WO2021224386A1 - Soupape à entraînement hybride, électrique et pneumatique - Google Patents

Soupape à entraînement hybride, électrique et pneumatique Download PDF

Info

Publication number
WO2021224386A1
WO2021224386A1 PCT/EP2021/061984 EP2021061984W WO2021224386A1 WO 2021224386 A1 WO2021224386 A1 WO 2021224386A1 EP 2021061984 W EP2021061984 W EP 2021061984W WO 2021224386 A1 WO2021224386 A1 WO 2021224386A1
Authority
WO
WIPO (PCT)
Prior art keywords
actuator
control
adjusting device
control actuator
designed
Prior art date
Application number
PCT/EP2021/061984
Other languages
German (de)
English (en)
Inventor
Karl Morgenbesser
Thorsten NEUKAMM
Original Assignee
Karl Morgenbesser
Neukamm Thorsten
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Karl Morgenbesser, Neukamm Thorsten filed Critical Karl Morgenbesser
Publication of WO2021224386A1 publication Critical patent/WO2021224386A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0207—Surge control by bleeding, bypassing or recycling fluids
    • F04D27/0215—Arrangements therefor, e.g. bleed or by-pass valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
    • F16K1/18—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps
    • F16K1/22—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation crossing the valve member, e.g. butterfly valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
    • F16K31/041—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves
    • F16K31/042—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves with electric means, e.g. for controlling the motor or a clutch between the valve and the motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
    • F16K31/041—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves
    • F16K31/043—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves characterised by mechanical means between the motor and the valve, e.g. lost motion means reducing backlash, clutches, brakes or return means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/126—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a diaphragm, bellows, or the like
    • F16K31/1262—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a diaphragm, bellows, or the like one side of the diaphragm being spring loaded
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/42—Actuating devices; Operating means; Releasing devices actuated by fluid by means of electrically-actuated members in the supply or discharge conduits of the fluid motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/44—Mechanical actuating means
    • F16K31/53—Mechanical actuating means with toothed gearing
    • F16K31/54—Mechanical actuating means with toothed gearing with pinion and rack
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D16/00—Control of fluid pressure
    • G05D16/024—Controlling the inlet pressure, e.g. back-pressure regulator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/60—Control system actuates means
    • F05D2270/62—Electrical actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/60—Control system actuates means
    • F05D2270/65—Pneumatic actuators

