Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
  • F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
  • F15B9/08—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor
  • F15B9/12—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor in which both the controlling element and the servomotor control the same member influencing a fluid passage and are connected to that member by means of a differential gearing

Definitions

• the present invention relates to a fluid-operated actuator to a valve, in particular a shut-off, safety or control valve.
• valve actuators are known and in use.
• these are in particular also fluid-operated valve actuators (see, for example, EP 0665381 Bl, EP 1418343 Bl, EP 1593893 Bl and EP 2101061 AI).
• fluid actuated valve actuators include a linear actuator whose slide is directly or indirectly coupled to the input of the valve, and a fluidic control base unit.
• the latter typically comprises an electro-fluidic signal converter, which in particular may be upstream of the fluidic control and cooperate therewith and have a proportional output behavior.
• an external electrical control unit is typically connected to a signal input connected to or associated with the electro-fluidic signal converter and may include input means, a setpoint input, control electronics, a communication unit, a signal output and / or a signal generator. In the sense of a closed control loop, the actual value signal of a sensor assigned to the fitting is fed back to the electrical control unit.
• EP 884481 A2 discloses a pneumatic positioner for a pneumatic actuator whose manipulated variable is readjusted to an adjustable setpoint value, in particular
• CONFIRMATION COPY in particular for the positioning of diaphragm- and piston-operated control valves proportional to a pneumatic input signal.
• the positioner to prevent pressure losses provided with three main components, namely a comparator, which compares the manipulated variable with the setpoint size and outputs a differential amount, a first valve, which is in the flow path from a pneumatic pressure source to the actuator, is closed in the idle state and is controllable by the difference size, and a second valve, which lies in the flow path from a discharge opening of the actuator to a pressure sink, is closed in the idle state and can be controlled by the difference in size.
• the control loop of the positioner includes a pneumatic actuator with an actuator in the form of an actuating rod, which couples the manipulated variable to the flow of the valve, slide or the like determining element.
• the actuator has a pressurized diaphragm to which the actuator is connected.
• the lifting movement of the actuating element is fed via a gear, preferably a cam gear with interchangeable cams, the one end of a compression spring, the other end of the one arm of a two-armed lever loaded, which is pivotally mounted in its center.
• a pressure / force transducer with a diaphragm loaded by a setpoint pressure will push on the same lever arm as the compression spring, but in the opposite direction.
• the force exerted by the compression spring on the lever arm force is compared in the capture range of the control loop with the force exerted on the membrane, opposite force by adjusting a balance between these forces.
• Pressure / force converter thus forms a setpoint / actual value comparator with the compression spring.
• this comparator forms the compression spring with her vorgebagerten cam gear a path / force converter, which converts the stroke of the actuating element into the actual value force.
• DE 3819122 C2 discloses a method for controlling the position of control valves with fluid or electric motor operated, controlled actuators, in which the deviations between the actual and the ideal assignment of the reference variable and control variable of the control valve in dependence on the
• Detected movement direction and a correction value formed from this deviation is supplied to the comparator of reference variable and controlled variable to the control device.
• the delivery of the correction value takes place in the form of a change in the signals of the control and / or controlled variable sent to the comparator.
• the correction value of the control device is delivered such that the conditional by the hysteresis of the system control valve with controlled actuator deviation of the assignment of reference variable and controlled variable is compensated.
• the present invention has set itself the task of providing a fluid-operated valve actuator, which is characterized by a particularly favorable control behavior. This includes, in particular, the fact that disturbances affecting the system are regulated particularly quickly and efficiently.
• the fluid-actuated valve actuator according to the invention is characterized in particular by the fact that at least one functional, preferably between the signal input and the at least one linear actuator electro-luidischen signal converter downstream, fluidic internal control circuit is arranged.
• at least one functional, preferably between the signal input and the at least one linear actuator electro-luidischen signal converter downstream, fluidic internal control circuit is arranged.
• the fluidic internal control loop is designed as a subordinate position control loop.
• Another preferred embodiment of the invention is characterized in that the electro-fluidic signal converter with a closed loop, preferably a pressure or volume flow control loop is designed as a subordinate control loop. This is particularly advantageous in such valve actuators according to the invention, in which the pressurized fluid supply is not decentralized, i. but rather centrally organized.
• an I / P converter is used.
