found that increasing the flow from zero to full flow or closing it from full flow can be achieved up to about 1 ms. As a result, the actuator is quickly positioned to the desired operating mode.

Due to its simpler design, the valve is also cheaper than the valves available on the market today, which are able to perform almost the same function.

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g 30 The valve is designed to be easy to maintain and to replace wear parts. Internal valve calibration can be easily performed using a pressure sensor.

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o ° Especially in terms of damping vibrations, there is a great advantage in accelerating the step response of the actuator. In addition, non-sinusoidal wave can be achieved by the valve.

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Description of the Figures Ivhvt

In the following, the invention will be described in more detail with reference to the accompanying drawings, in which: Fig. 1 is a cross-sectional view of a prior art valve, Fig. 2 is a cross-sectional view of an adjusting valve according to the invention; 3c shows a hydraulic connection diagram of a set of valves in which 20 two valves are connected to each other, Fig. 3d illustrates actuator control by two sets of valves, Fig. 4 illustrates another control valve according to the invention, and Fig. 25 illustrates a paper finishing treatment, ™ is attenuated by a separate actuator.

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Detailed Description of the Invention g 30

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As used herein, the term process equipment refers to papermaking or post-processing equipment, equipment for processing mineral materials or parts, components, subassemblies, and foundations therein.

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Figure 2 shows an embodiment of the invention 2/2 as a valve. The control valve 14 shown in the figure comprises a valve body 15 which is formed internally to accommodate valve parts within the body 15. The body may be formed of a single housing-like body 15a forming a base and side walls 5 and a lid portion 15b attached thereto, as made in the embodiment of Figure 2. The valve body may also consist of separate base and cover portions and associated side walls. The valve can also be manufactured without the cover if desired. The valve is secured to the actuator 23 by a fastening member 32 such that the valve cover 15b is in contact with the actuator 23.

A magnet 16 is inserted inside the housing, which is preferably an electromagnet, but a permanent magnet can also be used. The magnet coil 17 is wound around the magnet core 16a. An electrical current is applied to the coil 17 of the magnet 15 through a conductor 18 to generate a magnetic field.

The magnet 16 is at least partially in contact with the adjusting member 19, which is internally formed as a hollow cylindrical body. A winding 20 is arranged around the adjusting member 20 19. Electric current is conducted to and from the winding 20 via conductors 21a, 21b. The volume flow rate of the medium supplied by the valve 14 to the actuator is controlled by adjusting the amount and direction of the control current supplied to the coil 20.

An outflow chamber 22, g, which is separated from the inflow chamber 28 by a cylindrical wall 27, is provided as an extension of the magnet core 16a. The adjusting member 19 is arranged around the wall 27 of the magnet core 17a and 9 so that it extends over the entire length of the wall 27 and a portion of the distance to the core 30a of the magnet. From this portion, the inner surface of the mandrel is in contact with the magnet

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on the outer surface of the heart 16a, o

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m § The receiving member 19 thus delimits the valve outflow chamber 22 with its walls. Correspondingly, outside the valve inflow chamber 35, the winding winding of the regulating member 19 is thus located inside the inflow chamber 28, surrounded by the medium contained therein.

At the valve cover end 5 of the outlet chamber wall 27, a flow guide 25 is provided which controls the flow of fluid from the inlet chamber 28 to the outflow chamber 22 when the control member 19 is moved to a position where it does not obstruct flow. In the embodiment of Figure 2, the flow guide 25 is formed by holes 25a provided in the wall of the outflow chamber.

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2, the other end of the actuator 19 is in contact with a damping plate 24 attached to the valve cover 15b, thereby obscuring the holes 25a of the flow guide 25 and preventing the fluid from flowing from the flow chamber 28 to the flow chamber 22 and therethrough.

The valve body 15a, the cover 15b, the magnet 16 and the valve stem 19 define the valve inlet chamber 28 to which an inlet 20 conduit 29 is provided to guide the pressure medium into the inlet chamber 28.

As can be seen from the figure, the magnet 3 is shaped to form a magnetic gap 30. The magnetic gap 30 is narrow in shape. This design provides an effective magnet with a steady-state magnetic flux of 25. The length of the adjusting member 19 and the location of the coil 20 relative to the length of the adjusting member are arranged such that the coil ™ 20 is substantially disposed within the magnetic slot 30, so that the movements of the adjusting member 19 are quick and precise.