Definitions

  • the invention relates to an actuating device for systems with flowing fluid, in particular for fluid delivery systems.
  • the invention also relates to a system with such an actuating device.
  • Turbo compressors are used to compress any gases, for example air.
  • turbo compressors can be used in applications in which large volume flows are to be compressed. These include blast furnace blowers, air separation systems, chemical and petrochemical systems, applications to increase pressure in gas pipelines, vacuum blowers in the paper industry, vapor compression in evaporation processes or compressed air compressors.
  • Turbo compressors especially those with an electric drive, must be able to start up against minimal counter pressure because of the reduced torque of the electric motor when starting up.
  • a small safety margin to the surge limit (stability limit of a turbo compressor)
  • an adequate anti-surge control is required.
  • the pressurized compressor should be relieved as quickly as possible.
  • a turbo compressor should not pump even after a load shutdown while coasting. Rapid relief should also meet high security requirements and be fail-safe.
  • the energy required for quick adjustment is stored beforehand, which is usually achieved by pretensioning a spring. Such devices require additional energy, build very expansive and increase the investment costs.
  • Further design variants are, for example, hydraulic or pneumatic accumulators, which are considered to be pressure vessels and are correspondingly maintenance-intensive.
  • the object of the present invention was to provide an actuating device which, with a simple structure and at the same time with a high level of safety, enables a safety position to be approached.
  • the task also consisted of specifying a system with such an actuating device.
  • An actuating device according to the invention is designed for systems with flowing fluid, in particular for fluid delivery systems.
  • Such an actuating device has at least one actuator which can be adjusted to throttle and / or shut off a flowing fluid between a plurality of operating positions and for quick relief or for quick shutoff using the pressure of a fluid as the exclusive, main or supporting actuating force for approaching a safety position.
  • the actuator can have an electric actuator and / or be driven by an electric actuator.
  • Electric actuators allow precise adjustment and thus also contribute to a precise position of the respective actuator.
  • the actuator can be set up as a fail-safe device to use the pressure of the fluid as the exclusive, main or supporting actuating force in the event of failure of a supply of drive energy, in particular in the event of failure of an electrical energy supply to the actuator, for quick relief or for quick shut-off To use approaching a safety position.
  • safety elements such as adjusting springs
  • an electric drive can be made smaller overall.
  • the actuator can be set up to move to a safety position for rapid relief with reduced or minimized electrical energy or without electrical energy. This allows the Operational safety can be further improved. In such a configuration, no or only reduced electrical energy is required to achieve a safety position. A safety position can be approached even in the event of malfunctions in the electrical power supply.
  • an actuator of the actuator can be decoupled for moving to a safety position, in particular can be decoupled by a switchable coupling with fail-safe function.
  • a decoupling can simplify or accelerate the approach to the safety position, since any counteracting forces of the actuator are avoided.
  • the switchable coupling with fail-safe function can be closed under electrical voltage and, in the event of a voltage failure, can be opened and uncoupled by opening. In the event of a fault in the electrical energy supply, uncoupling and thus also approaching a safety position can take place with high reliability.
  • an actuator of the actuator can be operated to approach a safety position at a higher speed, in particular by switching to a different gear ratio or by increasing the drive speed in the case of a variable-speed design. Approaching a safety position can be accelerated in this way with only simple means.
  • the actuator can be set up to move to a safety position driven by an opening piston for quick relief.
  • the opening piston can be controlled by a solenoid valve which opens in the de-energized state, with the opening piston being acted upon by a pressurized fluid in the open state of the solenoid valve. In this way, the pressurized fluid can be used in a reliable manner to approach a safety position.
  • the actuator can be set up to move to a safety position, driven directly by a pressurized fluid, for quick relief. This can be done with a relatively small number of components, which ensures a structure that is not susceptible to failure. In particular, such a structure can be implemented without separate components for approaching a safety position.
  • the actuating device according to the invention can consist of a plurality of actuators. In this way, different functionalities can be advantageously distributed among different actuators.
  • actuators for throttling and / or blocking a flowing fluid can be adjustable between a plurality of operating positions. In this way, a high degree of flexibility in operation can be achieved.
  • actuators for quick relief and / or for quick shut-off can be adjustable using the pressure of a fluid as the exclusive, main or supporting actuating force for approaching a safety position.
  • the actuator can be adjustable to a safety position OPEN or CLOSED for quick relief or for quick shut-off, or several or all of the actuators can be adjustable to a safety position OPEN or CLOSED for quick relief or for quick shut-off.
  • a dangerous situation can be counteracted in just a short time.
  • Critical system components can thus be protected from damage. In many applications, this can be of particular importance in order to ensure operational reliability.
  • At least one of the actuators can be designed as a pressure-compensated actuator. Since no gas forces have to be overcome in a pressure-balanced actuator, the actuating forces required during operation are low.
  • At least one of the actuators can be designed as a non-pressure-compensated actuator.
  • a non-pressure-compensated actuator can advantageously be moved directly into a safety position, driven directly by a pressurized fluid, in particular without separate drive components.
  • the pressure of the fluid can also be used in normal operation to adjust the respective actuator.
  • Any pneumatic and / or hydraulic drive can be made smaller in this case.
  • the actuator or at least one actuator can be designed as a control actuator that is adjustable between a plurality of operating positions in a controlled manner, and / or that the actuator or at least one actuator is designed as a control actuator that is adjustable in a controlled manner. While relatively large flow rates can be achieved with the control actuator, the control actuator enables sensitive regulation. The division into separate actuators allows the control actuator to be designed primarily with regard to the control accuracy. The implementation of a high control quality with high flow rates at the same time by means of a single and therefore complex actuator can be avoided according to the invention.
  • control or a control As far as a control or a control is mentioned in the sense of the present invention, this is intended to mean an open control or an open control. Insofar as a regulation or a regulation is mentioned in the sense of the present invention, a closed regulation or a closed regulation should be meant.