• the I / P converter preferably has an internal pressure sensor and an internal pressure control loop. Instead of a controlled signal transmission here is a closed electrical pressure control loop with a self-regulating pressure plate. The improved control performance achievable in this way leads to optimized process control and quality.
• the I / P converter is operated via particularly energy-efficient and highly dynamic piezoelectric valve technology and / or has no internal air consumption in the adjusted state, the pressure sensor signal for external processing to the electrical control unit is transmitted and / or corresponds to the pneumatic connection diagram between the drive and I / P converter VDI / VDE 3845 for single-acting actuators.
• the fluidic internal control circuit can in particular comprise a control group arranged upstream of the linear actuator with two control elements which can be moved relative to one another.
• Portions releasing or closing components include, of which a first component is coupled to a pilot cylinder acted upon by a control pressure and the second component is coupled to the slide of the linear actuator.
• the control group preferably communicates via a respective discharge line with the two working spaces permanently connected to a pressurized fluid supply.
• the control group comprises two drain valves, each comprising a valve seat slidably mounted within a housing against a bias.
• the valve actuator comprises two opposing linear actuators and one arranged between the two linear actuators whose slide comprises mutually coupling mechanical transducer.
• the said mechanical converter can in particular implement the linear movement of the slides of the two linear actuators in a rotary movement, namely when the valve has a rotatable locking member whose position is variable by means of the valve actuator.
• the actuator as a compact, closed, only one electrical input and acting on the input of the valve mechanical drive having fluidic drive system modularly constructed of individual, assembled into a functional unit components in the form of the base unit, the two linear actuators and the mechanical transducer ,
• the joining of said components to the compact, closed fluidic see drive system can be characterized in particular reali ⁇ Siert that the two linear actuators are flanged to the transducer, which in turn is connected via a flange with the base unit. This allows - according to a turn preferred development - all fluid connections between the base unit and the actuators and optionally the
• valve actuators run within the components in question, so that no exposed fluid lines exist.
• the said fluid connections can be equipped with self-closing barriers, especially in the area of the dividing planes through which they pass, between the said components, which prevent the escape of fluid or the unintentional penetration of contaminants along the dividing planes, in particular if individual components have been dismantled for the purpose of maintenance , In the area of the barriers, additional filter elements for the fluid can be provided, in particular integrated into these or connected to these in each case to form a structural unit. All of the above-mentioned, the valve actuator according to the invention structurally further developing technical aspects prove to be particularly advantageous in hydraulic valve actuators according to the present invention.
• the pressurized fluid supply is both centrally, i. for several valve actuators in common, as well as decentralized, i. each associated with only a single valve actuator, can be organized.
• decentralized i. each associated with only a single valve actuator
• Base unit of the invention fizidbetätigten valve actuator drive a pressurized fluid supply unit.
• a hydraulically actuated valve actuator according to the present invention comprises such
• the said pressurized fluid supply unit preferably comprises an ambient medium driven by an electric motor, preferably via a filter system, and sucking in a pneumatic pump.
• the fluid-actuated valve actuator according to the invention may, according to yet another preferred development, have a filling port suitable for initial filling of the fluid system with hydraulic fluid from a cartridge, in particular on the base unit. This allows the user-side commissioning of a hydraulically operated valve actuator according to the present invention, without the user in any way comes into contact with Hydraulikfizid.
• valve actuators which are superior in terms of their operating behavior, are hydraulically actuated (see above).
• the valve actuators can also be used in applications in which the user is particularly concerned with cleanliness and a minimal risk of coming into contact with hydraulic fluid.
• fluid energy can be stored in a (especially external) accumulator to bring in case of failure of the pressurized fluid supply, the valve at least in a predetermined safety position , Rather, it is also possible, if appropriate in addition, to integrate a mechanical storage spring into the at least one linear actuator.
• a mechanical accumulator spring is biased by fluid pressure and locked in the biased position, so that they are not constantly applied to the slide of the linear actuator in the sense that would have to be permanently worked against the force of the mechanical accumulator.
• the mechanical storage spring acts on the slide of the associated linear actuator only after actuation of an unlocking, by means of which a blockage blocking the storage spring is released.
• Such blocked in normal operation blocking locked, released only in an emergency by removing the blockage mechanical accumulator combines the advantages of high reliability of the valve actuator with other aspects such as economy, compactness and dynamic response.
