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US20110240152A1 - System and method for adjusting the position of a control member of a power plant - Google Patents

System and method for adjusting the position of a control member of a power plant Download PDF

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Publication number
US20110240152A1
US20110240152A1 US13/121,127 US200913121127A US2011240152A1 US 20110240152 A1 US20110240152 A1 US 20110240152A1 US 200913121127 A US200913121127 A US 200913121127A US 2011240152 A1 US2011240152 A1 US 2011240152A1
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United States
Prior art keywords
fluid
hydraulic actuator
valve
bypass
hydraulic
Prior art date
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Abandoned
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US13/121,127
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English (en)
Inventor
Johannes Adrianus Maria Overgaag
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Thomassen Energy BV
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Ansaldo Thomassen BV
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Assigned to ANSALDO THOMASSEN B.V. reassignment ANSALDO THOMASSEN B.V. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: OVERGAAG, JOHANNES ADRIANUS MARIA
Publication of US20110240152A1 publication Critical patent/US20110240152A1/en
Abandoned legal-status Critical Current

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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
    • F15B9/09—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 with electrical control means
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/042—Controlling the temperature of the fluid
    • F15B21/0427—Heating
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/62—Cooling or heating means
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/66—Temperature control methods
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6656—Closed loop control, i.e. control using feedback
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/85954—Closed circulating system