  • control actuator can be adjustable between more than two operating positions, in particular between two end positions and any number of intermediate positions.
  • control actuator and the control actuator can be connected in parallel to influence the same process variable, the control actuator being set up for adjustment as a function of an operating position of the control actuator.
  • control actuator as a function of an operating position of the control actuator enables a suitable control range of the control actuator to be maintained at all times during operation.
  • control actuator as a function of the control actuator, however, the overall control range is significantly expanded without increasing the complexity of the individual components or the entire arrangement.
  • control actuator can be set up for adjustment as a function of an operating position assumed by the control actuator when passing through a limit manipulated value, in particular an operating position assumed by the control actuator when a lower limit manipulated value is undershot and / or an operating position assumed by the control actuator when an upper limit manipulated value is exceeded .
  • a limit manipulated value in particular an operating position assumed by the control actuator when a lower limit manipulated value is undershot and / or an operating position assumed by the control actuator when an upper limit manipulated value is exceeded .
  • control actuator can be set up for a controlled adjustment, which generates a regulated adjustment of the control actuator into a setpoint adjustment range. This ensures that a high control quality is maintained over the entire setting range.
  • a controller can be set up to adjust the control actuator as a function of an operating position of the regulating actuator.
  • a control system can be set up to adjust the control actuator as a function of a process variable influenced by the control actuator and the control actuator. With such a control or regulation, the control actuator or the regulating actuator can be operated in a suitable manner and sensitive regulation can be implemented over the entire setting range.
  • a controller of the control actuator can preferably be set up to continue an adjustment of the control actuator until the control actuator has reached and / or passed a predefined operating position within the setpoint adjustment range.
  • Such predefined operating positions can be freely set (for example 50% or 45% and 55%) or can be changed subsequently. In this way, stable operation of the regulating actuator and the control actuator can be ensured, in particular without the risk of undesired build-up.
  • a lower limit manipulated variable of the regulating actuator in particular when the operating position is 10% open, and / or an upper limit manipulated variable of the regulating actuator, in particular when the operating position is 90% open, can be preset.
  • the respective limit control values can be freely adjustable or subsequently changed, depending on the application. Such limit control values can be used to determine an optimal operating range or setpoint control range of the control actuator in a suitable manner.
  • a target setting range of the control actuator can be between an operating position that is 10% open and an operating position extend to 90% open operating position.
  • the respective target setting range can be freely adjustable or subsequently changed, depending on the application. With such a dimensioned target setting range, an optimal operation with a safe distance from the respective end positions of the control actuator can be guaranteed.
  • control actuator can be set up for fully automatic, partially automatic and / or purely manual adjustment as a function of an operating position of the control actuator.
  • a fully automatic adjustment can reduce the operating effort during operation to a low level.
  • a semi-automatic adjustment can take place, for example, in that when the control actuator passes through a limit setting value, a signal is generated to an operator, in particular an optical or acoustic warning signal, whereupon a manually initiated adjustment of the control actuator can be initiated.
  • a purely manual adjustment of the control actuator can also take place, for example, in that an operator continuously monitors the passage through a limit control value by the control actuator. If necessary, an adjustment of the control actuator can again be initiated manually.
  • control actuator has and / or is operated by an electric actuator electric actuator driven.
  • Electric actuators allow precise adjustment and thus also contribute to precise regulation of the position of the control actuator.
  • control actuator can have an electric actuator and / or be driven by an electric actuator.
  • an electric actuator allows precise adjustment and thus also enables precise control of the position of the control actuator.
  • control actuator can have a greater flow capacity than the regulating actuator.
  • the flow capacity should be understood here as the possible flow rate per unit of time that can be guaranteed by the respective actuator.
  • control actuator can be designed as a controlled valve.
  • regulating actuator can be designed as a regulated valve.
  • Such valves are suitable for a large number of applications and can be used in a suitable manner in fluid delivery systems and can be combined with one another.
  • the actuator in particular the control actuator and / or the regulating actuator, are designed for use with turbo compressors.
  • Turbo compressors are used in a wide variety of applications used to compress gases.
  • control actuator is designed and / or set up for the start-up relief and / or for the event-controlled rapid relief during operation of a turbo compressor. In many cases, it is only the start-up relief that enables an electric motor-driven turbo compressor to start up. Event-controlled rapid relief can be used in the event of malfunctions to prevent damage to the compressor or to the downstream process.
  • a tightly closing regulating actuator can be designed and / or set up for anti-pumping, in particular by means of anti-pumping control. With such a regulating actuator, stable operation along the surge limit line can be maintained in a turbo compressor.
  • control actuator can be designed and / or set up for anti-surge protection, in particular by means of anti-surge control.
  • a turbo compressor pumps if an anti-surge control does not intervene or intervenes too late. Continuous pumping can very quickly lead to massive damage to the compressor and fatal effects on the downstream process. This can be prevented with a pump protection control, which is only activated by a pumping process and subsequently activates rapid relief by the control actuator and / or the regulating actuator or by switching off the motor.
  • the regulating actuator can have a linear, equal percentage or individualized characteristic curve. Any application-related optimization can be achieved through an individualized opening characteristic.
  • control actuator can have a non-linear characteristic curve, in particular one
  • Rapid opening characteristic in which the change in the flow rate per travel unit increases disproportionately when the closed position is left. In this way, particularly rapid pressure relief can be achieved by the control actuator.
  • the actuator in particular the control actuator and / or the regulating actuator, can be set up to check the freedom of adjustment, in particular for test actuation movements at predefined time intervals.