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Two springs 31 are fixed symmetrically around the adjusting member 19 so that the first end of the spring is fixed to the adjusting member 19. The other end of the springs is fixed to the wall of the inflow chamber 28.

§ The springs press the adjusting member 19 against the damping plate when no control is applied to the adjusting member. The spring can also be used as a support structure for the winding conductors 21a and 21b for 35 min 20, making the conductors more durable.

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The control valve of Figure 2 operates as follows:

By means of an electric current applied through the conductor 18 to the coil 17 of the magnet, a magnetic field is generated by the magnet 16. Valve 5 is continuously supplied with pressurized fluid through the inlet port 29 to the inlet chamber 28. When no control is applied to the valve, i.e., no current is applied to the coil 20 arranged around the actuator 19, the spring 31 presses the actuator 19 against the damping plate 23. The actuator then obscures the holes 25a in the flow guide 25 and blocks the outflow from the

When a control current is introduced into the windings 20 arranged around the actuator, the actuator 19 is moved away from the damping plate 15 to a fluid flow path through the holes 25a towards the damping plate. The springs 31 enhance these 20 movements.

The coil wound around the adjusting member may be formed, for example, by wrapping a litz wire or aluminum foil around the valve stem. Preferably, a litz yarn which is a very strong winding material is used. By using it, higher control frequencies can be used, and yet the losses are smaller. Other conductive materials, single or multiple ™ filament wires, may also be used as winding material.

σ> o i c5 Fig. 3a shows one alternative for connecting the control valve of Fig. 2 to the actuator. The actuator in question is further coupled to a process device (not shown) to attenuate its vibrations. The connection shown is so-called. 2/2 connection. The control valve section 14 is connected to the actuator 23 which in this embodiment is a motor. The actuator may also be a pump or a hydraulic cylinder which acts as a vibration dampener. Valve 14 is connected via line 34 to control unit 33 which controls the amount and direction of electric current to be supplied to the coil 12 arranged around the valve control member. This causes the desired movement of the actuator and the volume flow of the pressure medium through line 35 to the motor 23. The motor outlet provides feedback to the actuator. To this end, a measuring sensor 36 for measuring fluid flow, pressure, velocity or acceleration is provided at the outlet of motor 23, from which the measurement result is led via line 37 to the control unit 33.

Figure 3b shows another alternative for controlling the valve 10 shown in Figure 2 to actuator. The connection shown is so-called.

2/2 leakage flow connection. The control valve 14 is connected via line 34 to the control unit 33 which controls the movements of the valve control member as described above and provides the desired fluid flow through line 38 to the actuator 23. In this example, the actuator 23 is a hydraulic cylinder 15. A choke 40 is provided at the leakage connection 39 to control the leakage flow. The actuator output is fed back to the control unit. For this purpose, a measuring sensor 41 is provided in connection with the hydraulic cylinder 23, which may be a linear sensor or a force sensor, from which the measurement result is led via line 37 to the control unit 33.

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Figure 3c shows a set of valves in which two control valves 14 are connected together. The connection method shown is so-called. A 3/2 circuit with a second control valve controls the pressure medium flow inlet P and a second control valve controls the pressure medium flow 25 exiting the valve assembly. The 3/2 circuit is known to those skilled in the art and is not further explained herein. Both valves 14 are connected via line 34 to a control unit 33 which controls the movements of the control elements of each of the control valves as described above and provides the desired fluid flow through line 38 to the actuator 23. g 30 In this example, the actuator 23 is a hydraulic cylinder. The output from the unit is the feedback to the control unit. For this purpose, a measuring sensor 41 is provided in connection with the spindle of the hydraulic cylinder 23, which may be a linear sensor or a force sensor, from which the measurement result ° is led via line 37 to the control unit 33.