Definitions

  • the present invention relates to a system for adjusting the position of at least a control member of a power plant.
  • this type of systems comprises at least one hydraulic actuator including a displaceable member connected to the control member, and controllable by a mineral based hydraulic fluid; at least one servo valve, which includes a valve housing, is arranged to control the actuator utilizing said hydraulic fluid, and is selectively operable between an open position for being in fluid connection with the hydraulic actuator and a closed position for blocking fluid connections to the hydraulic actuator; a hydraulic circuit extending through said hydraulic actuator and said servo valve for circulating said hydraulic fluid; and a control device configured to selectively operating the valve in accordance to the requirements of the power plant.
  • a system of the above-identified type is often used to adjust the position of the IGV vanes assembly of gas turbines and suffers of a number of problems determined by the mineral based hydraulic fluid.
  • the insoluble particles like sludge and varnish, affect the operational reliability of servo valves. In many cases the insoluble particles lead to oil flow problems and lock the components of the servo valves. For example, a gas turbine unit which is affected by sludge and varnish may show increasing costs due to trips or other operational disturbances. The problem is considerably relevant for power plants, for example large power producers operating several generator units in peaking mode. In such a case, the mechanical components of servo valves exposed to the hydraulic fluids may become contaminated with sludge and varnish, leading to malfunction of servo valves that hydraulically control generator operations. Hydraulic fluid cleaning methods have been tried to solve the problem, however, so far, they were not completely effective in solving the problem.
  • EP 269,091 discloses a hydraulic circuit including a servo valve, and a double effect hydraulic cylinder controlled by the servo valve.
  • the supply branch of the hydraulic cylinder is connected to the hydraulic fluid draining branch of the hydraulic cylinder so as to keep the hydraulic fluid flowing even in absence of stroke of the displaceable member.
  • the proposed solution is effective when the displaceable member is in abutment against outer elements limiting the stroke of the displaceable member, but it cannot be adopted in a system for adjusting the position of the IGV vane assembly wherein the displaceable member shall assume an indefinite number of adjusting positions without abutments.
  • the object of the present invention consists in making a system for adjusting the position of at least a control member of a power plant that can overcome or at least reduce the problems caused by the precipitation of sludge and varnish in the hydraulic fluid.
  • a system for adjusting the position of at least a control member of a power plant comprising;
  • At least one hydraulic actuator operated by a hydraulic fluid including a displaceable member connected to the control member, and having operating parameters such as the position of the displaceable member and the operating pressure;
  • At least one servo valve which includes a valve housing, is configured to control the hydraulic actuator by means of the hydraulic fluid, and is selectively operable between at least an open position for allowing fluid connection with the hydraulic actuator and a closed position for blocking fluid connection to the hydraulic actuator;
  • a by-pass fluid device to drain the hydraulic fluid from the hydraulic actuator in any position of the servo valve
  • control device configured to selectively driving the servo valve as a function of at least an operating parameter of the hydraulic actuator so as to compensate the fluid drain, and keep the operating parameter within a given range about a selected target value.
  • control device includes a monitoring device and a valve controller; the monitoring device being configured to detect at least one operating parameter, and emit a signal correlated to the operating parameter, whereas the controller is configured to drive the servo valve on the basis of said signal so as to keep the operating parameter within said given range about the selected target value.
  • the fluid bypass-device has a housing, configured to be detachably connected to the valve housing; the bypassed hydraulic fluid flowing through the housing, which preferably is a metal or metal alloy plate.
  • the housing of the fluid bypass-device and the valve housing are configured to exchange heat with each other.
  • the present invention further relates to a method for adjusting the position of at least a control member of a power plant.
  • a method for adjusting the position of at least a control member of a power plant comprising:
  • control member by means of displacing a displaceable member of a hydraulic actuator controllable by hydraulic fluid and having given operating parameters, such as the position of the displaceable member and the operating pressure;
  • a servo valve including a valve housing, and selectively operable between an open position for being in fluid connection with the hydraulic actuator and a closed position for blocking fluid connections to the hydraulic actuator,
  • controlling the servo valve to selectively operating the servo valve as a function of at least one operating parameter so as to compensate the fluid drain, and keep the operating parameter within a given range about a selected target value.