  • certain applications only require the adjustment of actuators in larger time intervals. If the actuator is not actuated for a longer period of time, the respective actuator may become jammed. Such jamming can be avoided or at least recognized at an early stage by means of test positioning movements at predefined time intervals, so that suitable measures can be taken.
  • At least two actuators in particular the control actuator and the regulating actuator, form a structural unit and / or are designed as a double actuator.
  • Such a configuration enables particularly simple assembly in a fluid delivery system.
  • a coordination of the individual actuators can be preset in an advantageous manner when designed as a double actuator.
  • control actuator can have a housing with connections for Have the control actuator installed.
  • This compact unit is particularly suitable for replacing an already installed actuator without additional welding work on the pipeline.
  • the actuator in particular the control actuator, can furthermore preferably be set up to act with full adjusting capacity from a closed operating position and in the event of a control deviation of the control until the actuator, in particular the regulating actuator, effectively begins to open, and from the start of opening to switch from the adjustment controlled with full capacity to a regulated adjustment with standard capacity. In this way, the achievement of an effective start of opening can be accelerated.
  • the actuator in particular the regulating actuator, can have a pneumatic actuator, which is operated for opening at full adjusting capacity with suspension of control parameters and / or with suspension of pulsing activation and / or with permanent activation until the actuator, in particular the regulating actuator effectively begins to open.
  • a pneumatic actuator which is operated for opening at full adjusting capacity with suspension of control parameters and / or with suspension of pulsing activation and / or with permanent activation until the actuator, in particular the regulating actuator effectively begins to open.
  • the actuator in particular the regulating actuator, can have an electric or hydraulic actuator which is operated for opening at full actuating capacity, in particular from an overlapping, sealed valve position, at maximum actuating speed until the actuator, in particular the regulating actuator, begins to open effectively .
  • the actuator in particular the regulating actuator
  • the actuator can have an electric or hydraulic actuator which is operated for opening at full actuating capacity, in particular from an overlapping, sealed valve position, at maximum actuating speed until the actuator, in particular the regulating actuator, begins to open effectively .
  • dead times of the regulating actuator can be avoided in a particularly advantageous manner or reduced to a small extent.
  • the actuator in particular a control actuator, is designed as a flap actuator and the control range of a control actuator designed as a control valve or control flap is at least as large as a limit area adjacent to a CLOSED position of the flap actuator, which is provided by the manufacturer and / or or is structurally not designed for continuous operation and / or in which continuous operation is prevented by control parameters.
  • the flow velocity around such a limit area can be high, for example assume the speed of sound, which causes dynamic forces on the valve plate in alternating directions.
  • control parameters in such a limit area can therefore be prevented by control parameters in such a limit area.
  • the control parameters can be selected or set with a view to merely passing through such a limit area during operation and thereby avoiding continuous operation in the limit area.
  • control range of the control actuator designed as a control valve or control flap can advantageously be dimensioned at least as large as the limit area of the flap actuator.
  • control range of a control actuator can advantageously be designed in such a way that at least one limit area of the flap actuator specified by the manufacturer is covered. Individual process requirements can result in a larger control range.
  • Another aspect of the present invention relates to a system with a delivery device for a flowing fluid, in particular a turbo compressor, and with an actuator device described above. The arrangement according to the invention in such a system is simple and robust in structure and at the same time ensures sensitive control over an arbitrarily large capacity range through the actuating device.
  • control actuator and the regulating actuator are preferably installed in lines running in parallel. In this way, the control actuator and the regulating actuator can advantageously influence the same process variable.
  • control actuator is installed in a line in which connections for the installation of the control actuator are integrated immediately before and after the control actuator.
  • the installation of the control actuator can be simplified in this way, since there is no welding work for pipelines.
  • a fitting piece for connecting the control actuator and / or the regulating actuator can be provided in at least one line.
  • the connection for a control actuator and / or regulating actuator can be implemented via a fitting piece of this type.
  • the regulating actuator can be integrated in a fitting piece which has connections for the installation of an external control actuator.
  • One Optimization of the system by adding a further actuator can be simplified as a result.
  • the control of the delivery device in particular the turbo compressor, is designed and / or set up for a fault shutdown.
  • This device has the effect that the quick opening of the actuators involved is activated immediately if the drive fails. Without activation, damage can occur, especially in the intake area of a turbo compressor. Reaching the safety position can be recognized within a predefined time after activation of the quick opening function, otherwise the compressor is switched off.
  • the conveyor device in particular the turbo compressor, can be designed and / or set up to detect a malfunction in the rapid relief of the control actuator and / or the regulating actuator due to the lack of feedback (OPEN or CLOSED) within a predefined and / or parameterizable period of time
  • OPEN or CLOSED the lack of feedback
  • Such a monitoring can initiate a fault shutdown and fatal damage can be avoided.
  • Another aspect of the present invention relates to a method for controlling and / or regulating a system with flowing fluid, in particular for a fluid delivery system, in which at least one actuator for throttling and / or blocking a flowing fluid between a plurality of operating positions and for quick relief and / or for quick shut-off using the pressure of a fluid as exclusive, primary or auxiliary Adjusting force to approach a safety position is adjusted.
  • FIG. 1 shows a fluid delivery system with a turbo compressor and an actuating device according to the prior art
  • FIG. 2 shows a fluid delivery system with a turbo compressor and an actuating device according to an embodiment of the present invention
  • FIG. 3 shows a fluid delivery system with a turbo compressor and an actuating device according to a further embodiment of the present invention
  • FIG. 4 shows a fluid delivery system with a turbo compressor and an actuating device according to yet another embodiment of the present invention
  • FIG. 5 shows a fluid delivery system with a turbo compressor and an actuating device according to yet another embodiment of the present invention
  • FIG. 6 shows a fluid delivery system with a turbo compressor and an actuating device according to yet another embodiment of the present invention