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Fig. 3d shows a connection in which four control valves 14 are connected to each other in a so-called. 4/3 to connect. This type of coupling is also known to those skilled in the art and is therefore not further explained herein. All control valves 14 are connected via lines 34 to control unit 5 which controls the movements of control elements 19 of each valve as described above. The control valves 14 are coupled in pairs so that the two control valves 14 are connected together. One pair A directs the pressure medium via line 42 to the piston side chamber of the actuator 23, i.e. the hydraulic cylinder, and the other pair B directs the pressure medium 10 through line 43 to the piston side chamber of the hydraulic cylinder. The actuator output is fed back to the control unit. For this purpose, a measuring sensor 41 is provided in connection with the spindle of the hydraulic cylinder 23, from which the measurement result is conveyed via line 37 to the control unit 33.

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Only a few examples of valve switching possibilities are given above. Other connections, for example 4/2 or 5/2 connections, may also be implemented.

The connections described in connection with Figures 3a and 3b may also be implemented without a control unit and a feedback loop derived therefrom. If several valves are connected together, the control unit is necessary for the valves to be controlled synchronously in the desired manner, for example in the 3/2, 4/2 or 5/2 style. The control unit can also be used to provide valve / valves control as desired, for example, proportionally, servotype or on / off.

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Figure 4 shows an embodiment of the invention 4/2 as a valve. The control valve 14 shown in Fig. CG has a valve body 15. A magnet 16 is disposed within the body, surrounded by a magnet coil 17. An electric current is applied to the magnet via conductor 18. The magnet is at least partially in contact with an adjusting member 19 arranged around a coil 20. For the electric current required by the coil, conductors 21a and 21b are connected thereto. The volume flow rate of the medium supplied to the actuator of valve 14 is controlled by adjusting steering current regulator direction.

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To supply the pressure medium to the valve 14, it is provided with a lead-through for the flow passage 29. It extends uniformly through the entire valve and is divided by a stopper 46 into an inlet conduit 29a, and an outflow conduit 29b. The inflow channel 29a is partially surrounded by a magnet 16. The outflow channel 29b is surrounded by a body.

Separated from the flow passage 29, the valve 14 is provided with two outflow chambers 22a and 22b. An inlet duct 29a is provided with a lead-through 44 for introducing fluid into the first outflow chamber 22a. An outlet 45 is provided from the outflow channel 29b for introducing the medium into the second outflow chamber 22b. The bushings act as flow controllers for the valve.

The adjusting member 19 is arranged to move in the outflow chambers 22a and 22b. The length of the adjusting member 19 is selected so as to extend from the first outflow chamber 22a to the second outflow chamber 22b, a portion of its length being in contact with the surface of the magnet 16. The regulating member 19 is mounted so that it surrounds the flow passage 29. The winding 20 coiled on the surface of the regulating member 19 is contained within the second outflow chamber 22a, surrounded by the medium contained therein.

The inner surface of the adjusting member 19 is provided with grooves 47 which guide the medium from the inlet conduit 29a and / or the outflow conduit 29b 25 to the outflow chambers 22a and 22b. The medium flow is controlled by moving ^ tamalla adjustment member as indicated by the arrow 19 in Fig. In the situation shown in Fig. ™, the control member 19 is in a position such that medium 9 through the flow guides 44 and 45 does not flow out into the chambers 22a and 22b. When the control member 19 is moved £ 30 in either direction, the medium can flow through the passageway 44 and one of the grooves 47 from the inlet conduit 29a to the first outflow chamber 22a. Correspondingly, the flow of medium § is passed through the passage 45 and the groove 47 from the outflow channel 29b to the second outflow chamber 22b. The adjusting member may also be moved to a position 35 such that the medium can simultaneously flow through both flow guides 44 and 45 to the outflow chambers 22a and 22b.

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The outflow chambers 22a and 22b are connected to the outflow channels 26a and 26b for the actuator. The valve is also provided with springs 31 which enhance the movement of the actuator.

Fig. 5 shows a multi-roll calender 50 whose vibrations are dampened by one or more actuators using a valve according to the invention. The multi-roll calender has a body 51 supported on a calender base 52. The calender rolls 53, the number of which may be varied, are superimposed so that successive rolls are in contact with nip-10. The web W is introduced into the calender and guided through guide rollers 54 from below upwards so that it passes through each nip.