• FIG. 1 is a schematic representation of a hydraulically operated valve actuator according to the present invention
• Fig. 2 shows a structural design of a in the
• Valve actuator according to FIG. 1 realized self-regulated position drive
• Fig. 3 is a schematic representation of a pneumatic working valve actuator according to the present invention.
• Fig. 4 is the control diagram of that shown in Figs. 1 and 3
• Embodiments of a fluid-operated valve actuator according to the invention Embodiments of a fluid-operated valve actuator according to the invention.
• a linearly movable gate valve 1 comprehensive shut-off valve 2 is assigned a hydraulically operating valve actuator 3.
• This comprises as main components a linear actuator 4 and a pressure fluid supply unit 5 and a fluidic control having base unit 6.
• the linear actuator 4 is a double-acting hydraulic cylinder with a guided in a cylinder 7 piston 8, the two oppositely acted on working spaces 9 and 10 from each other separates and is connected to a slide 11 in the form of a piston rod 12 executed.
• the piston rod 12 acts directly on the gate valve 1 of the shut-off valve. 2
• the pressurized fluid supply unit 5 comprises in known manner a hydraulic unit 13 with a driven by an electric motor 14 hydraulic pump 15 and a tank 16 for the hydraulic fluid.
• the base unit 6 further comprises fluidically pilot-operated valves 17 and a fluidic interface 18, via which the base unit is connected to a downstream fluidic translator 19.
• the fluidically pilot-operated valves 17 of the base unit 6 are actuated-via associated signal inputs-by electro-fluidic signal converters in the form of pilot valves 20, to which in turn an electrical control unit 22 equipped with a communication interface 21 acts. Via the communication interface
• a setpoint value input 23 connected to a desired value input is furthermore connected to the control unit 22.
• the gate valve 1 of the shut-off valve 2 is associated with a position sensor 24 which is connected via a communication interface 25 with the control unit 22 and the actual position of the gate valve 1 to the control unit
• valve actuator of FIG. 1 is based on the well-known, widely used in the art, so that further explanations are unnecessary.
• the fundamental deviation of the valve actuator 3 of FIG. 1 over the prior art is that the control unit 22 does not act directly on the linear actuator 4, as a function between the signal input of the base unit 6 and the linear actuator 4 a the electro -fluidic signal converter downstream fluidic internal control loop 27 exists.
• the fluidic translator 19 is thus not in direct hydraulic communication with the terminals of the linear actuator 4, but rather, with a purely hydraulic, a self-regulated position drive 28 comprehensive rule group 29th
• the self-regulated position drive 28 comprises (see FIG. 2) a housing 30 and a slide 31 guided therein (double arrow A), which is sealed relative to the housing 30 by means of the sealing rings 32. Furthermore, two nozzle inserts 33 are received in the housing 30. These are also slidably guided in the housing 30, parallel to the direction of movement A of the slide 31, and sealed relative to the housing 30 by means of the sealing rings 34. They are further biased by means of springs 35 against a stop 36. In this case, in the neutral position of the self-controlled position drive 28 illustrated in FIG. 3, the two nozzle inserts are sealingly connected to sealing bodies 49, which are arranged on the slide 31 at the front end, that control openings of the nozzle inserts 33 are closed by said sealing bodies 49.
• the slide 31 of the self-regulating position drive 28 is connected via a coupling rod 37, which passes through the housing 30 through a window 48, with the slider 11 of the linear actuator 4, so that it follows its movement immediately.
• the housing 30 of the self-regulating position drive 28 is in turn displaceable. Its position is from a double-acting pilot cylinder 38
• the pilot cylinder 38 is controlled by the control unit 22 via the base unit 6 and the fluidic translator 19; The latter thus provides the position of the housing 30 of the self-controlled position drive 28 via the pilot cylinder 38.
• the two working spaces 9 and 10 of the linear actuator 4 are constantly connected via high-pressure lines 39 with flow restrictors 40 to the high-pressure side 41 of the pressure fluid supply unit 5, ie are constantly subjected to their delivery pressure.
• the two working spaces 9 and 10 of the linear actuator 4 are in each case connected via an outlet line 42 to an input 43 in the housing 30 of the self-controlled position drive 28. In the adjusted state, the same pressure conditions prevail in both pressure chambers 44 of the self-regulated position drive 28 as in the working spaces 9 and 10 of the linear actuator 4.