  • 7 shows a logic for the activation of a control actuator as a function of the position of a control actuator according to an embodiment of the present invention.
  • FIG. 1 shows schematically a fluid delivery system 100 with a turbo compressor 102 and an actuating device 104 according to the prior art.
  • the actuating device 104 comprises, in a conventional manner, a single control flap, which is moved by a pneumatic diaphragm control drive 106 with an associated position controller 108.
  • the actuating device 104 embodied as a regulating flap can be, for example, a so-called blow-around valve that guides gas from the pressure line 110 back into the suction line 112.
  • a 2/3-way solenoid valve 114 can be provided both for quick opening and also provide fail-safe functionality.
  • the actuating device 104 designed as a control flap must meet several requirements at the same time. Both sensitive control and a relatively large flow rate must be implemented. The actuating device is therefore large and at the same time equipped with a large number of accessories. This leads to high susceptibility to failure and high acquisition costs.
  • the fluid delivery system 10 has a turbo compressor 12, a suction line 14 upstream of the turbo compressor 12 and a pressure line 16 after the turbo compressor 12.
  • the fluid conveying system 10 in FIG. 2 differs from the fluid conveying system 100 from FIG. 1 in the arrangement of the actuating device 18 instead of the large control flap
  • the system 100 from FIG. 1 can be converted into a system 10 according to the invention according to FIG Actuating device 18 can be provided, as can be seen from FIG. 2. With such a fitting 20 it is possible to integrate an adjusting device 18 according to the invention into an existing line system without welding.
  • the actuating device 18 has at least one control actuator 22, which is openly adjustable between a plurality of operating positions, and at least one regulating actuator 24, which can be adjusted between a plurality of operating positions in a closed manner.
  • the control actuator 22 and the regulating actuator 24 are connected in parallel to influence the same process variable and / or the same process variables.
  • the process variables are, in particular, the pressure in the suction line 14 and the pressure in the pressure line 16.
  • control actuator 22 is set up for adjustment as a function of an operating position of the regulating actuator 24.
  • the control actuator 22 can be designed as a large and pressure-balanced actuator and / or as a flap actuator and can move to a safety position OPEN.
  • control actuator 24 Integrated into the housing of the control actuator 22 are two connections for the lines to and from the control actuator 24.
  • a relatively small actuator that is moved by an actuator 26 is shown as the control actuator 24.
  • the control actuator 24 can move to a safety position OPEN.
  • the actuator 26 can be controlled by an anti-surge controller 28.
  • the anti-surge controller 28 can control the actuator 26 as a function of the pump-relevant variables (for example flow and pressure) measured in the suction line 14 and / or in the pressure line 16.
  • the control actuator 22 can be moved by a variable-speed actuator 30 via an adjustment logic 32. Furthermore, a gear 31 can be provided between the actuator 30 and the control actuator 22.
  • the adjustment logic 32 can receive signals from the actuator 30, from the anti-surge controller 28 and / or from the control actuator 24 or the actuator 26 for the control actuator 24.
  • the control actuator 22 is also set up to move to a safety position driven by an opening piston 34 for rapid relief, in particular into an OPEN position.
  • the opening piston 34 can advantageously be actuated by the process medium from the pressure line 16.
  • a solenoid valve 36 is provided, which is open in the de-energized state. In the event of a power failure, pressure from the pressure line 16 can thus actuate the opening piston 34, by means of which the control actuator is moved in the OPEN direction.
  • the opening piston 34, the solenoid valve 36, the actuator 30 with the gear 31 thus form a device 38 for quickly moving the control actuator 22 into a safety position.
  • FIG. 3 shows a fluid delivery system 10 according to a further embodiment of the present invention.
  • the embodiment in FIG. 3 differs from the embodiment in FIG. 2 only in the arrangement or configuration of the actuating device 18.
  • the fitting piece 20 is equipped with an internal line routing and an integrated regulating actuator 24.
  • the actuator 24 integrated in the fitting is designed as a small control valve.
  • the regulating actuator 24 is moved by the regulating drive 26, which is controlled by the anti-surge controller 28.
  • the control actuator 24 can move to a safety position OPEN.
  • connections for the externally arranged control actuator 22 are also provided on the fitting piece 20.
  • the control actuator 22 is designed as a large, non-pressure compensated control valve, in particular larger than the control actuator 24.
  • the control actuator 22 can therefore ensure a greater flow rate than the control actuator 24.
  • the control actuator 22 can move to a safety position OPEN.
  • control actuator 22 can be moved by an actuator 30 via an adjustment logic 32.
  • a gear 31 with a switchable gear ratio can be provided between the actuator 30 and the control actuator 22.
  • the adjustment logic 32 can in turn receive signals for the adjustment of the control actuator 22 from the anti-surge controller 28 and / or from the control actuator 22 or the actuator 26 for the control actuator 22.
  • the gas pressure on the inlet side of the control actuator 22 acts in the opening direction.
  • the transmission 31 is switched to a different transmission ratio, which causes the control actuator 22 to move much more quickly. This is possible because the actuator 30 is supported in the opening direction by the gas pressure.
  • the actuator 30 and the gear 31 with switchable gear ratio thus form a device 38 for quickly moving the control actuator 22 into a safety position.
  • FIG. 4 shows a fluid delivery system 10 according to a further embodiment of the present invention.
  • the embodiment in FIG. 4 differs from the embodiment in FIG. 2 only in the arrangement or configuration of the actuating device 18.
  • Actuating device 18 in turn has a control actuator 22 and a regulating actuator 24.
  • the control actuator 22 and the regulating actuator 24 are designed according to FIG. 4 as a double actuator or double valve
  • the control actuator 22 according to FIG. 4 is designed as a large, pressure-balanced control valve and can move to a safety position OPEN. Integrated into the housing of the control actuator 22 is the smaller control actuator 24, which can also move to a safety position OPEN. The control actuator 24 is moved by the actuator 26 and the actuator 26 is activated by the anti-surge controller 28.
  • the control actuator 22 is moved by the actuator 30 via an adjustment logic 32.
  • the adjustment logic 32 receives signals from the anti-surge controller 28 and / or from the control actuator 22 or the actuator 26 for the control actuator 22.
  • a gear 31 and a switchable clutch 33 can be provided between the actuator 30 and the control actuator 22.
  • the switchable Coupling 33 of the actuator 30 can be decoupled from the gearbox 31.
  • the control actuator is driven by the opening piston 34 into a safety position, in particular into an OPEN position.
  • the opening piston 34 is actuated by the pre-pressure control actuator 22 or by the pressure of the process medium from the pressure line 16.