  • FIG. 1 is a schematic view, with part removed for clarity, of a system according to the present invention in a first operational position;
  • FIG. 2 is a schematic view, with part removed for clarity, of a system according to the present invention in a second operational position;
  • FIGS. 3A , 3 B, 3 C are respectively a bottom view, a top view, and a side view of a component of the system of FIG. 1 .
  • FIG. 1 with reference numeral 1 is indicated a system 1 for adjusting the position of at least a control member 2 of a power plant not shown in further details in the enclosed figures.
  • the system 1 comprises a hydraulic circuit 3 for circulating a hydraulic fluid and a control device 4 for monitoring and controlling the operations of the hydraulic circuit 3 .
  • the hydraulic circuit 3 comprises a fluid source S; a servo valve 10 ; a bypass device 20 ; a hydraulic actuator H controllable by hydraulic fluid, a fluid drain D and a number of lines connecting the above-identified components.
  • the hydraulic actuator H can be configured in many different ways, and can for example include a double acting linear hydraulic actuator H, a piston/cylinder type device, it can be part of a generator system, a turbine system.
  • the hydraulic actuator H can be pressure controlled, wherein an operating state of the hydraulic actuator H can be set or changed by (for example, temporally) adjusting pressure of hydraulic fluid that is fed to respective control ports AH, BH of the hydraulic actuator H.
  • the hydraulic actuator H comprises a displaceable member 5 , namely a piston, which is connected to control member 2 and can be displaced in two opposite directions.
  • the hydraulic actuator H has two chambers H 1 and H 2 arranged on opposite sides of the piston and connected to respective lines L. The displacement of the displaceable member 5 is function of the pressure difference in chambers H 1 and H 2 .
  • the servo valve 10 is a four way three positions sliding valve and has the function of hydraulically controlling the hydraulic actuator H.
  • valve 10 is configured to feed hydraulic fluid to the hydraulic actuator H, and to receive hydraulic fluid from the hydraulic actuator H, via respective fluid lines L.
  • the servo valve 10 comprises a housing 11 provided with first fluid ports, namely a supply port P and return (drain) port T; and second fluid ports A, B suitable to be connected to the hydraulic actuator H via the respective fluid lines L.
  • the servo valve includes a different number of first and/or second ports.
  • the servo valve 10 comprises a valve mechanism 13 namely a slider that is selectively moveable inside the valve housing 11 between a closed position to block fluid connection between the hydraulic actuator H and fluid supply S and fluid drain D as shown in FIG. 1 ; and two open positions for driving the hydraulic actuator H in two respective opposite directions (one of the two open position is shown in FIG. 2 ).
  • the servo valve 10 further includes an adjuster Q operatively connected to the valve mechanism 13 for selectively displacing the valve mechanism 13 inside the valve housing 11 .
  • the control device 4 is configured to adjust the valve mechanism 13 of the servo valve 10 , for example based on one or more signals correlated to the operating parameters of the hydraulic actuator H such as the position of the displaceable member 5 and/or the pressure in chambers H 1 and H 2 .
  • the control device 4 comprises a controller C that can be configured in different ways, for example including suitable hardware and/or software, a microcontroller, computer, or in a different manner.
  • the servo valve 10 can include one or more controllable valve adjusters Q, for example an actuator or a servo, that can adjust the operating state of the valve 10 , the adjuster Q being (for example electronically) controllable by the controller C.
  • the controller C and adjuster Q are depicted as being separate components (the controller C being located outside of the valve housing 11 , and the adjuster Q being included in the housing 11 ). Alternatively, controller and adjuster can be integrated with each other.
  • the servo valve controller C can be configured to adjust the servo valve 10 (i.e., to adjust the valve mechanism 13 ), to set the operating parameters of the hydraulic actuator H to a predetermined values
  • valve controller C can be configured to control the servo valve 10 , depending on one or more actuator related signal, relating to the detected operating parameters of the hydraulic actuator H.
  • the actuator related signal can include various types of signals, for example a control signal, sensor signal, a linear position transducer signal, a feedback signal, a signal relating to a detected functioning of the hydraulic actuator H, and/or a different type of signal.
  • the control device 4 comprises a monitoring device MH associated to the hydraulic apparatus H in order to detect the operating parameters such as the position of the displaceable member 5 or the pressures in chambers H 1 and H 2 .
  • the monitoring device MH provides the controller C with the signal correlated to at least one operating parameters.
  • the signal can relate to a piston position in case the hydraulic actuator H is a piston/cylinder type device, or a parameter that relates to the piston position.
  • it can relate to a turbine power output parameter in case the hydraulic actuator H is part of a turbine generator system.
  • the controller C and monitoring device MH are depicted as being separate components: Alternatively, controller C and device MH can be integrated with each other.