The figure schematically shows three actuators 55, 56 and 57. The actuators can be any actuator to which a pressurized medium is controlled by a valve. The actuator 55 is arranged to dampen the vibrations occurring in the calender base 52 and the actuator 56 is arranged to dampen the vibrations occurring in the calender body 52. The actuator 57 is arranged in connection with a lightening arm 58 arranged on a single calender roller 53 to dampen the vibrations therein.

The invention is not intended to be limited to the exemplary embodiments set forth above, but is intended to be extensively applied within the scope of the inventive idea defined in the claims defined below. The control valve can be used to control a variety of media. Both liquids, gases and liquid-gas mixtures O) 9 are suitable for control. The control valve can thus be used to direct ci medium to both hydraulic and pneumatic actuators, ϊ 30 ο- οο o c \ j

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Claims (13)

A control valve for directing pressure medium to a control means (23), which control means (23) is arranged to attenuate vibrations of a process device coupled to the same, the control valve comprising: - a body (15), - a magnet (16) for generating a magnetic field, - an inlet channel (29a) for flowing the medium, - a first outlet channel (26a) for flowing the medium, a second outlet channel (29b) for flowing the medium, - a current control unit (44) for controlling the flow of the medium, and - a regulator (19) which is cylindrical and arranged to be surrounded by a coil (20) for moving the regulator in the magnetic field of the magnet and which is movable relative to the current controller 15 (44), for controlling the volume flow of the the medium flowing through the current control unit, characterized in that: - the control valve also comprises an outlet chamber (22a) which starts in communication with the first outlet channel (26a), 20. the control device (19) is arranged to move in output the upstream chamber (22a), - the current control unit (44) is arranged to control the flow of the medium from the inlet channel (29a) to the outlet chamber (22a), - the magnet comprises a core and a magnetic gap (30), and further the core of the magnet is arranged surrounding the inlet duct 5 (29a), ™ inlet duct (29a), the second outlet duct (29b) and the 9 actuator (19) are arranged concentric so that the actuator c \ l (19) surrounds the inlet duct (29a) and the second outlet duct £ 30 ( 29b) which constitute an extension to each other, the CL controller (19) is installed in a manner relative to the magnetic gap ° (30) that the coil (20) of the controller is placed at least partially in § the magnetic gap (30) and to surround the core of the magnet. o C \ J Control valve according to claim 1, characterized in that the control coil (20) is at least one conductor (21a, 21b) connected to supply current to the coil (20), and that the control device is arranged to move in the magnetic field produced by the magnet ( 16) under the influence of the electric current supplied to the coil (20). Control valve according to claim 1, characterized in that the control valve also comprises a second flow control unit (45) for conducting medium from the second outlet channel (29b) to the second outlet chamber (22b). Control valve according to claim 3, characterized in that at least one passage (44) is arranged in the wall of the inlet passage (29a), and at least one passage (45) is arranged in the wall of the second outlet passage (29b). Control valve according to claim 3 or 4, characterized in that the length of the control device (19) is selected to extend into the first and second outlet chambers (22a, 22b). Control valve according to any of claims 3-5, characterized in that the control device is positioned relative to the first and second outlet chambers (22a, 22b) that the coil (20) arranged in the control device (19) is in an outlet chamber (22a, 22b). Control valve according to any of claims 3-6, characterized in that the inner surface of the control means (19) is provided with at least one spar (47) for passing the medium flowing through the flow control unit (44, 45) to the outlet chamber (22a). , 22b). C \ J Control valve according to claim 1 or 6, characterized in that the coil c1 (20) is surrounded by the medium. I 30 Control valve according to claim 2 or 3, characterized in that the ° regulator (19) is arranged to move also relative to the second section of the current control unit (45), to control the volume flow of the medium which ° flows through the current control unit (44, 45). 35 Control valve according to claim, characterized in that the control valve comprises at least one spring (31). Control valve according to claim 1, characterized in that the magnet 5 (16) is provided with a magnetic coil (17), and in conjunction with the coil there is a conductor (18) for supplying electric current to the magnetic coil (17). 12. A regulating valve according to claim, characterized in that the processing device is one of the following: a device for making or finishing paper, a device for processing mineral materials, or a part of the above-mentioned devices. Control valve according to claim 1, characterized in that the medium is a liquid or a gas. 15 C \ J δ CvJ σ> cp CvJ X X Q. CO o CvJ m CD o o CvJ