  • the solenoid valve 36 is open to ensure fail-safe functionality in the de-energized state, so that in the event of a power failure, the pressure from the pressure line 16 actuates the opening piston 34.
  • the opening piston 34, the solenoid valve 36, the actuator 30 with gear 31 and clutch 33 form a device 38 for quickly moving the control actuator 22 into a safety position.
  • FIG. 5 shows a fluid delivery system 10 according to a further embodiment of the present invention.
  • the embodiment in FIG. 5 differs from the embodiment in FIG. 4 only in that the actuating device 18 is connected to the suction line 14 and the pressure line 16 via a fitting piece 20.
  • FIG. 6 shows a fluid delivery system 10 according to a further embodiment of the present invention.
  • the embodiment in FIG. 6 again differs from the embodiment in FIG. 2 in the arrangement or configuration of the actuating device 18.
  • the actuating device 18 has a control actuator 22 and a regulating actuator 24.
  • the control actuator 22 and the Control actuator 24 are installed as separately designed valves parallel to the pressure line 16 according to FIG.
  • the control actuator 22 according to FIG. 6 is designed as a large, non-pressure compensated control valve and can move to a safety position OPEN.
  • the small control actuator 24 connected to it can be moved into a safety position OPEN.
  • the control actuator 24 is moved by the actuator 26 and the actuator 26 is activated by the anti-surge controller 28.
  • the control actuator 22 can be moved by the actuator 30 via an adjustment logic 32 and can receive signals from the anti-surge controller 28 and / or from the control actuator 22 or the actuator 26 for the control actuator 22 to adjust the control actuator 22.
  • a gear 31 and a switchable clutch 33 can be provided between the actuator 30 and the control actuator 22.
  • the actuating drive 30 can be decoupled from the gear 31 via the switchable coupling 33.
  • the gas pressure on the inlet side of the control actuator 22 acts in the opening direction.
  • a quick relief can take place through the pressure of the process medium acting directly on the control actuator 22 in the opening direction.
  • the control actuator 22 is designed as a non-pressure-compensated control valve.
  • the actuator 30 with gear 31 and clutch 33 form a device 38 for quickly moving the control actuator 22 into a safety position.
  • FIG. 7 shows a logic 32 for activating a control actuator 22 as a function of the position of a control actuator 24 according to an embodiment of the present invention.
  • the position of the control actuator 22 is readjusted depending on the position of the control actuator 24 if a predefined control signal and / or a predefined position of the control actuator 24 is exceeded or not reached.
  • the operating position of the control valve 24 can be defined or output by the control signal 28 ′ of the anti-surge controller 28 and also by the analog feedback signal 25 ′ of the position controller 25.
  • the adaptation can be application-related and can be different for the opening and closing process.
  • the control actuator 22 is repositioned when the control actuator 24 with a target setting range 27 between 10% and 90% exceeds a limit control value 31 of 90% or falls below a limit control value 29 of 10% .
  • the logic 32 according to FIG. 7 initiates a movement of the control actuator 22 in the same effective direction and consequently supports the change in quantity aimed at by the controller 28.
  • the control actuator 24 has reached a parameterizable position 33 or 35, which in the exemplary embodiment is 50% in each case, the repositioning of the control actuator 22 is completed. This sequence can be repeated as required, so that even very large quantities can be precisely controlled.
  • the 7 has the comparators 40, 40 ′, 42 and 44.
  • the comparators 40, 40 ', 42 and 44 receive signals 28' from the anti-surge controller 28, which in turn controls the actuator 26 for the control actuator 24. Instead of the control signal, the comparators 40, 40 ', 42 and 44 can also monitor the analog position feedback 25' of the control actuator.
  • the comparator 42 detects as soon as the control actuator 24 exceeds a limit control value 31 of 90%.
  • the comparator 44 detects as soon as the control actuator 24 exceeds a limit control value 29 of 10%.
  • the values for the comparators 40, 40 ', 42 and 44 can be freely parameterized.
  • the comparators 40, 40 ', 42 and 44 are followed by the pulse generators 46, 46', 48 and 50.
  • the comparator 40 and the downstream pulse generator 46 reset the flip-flop switching element 54.
  • the comparator 40 'and the downstream pulse generator 46' reset the flip-flop switching element 52.
  • the comparator 42 and the downstream pulse generator 48 set the flip-flop switching element 52.
  • the comparator 44 and the downstream pulse generator 50 set the flip-flop switching element 54.
  • the flip-flop switching elements 52 and 54 are followed by a freely adjustable ramp 56 , via which the actuator 30 of the control actuator 22 is controlled.
  • the pulse generator 48 sets the flip-flop switching element 52 and actuates the actuator 30 in the opening direction via a freely adjustable ramp 56. By activating the actuator 30, the control actuator 22 is adjusted in such a way that the quantity change aimed for by the controller 28 is supported.
  • the flip-flop switching element 54 is set by the pulse generator 50 and the actuator 30 is controlled in the closing direction via a freely adjustable ramp 56. By activating the actuator 30, the control actuator 22 is adjusted in such a way that the quantity change aimed for by the controller 28 is supported.
  • the limit control value 31 is exceeded by 90%, an adjustment of the control actuator 22 is activated until the comparator 40 'detects that a position 35, for example 50%, has been passed through. In the event of a corresponding detection, the flip-flop switching element 52 is reset by the pulse generator 46 'and further activation of the actuator 30 is stopped. The adjustment of the control actuator 22 is thereby ended or at least interrupted. This process can be repeated as often as desired as soon as the control actuator 24 passes through a limit control value.
  • an adjustment of the control actuator 22 is activated until the comparator 40 detects a position 33, for example 50%, being passed through.
  • the flip-flop switching element 54 is reset by the pulse generator 50 and further activation of the actuator 30 is stopped.
  • the adjustment of the control actuator 22 is thereby ended or at least interrupted. This process can be repeated as often as required as soon as the control actuator passes through a limit manipulated variable.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Fluid Mechanics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un dispositif d'actionnement pour des systèmes à fluide en écoulement, en particulier pour des systèmes de distribution de fluide, comprenant au moins un actionneur de commande qui, dans le but d'étrangler et/ou de bloquer un fluide en écoulement, est réglable entre une pluralité de positions de fonctionnement et pour un déblocage rapide ou un blocage rapide à l'aide de la pression d'un fluide en tant que force d'actionnement exclusive, principale ou de support pour s'approcher d'une position de sécurité.
PCT/EP2021/061984 2020-05-06 2021-05-06 Soupape à entraînement hybride, électrique et pneumatique WO2021224386A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202020102558.9U DE202020102558U1 (de) 2020-05-06 2020-05-06 Stelleinrichtung für Systeme mit strömendem Fluid sowie System mit Stelleinrichtung
DE202020102558.9 2020-05-06