  • the valve mechanism 13 is set to a neutral state to block fluid connections between the first ports P, T and second ports A, B.
  • the valve mechanism 13 can be adjusted, from the neutral state, to at least one fluid transmission state to allow fluid connections between the first ports P, T and second ports A, B.
  • FIG. 2 shows one fluid transmission state, wherein the supply port P is in fluid connection with port B, and wherein return (drain) port T is in fluid connection with port A.
  • supply port P can be in fluid connection with supply port A, and return port T in fluid connection with port B.
  • the second fluid ports A, B of the valve are (indirectly) in fluid connection with respective ports AH, BH of the hydraulic actuator H. Also, the valve's first fluid ports P, T are in fluid connection with a fluid supply S and a fluid drain D, via respective hydraulic fluid connections s 1 and d 1 .
  • the hydraulic fluid supply S can be configured in various ways, and may for example include one or more fluid transport lines (i.e., fluid ducts, conduits), one or more fluid pumps, one or more fluid reservoirs, one or more fluid treatment devices, a filter system for filtering the hydraulic fluid, a fluid heating system to heat the fluid to a desired fluid temperature.
  • the bypass-device 20 is configured to allow fluid bypass-connection between first port T and one of the second port A, B in any operational condition of the servo valve 10 or, in other words, in any operational positions of the valve mechanism 13 .
  • the fluid bypass-device 20 comprises a first fluid bypass-connection 33 a between second ports A and the return port T that is connected to a return line d 1 ; and a second bypass-connection 33 b between second ports B and the return port T (via the return line d 1 ).
  • the fluid bypass-device 20 has a bypass housing 21 , which is configured to be detachably connected to the valve housing 11 by an optional fluid line connector plug 45 , which is depicted in dashed lines and is provided with end ports of the four fluid lines s 1 , d 2 , L leading to the source S, drain D and hydraulic actuator H.
  • a connection between the bypass housing 21 and a valve housing 11 (and optional plug 45 ) can be achieved in various ways, for example using one or more attachment devices, clamping devices, and/or suitable interconnection means.
  • the present embodiment is provided with a number of bolts 41 , for bolting the bypass housing 21 to the valve housing 11 .
  • the valve housing 11 is provided with bolt receivers 42 (configured to cooperate with bolt ends), and the by pass housing 21 include bores 46 to lead the bolts via the device housing 21 to the valve 10 .
  • the device 20 is connected to the valve housing 11 , and can provide a fluid connection between drain port T and at least one of the second port A, B.
  • the bolts 41 can be used to connect the optional fluid line connector plug to the bypass-device 20 , as well, using respective bores of the plug.
  • the bypass housing 21 of the fluid bypass-device 20 and the valve housing 11 can be configured to exchange heat with each other, particularly for thermally conditioning the valve housing 11 .
  • the fluid bypass-device 20 can be configured to be thermally conditioned by a respective bypass-fluid flowing through the fluid bypass-device 20 .
  • the by pass housing 21 is substantially a plate in which the first fluid channels ( 32 a , 32 b ), the second fluid channels ( 31 p , 31 t ) and the at least a bypass channel ( 33 a , 33 b ) are made, namely machined.
  • bypass housing 21 is made of a material having a high thermal conductivity, for example metal or metal alloy and has a temperature conditioning surface 71 that is substantially in thermal contact with a facing surface of the valve housing 11 when the device 20 is connected to the valve housing 11 , to exchange heat with the valve housing (particularly via heat conduction).
  • the bypass housing 21 has two first fluid channels 31 p , 31 t , (in particular bores machined in the bypass housing 21 ), including a source channel 31 p and return channel 31 t , that are connected with respective first fluid ports P, T of the valve 10 after assembly.
  • the device 20 also includes two second fluid channels 32 a , 32 b (in particular bores machined in the bypass housing 21 ), and connected to respective second fluid ports A, B of the valve 10 .
  • the first and second channels 31 p , 31 t 32 a , 32 b of the bypass device 20 all extend in parallel, particularly extending normally with respect to two outer surfaces 71 , 72 of the bypass housing 21 (see FIG. 3B ).
  • the present bypass-device 20 comprises four first ports p 1 , t 1 , a 1 , b 1 (located along housing surface 71 ) facing the valve housing 11 after mounting, and second ports p 2 , t 2 , a 2 , b 2 (located along housing surface 72 ) facing away from the valve housing 11 .
  • first ends of the fluid channels 31 , 32 of the bypass-device 20 provide a first source port p 1 , a first return port t 1 , and two first actuator ports a 1 , b 1 , which are connected to respective opposite ports P, T, A, B of the valve, after mounting.
  • the bypass-device 20 is provided with sealing means, for example resilient seals, for example O-rings 29 that provide sealed hydraulic connections between the first ports p 1 , t 1 , a 1 , b 1 of the bypass-unit 20 and the respective valve ports P, T, A, B.
  • the first ports p 1 , t 1 , a 1 , b 1 of the bypass-unit 20 are arranged to be in precise alignment with the respective valve ports P, T, A, B, when the device's housing 21 is mounted onto the valve housing 11 .