• the housing 30 of the self-regulating position drive 28 is moved upward in the direction of lifting the gate valve 1 by the control unit 22, by the base unit 6 and the fluidic translator 19, then the upper of the two pressure chambers 44 passes through the bore 45 of the associated nozzle insert 33 is connected to the low pressure side 46 of the pressurized fluid supply unit 5.
• the pressure in the upper working chamber 9 of the linear actuator 4 falls below the pressure prevailing in the lower working chamber 10, so that the slider 11 of the linear actuator 4 is raised in the sense of a subsequent control, namely until it is coupled to the slider 11 of the linear actuator 4
• Gate valve reaches the position in which the coupled with him slide 31 of the self-regulating position drive 28 both nozzle inserts 33 closes again.
• control group 29 has two drain valves 47, each comprising a valve seat slidably mounted within a housing 30 against a bias voltage.
• An acting on the gate valve 1 disturbance is corrected in the system shown directly within the purely hydraulic control loop of the self-regulating position actuator 28, so far as no regulatory intervention of the control unit 22 takes place.
• the control characteristic of the control unit 22 is tuned to this.
• FIG. 3 illustrates an embodiment substantially similar in function to the embodiment according to FIG. 1, in which, however, the following deviations from the embodiment according to FIG. 1 should be emphasized.
• shut-off valve 2 instead of a locking slide on a shaft 50 rotatable locking member 51. This is rotatably connected to a shaft 52. Furthermore, in the embodiment according to FIG. 3, two counter-rotating double-acting linear actuators 4 are used. These are connected in pairs in opposite directions to the other components of the pneumatic system. Further, the linear motion of the two linear actuators in a mechanical transducer W is converted into rotation by the slide of the linear actuators on racks 53 act on a rotatably connected to the shaft 52 gear 54.
• the valve actuator operates pneumatically.
• the compressed-fluid supply unit 5 comprises an air compressor 55 instead of a hydraulic pump. This compressor sucks in ambient air via a filter 56. The pneumatic fluid is blown off at the low pressure side into the environment, for which purpose a silencer 57 is provided there.
• an input signal passes via the communication input 60 to the positioner 61 (see control unit 22).
• This can, as shown in FIGS 1 and 3, act directly on a Fuidstel- ler 62 (see, pilot valves 20) which acts on a fluid interrupter 63 (see hydraulically pilot operated valves 17), which in turn to another fluid intensifier 64 ( See fluidic translator 19) acts.
• a lower pressure control loop 65 comprising a self-regulating pressure regulator can be integrated with a pressure regulator 66, to which the signal of a pressure sensor 67 is fed back, between the positioner 61 and the further fluid converter 64.
• the output of the further fluid translator 64 acts on the position controller 68 (see control group 29), which forms a subordinate position control loop 71 comprising a self-regulating position drive in conjunction with the linear drive 69 (see linear actuator 4) and the displacement transducer 70 (see coupling rod 37) ,
• the linear actuator 69 acts on a
• Rotary transducer 72 (see mechanical transducer W) whose output acts on the valve 73 (see shut-off valve 2).
• the position of the rotary transducer 72 can be optically displayed in the position indicator 74 (see position indicator 26). Furthermore, the actual position of the linear drive (embodiment according to FIG. 1) or of the rotary converter (embodiment according to FIG. 3) is detected by a position sensor 75 (see position sensor 24) and returned to positioner 61 to form a control loop 76 for valve position ,

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Physics & Mathematics (AREA)
• Fluid Mechanics (AREA)
• Fluid-Driven Valves (AREA)
• Servomotors (AREA)
• Fluid-Pressure Circuits (AREA)
• Fluid-Damping Devices (AREA)

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• 2010
  • 2010-02-05 DE DE102010007152.8A patent/DE102010007152B4/de not_active Expired - Fee Related
• 2011
  • 2011-02-04 CN CN201180016589.9A patent/CN102822536B/zh not_active Expired - Fee Related
  • 2011-02-04 BR BR112012019657A patent/BR112012019657A2/pt not_active IP Right Cessation
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  • 2011-02-04 EP EP11703597A patent/EP2531734A1/de not_active Withdrawn
  • 2011-02-04 WO PCT/EP2011/000528 patent/WO2011095351A1/de active Application Filing
  • 2011-02-04 KR KR1020127020554A patent/KR20120120286A/ko not_active Application Discontinuation
• 2012
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