Publications (1)

Publication Number Publication Date
WO2021224386A1 true WO2021224386A1 (fr) 2021-11-11

Family

ID=76138047

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2021/061984 WO2021224386A1 (fr) 2020-05-06 2021-05-06 Soupape à entraînement hybride, électrique et pneumatique

Country Status (2)

Country Link
DE (1) DE202020102558U1 (fr)
WO (1) WO2021224386A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11624456B2 (en) * 2018-12-04 2023-04-11 VRG Controls, LLC Anti-surge recycle valve

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19541192A1 (de) * 1995-11-04 1997-05-15 Gutehoffnungshuette Man Verfahren zum Schutz eines Turbokompressors vor Betrieb im instabilen Arbeitsbereich mittels Armaturen mit zwei Stellgeschwindigkeiten
DE102006030108A1 (de) * 2006-06-28 2008-01-03 Man Turbo Ag Vorrichtung und Verfahren zum Durchführen eines Ventiltests an einer Turbomaschine
EP2101240A1 (fr) * 2008-03-10 2009-09-16 Karl Morgenbesser Organe de régulation pour liquides
US20150337977A1 (en) * 2014-05-20 2015-11-26 Dresser, Inc. Device to provide failsafe mechanism on a valve actuator assembly
DE102017222628A1 (de) * 2017-12-13 2019-06-13 Continental Automotive Gmbh Ventil