  • the first ports p 1 , t 1 , a 1 , b 1 can be located at the corners of a substantially square pattern (the actuator ports a 1 , b 1 being located diagonally with respect to each other, and the source and drain port p 1 , t 1 being located diagonally with respect to each other), in case the valves ports P, T, A, B are be located in such a configuration.
  • second ends of the channels 31 p , 31 t , 32 a , 32 b of the bypass-device 20 provide a second source port p 2 , a second return port t 2 , and two second actuator ports a 2 , b 2 , which are connected to respective fluid lines s 1 , d 1 , L of the system after assembly.
  • this connection can be achieved via the optional plug 45 that is provided with end ports of all the (four) fluid lines s 1 , d 2 , L leading to the source S, drain D and hydraulic actuator H.
  • the fluid lines s 1 , d 2 , L can be connected directly to the second ports p 1 , t 1 , a 2 , b 2 of the by-pass device 20 , using suitable fluid line connectors.
  • the second ports p 2 , t 2 , a 2 , b 2 of the bypass-unit are arranged to be in precise alignment (i.e. are located in a straight lines with respect to each other) with the respective first ports p 1 , t 1 , a 1 , b 1 of the bypass device 20 .
  • the bypass device 20 is arranged such, that a bypass fluid flow through the device 20 leads to a respective fluid flow (leakage flow) through the valve housing 11 .
  • the present bypass-device 20 can be mounted onto the valve ports P, T, A, B to provide fluid communication between these valve ports P, T, A, B and respective first device ports p 1 , t 1 , a 1 , b 1 ; after mounting, the bypass-device 20 provides external device ports p 2 , t 2 , a 2 , b 2 that effectively ‘replace’ the valve ports P, T, A, B, for example to receive fluid line connectors or the fluid line connector plug 45 .
  • the housing 21 of the fluid bypass-device 20 comprises a first fluid bypass channel 33 a to connect the second fluid channels 32 a (associated with actuator ports a 1 , a 2 ) to the return channel 31 t (and therefore to drain D).
  • the housing 21 of the fluid bypass-device 20 comprises a second fluid bypass channel 33 b to connect the second fluid channels 32 b (associated with the other actuator ports b 1 , b 2 ) to the return channel 31 t (and therefore to drain D).
  • the fluid bypass-channels 33 a , 33 b extend substantially transversally between the respective fluid channels 31 p , 31 t , and 32 a . 32 b (see FIG. 1-2 ).
  • the bypass device 20 is controllable to adjust a flow rate of bypass fluid flowing through a respective fluid bypass connection 33 a , 33 b .
  • the flow rate can be adjusted over a desired range, for example from zero flow rate to a certain maximum bypass fluid flow rate.
  • a channel width or diameter of each bypass channel 33 a , 33 b is adjustable (preferably in a range from zero to a maximum channel width or diameter), to set a respective bypass-flow.
  • the bypass-device 20 can include a bypass-control mechanism 25 , operable to adjust bypass flows during operation.
  • the bypass-control mechanism 25 can be automatically and/or remotely (for example electronically) controllable, for example by the controller C.
  • the bypass-control mechanism is manually controllable, and includes two manually controllable needle valve devices 25 a , 25 b , to control the flow rate through the two bypass-channels 33 a , 33 b .
  • Each needle valve device 25 a , 25 b can be set to a bypass-channel blocking state to close the respective bypass-channel 33 a , 33 b .
  • Each needle valve device 25 a , 25 b can be set to a respective opening state, allowing fluid flow via the respective bypass-channel, 33 a , 33 b , preferably such that the flow rate of the fluid flow can be set thoroughly and accurately.
  • the housing 21 support the needle valve devices 25 a , 25 b.
  • the bypass-device 20 is provided with a protecting mechanism, configured to prevent unauthorized control over the bypass-control mechanism 25 .
  • the protecting mechanism can include a blocking mechanism that can block operation of the control parts 25 , or a covering that can be locked onto the bypass-device 20 to prevent handling of the control parts 25 .
  • Operation of the embodiment can include a method to thermally condition the valve 10 .
  • the pressure of hydraulic fluid in a supply line s 1 (of the fluid supply S) that is upstream with respect to the valve 10 (and bypass-device 20 ) is higher than the pressure of hydraulic fluid in a downstream return line d 1 that leads (from return port t 2 of bypass-device 20 ) to the drain D.
  • the servo valve 10 is driven by adjuster Q on the basis of a control signal emitted by controller C in order to position the control member 2 in accordance with the operational requirements of the power plant.
  • the controller C is in connection with a control unit (not shown) of the power plant not shown in the enclosed Figures.
  • the control member is a IGV vanes assembly or a member connected to the IGV vanes assembly.
  • controller C When the control member 2 has to be set in a selected target position, controller C provides for setting the displaceable member 5 in a selected target position. When the displaceable member 5 reaches the selected target position, the servo valve 10 is set in the closed position and the hydraulic fluid does not flow through the hydraulic circuit 3 .
  • the bypass-device 20 determines a leakage in the hydraulic circuit 3 from the hydraulic actuator H towards the drain D and an instability in the position of the displaceable member 5 and the control member 2 .