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1107887B (de) 1957-04-16 1961-05-31 Power Jets Res & Dev Ltd Regler zur Pumpverhuetung bei Stroemungsverdichtern
GB2172053B (en) 1985-03-05 1988-10-05 Rolls Royce Gas turbine engine valve control system
DE3907289A1 (de) 1989-03-07 1990-09-13 Siemens Ag Stellantrieb fuer sicherheitsventile
DK2102458T3 (en) 2006-12-22 2016-11-14 Covanta Energy Llc Dynamic control of selective non-catalytic reduction system for semibatch-fed stoker-based urban waste incineration
CN204719557U (zh) 2015-06-04 2015-10-21 北京自动化技术研究院 一种温控设备的冷却控制系统

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19541192A1 (de) * 1995-11-04 1997-05-15 Gutehoffnungshuette Man Verfahren zum Schutz eines Turbokompressors vor Betrieb im instabilen Arbeitsbereich mittels Armaturen mit zwei Stellgeschwindigkeiten
DE102006030108A1 (de) * 2006-06-28 2008-01-03 Man Turbo Ag Vorrichtung und Verfahren zum Durchführen eines Ventiltests an einer Turbomaschine
EP2101240A1 (fr) * 2008-03-10 2009-09-16 Karl Morgenbesser Organe de régulation pour liquides
US20150337977A1 (en) * 2014-05-20 2015-11-26 Dresser, Inc. Device to provide failsafe mechanism on a valve actuator assembly
DE102017222628A1 (de) * 2017-12-13 2019-06-13 Continental Automotive Gmbh Ventil

Also Published As

Publication number Publication date
DE202020102558U1 (de) 2021-08-09

Similar Documents

Publication Publication Date Title
EP2840264B1 (fr) Système d'actionnement à sécurité intégrée
EP2638297B1 (fr) Entraînement hydraulique ou pneumatique pour l'actionnement d'un appareil de robinetterie comportant une soupape de réglage ou de commande
EP2321537B1 (fr) Dispositif d'actionnement et système de soupape comportant un tel dispositif d'actionnement
EP2033057B1 (fr) Dispositif et procédé pour réaliser un essai de fonction d'organe de réglage sur une turbomachine
WO2012104046A1 (fr) Dispositif de réglage hydraulique
EP2675673B1 (fr) Dispositif d'alimentation en air comprimé pour véhicules utilitaires
DE102013222953A1 (de) Hydraulische Antriebsvorrichtung für eine Arbeitsmaschine
WO2021224386A1 (fr) Soupape à entraînement hybride, électrique et pneumatique
EP1389686B1 (fr) Module de freinage électrohydraulique
DE3811230C2 (fr)
WO2021224385A1 (fr) Dispositif d'actionnement à deux soupapes reliées en parallèle, pour le fonctionnement d'un turbocompresseur
EP2597317A1 (fr) Machine-outil et groupe moteur-pompe
EP0757180B1 (fr) Procédé et dispositif d'opération des turbomachines avec régulateurs à gain proportionnel élevé
DE102010020528B4 (de) Hydrostatischer Antrieb
DE102016212671B4 (de) Ansteuerverfahren zum Ansteuern eines Einlassventils einer Kraftstoffhochdruckpumpe und Kraftstoffeinspritzsystem
EP0771950A1 (fr) Procédé de protection d'un turbo compresseur contre l'opération dans une plage instable au moyen de vannes ayant deux vitesses
EP0810358B1 (fr) Méthode de régulation de la pression de gaz pour des turbines à expansion de gaz
DE102010055716A1 (de) Hydraulischer Antrieb
DE102009012752A1 (de) Ventil
EP2101240B1 (fr) Organe de régulation pour liquides
EP3746662A1 (fr) Système de soupape de régulation permettant une régulation pneumatique indirecte, et procédé de régulation de la pression d'un fluide de travail
WO2020007536A1 (fr) Dispositif de réglage électromagnétique, en particulier pour ouvrir et fermer un dispositif soupape, dispositif soupape pourvu d'un tel dispositif de réglage, amortisseur de vibrations réglable comprenant un tel dispositif de réglage ainsi que véhicule automobile présentant un tel amortisseur de vibrations
DE102017120191B3 (de) Regelbare Kühlmittelpumpe für Haupt- und Nebenförderkreislauf
WO2012104047A1 (fr) Dispositif de réglage hydraulique
DE19505333C2 (de) Hydraulikantrieb

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 21728009

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 21728009

Country of ref document: EP

Kind code of ref document: A1