  • the displacement of the displaceable member 5 from the selected target position is detected by the monitoring device MH, which emits a signal, and the controller C emits a signal as function of the displacement signal for the adjuster Q in order to displace the valve mechanism 13 from the closed position to an open position in order to restore the position of the displaceable member in the selected target position.
  • the hydraulic fluid circulates in the hydraulic circuit and stagnation of the same is prevented in particular in the servo valve 10 .
  • the controller C is provided with a given admissible range of displacement of the displacement member from a target position.
  • the range is selected so as not to impair the operation of the power plant and keeping as continuous as possible the flow of the hydraulic circuit through the hydraulic circuit 3 .
  • the same control process of the servo valve 10 can be implemented by selecting as operating parameter the pressure in the hydraulic cylinder H in particular the differential pressure in cambers H 1 and H 2 of the hydraulic cylinder H.
  • the monitoring device MH provides for detecting a first pressure in the first chamber H 1 of the hydraulic actuator H; emitting a first signal correlated to the first pressure; detecting a second pressure in the second chamber H 2 of the hydraulic actuator H; and emitting a second signal correlated to the second pressure.
  • the controller C provides for emitting a third signal correlated to the differential pressure between the first pressure and the second pressure; and controlling the servo valve 10 on the basis of the third signal so as to keep the differential pressure in the hydraulic actuator H within a given range about the selected target value.
  • the selected target value allows keeping the displaceable member 5 in the selected target position or at least in a given acceptable range about the selected target position.
  • control process can be implemented using both position signal and pressure signal.
  • the bypass device induces a change in the operating parameters of the hydraulic actuator H.
  • the change is automatically counteracted by the control device 4 , by setting the valve 10 into a respective fluid transmission mode (as in FIG. 2 ), such, that high pressure fluid from the source S cancels (and even temporarily reverses) a fluid pressure drop experienced at the hydraulic actuator H due to the fluid bypass.
  • the valve 10 is controlled such that pressures in the hydraulic actuator H control lines L are restored to stationary pressure values that provide the desired (for example predetermined) operating parameters.
  • the system can experience a continuous fluid bypass-flow, flowing through the valve 10 and bypass-device 20 , when the actuator H is in a desired (for example stationary) operating condition to perform a respective actuator function, without the servo valve 10 being in a neutral state.
  • the bypass flow flows through the valve 10 , and bypasses the actuator H (i.e. the bypass flow does not particularly flow to and from the actuator's fluid ports AH, BH).
  • the system 1 provides to keep the hydraulic fluid flowing through the servo valve 10 and to thermally condition the servo valve 10 using hydraulic bypass fluid flow.
  • a temperature of the hydraulic bypass fluid supplied from the source S
  • the bypass fluid flow can lead to the valve mechanism 13 being in a fluid transmission state during a predetermined (for example stationary) operating state of the hydraulic actuator H.
  • heat is supplied to the servo valve 10 utilizing warm hydraulic fluid, particularly by setting the valve in a fluid transmission state.
  • operation of the system can include a method to thermally condition a servo valve.
  • the valve controller C can adjust the valve mechanism of the servo valve depending on one or more signals relating to a working condition of the hydraulic actuator H.
  • operation can then include supplying heat to the valve when the valve is in its neutral valve state.
  • heat can be supplied utilizing dedicated heating means, for example one or more electrical heating devices (not shown) integrated with or mounted on the valve housing 11 .
  • the heater can be configured to heat the valve housing to a temperature higher than 40° C., for example at least 50° C.
  • the present bypass-device 20 can create a defined hydraulic fluid flow through the valve component and the associated hydraulic system under various operating conditions.
  • the hydraulic fluid flow can thermally condition various components of the system, specifically in case the system is controlled to operate discontinuously (for example, in case the controller C controls the servo valve 10 to maintain a certain valve state during a substantial part of an operating period).
  • the servo valve 10 is controlled to maintain a certain valve state during a large operational period of at least one hour, particularly at least several hours, more particularly at least 24 hours.
  • the servo valve 10 can be controlled to maintain a certain valve state during at least 99% of a total operational life-time of the valve (i.e., most of the time, the servo valve 10 holds a certain desired operative valve state, to hydraulically control an hydraulic actuator H that is coupled to the valve 10 ). Then, preferably, the bypass-device 20 is set to ensure that a hydraulic bypass-flow (‘leakage’ flow) flows through the servo valve 10 during such a long period, to thermally condition the valve. In this way, precipitation of certain oxidation products (such as sludge and varnish) in the hydraulic system and its components can be prevented surprisingly well.
  • a hydraulic bypass-flow ‘leakage’ flow

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
US13/121,127 2008-09-26 2009-09-25 System and method for adjusting the position of a control member of a power plant Abandoned US20110240152A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
NL2002025A NL2002025C (en) 2008-09-26 2008-09-26 Hydraulic system, and a method to thermally condition a valve.
NLN2002025 2008-09-26
PCT/EP2009/062435 WO2010034804A1 (en) 2008-09-26 2009-09-25 System and method for adjusting the position of a control member of a power plant

Publications (1)

Publication Number Publication Date
US20110240152A1 true US20110240152A1 (en) 2011-10-06

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US13/121,127 Abandoned US20110240152A1 (en) 2008-09-26 2009-09-25 System and method for adjusting the position of a control member of a power plant

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US (1) US20110240152A1 (nl)
EP (1) EP2329152A1 (nl)
NL (1) NL2002025C (nl)
WO (1) WO2010034804A1 (nl)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10267426B2 (en) 2016-06-01 2019-04-23 B/E Aerospace, Inc. Valve assembly and method of operating same
US20240271540A1 (en) * 2023-02-15 2024-08-15 MTU Aero Engines AG Adjustment system for a compressor

Citations (2)

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US4513835A (en) * 1982-04-30 1985-04-30 Nissan Motor Company, Limited Steering control apparatus
US20070278797A1 (en) * 2006-05-31 2007-12-06 Flannery Patrick S Power conditioning architecture for a wind turbine

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US3245424A (en) * 1963-05-31 1966-04-12 Olsen Zenny Servo valve
US3885389A (en) * 1973-09-26 1975-05-27 Melvin Corp Manifold with internal filter
SU635297A1 (ru) * 1977-01-03 1978-11-30 Московский Автомобильно-Дорожный Институт Электрогидравлический сервомеханизм
JPS5821003A (ja) * 1981-07-30 1983-02-07 Hitachi Constr Mach Co Ltd シリンダ作動用油圧回路
JPS6387304U (nl) * 1986-11-28 1988-06-07
DE102005053265B4 (de) * 2005-11-08 2020-07-09 Linde Hydraulics Gmbh & Co. Kg Hydrostatisches Antriebssystem
DE112008000439A5 (de) * 2007-02-16 2009-12-03 Robert Bosch Gmbh Steuerbock

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Publication number Priority date Publication date Assignee Title
US4513835A (en) * 1982-04-30 1985-04-30 Nissan Motor Company, Limited Steering control apparatus
US20070278797A1 (en) * 2006-05-31 2007-12-06 Flannery Patrick S Power conditioning architecture for a wind turbine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10267426B2 (en) 2016-06-01 2019-04-23 B/E Aerospace, Inc. Valve assembly and method of operating same
US20240271540A1 (en) * 2023-02-15 2024-08-15 MTU Aero Engines AG Adjustment system for a compressor

Also Published As

Publication number Publication date
EP2329152A1 (en) 2011-06-08
NL2002025C (en) 2010-03-29
WO2010034804A1 (en) 2010-04-01

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