WO2023059560A1 - Régulateur de débit constant - Google Patents

Régulateur de débit constant Download PDF

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Publication number
WO2023059560A1
WO2023059560A1 PCT/US2022/045560 US2022045560W WO2023059560A1 WO 2023059560 A1 WO2023059560 A1 WO 2023059560A1 US 2022045560 W US2022045560 W US 2022045560W WO 2023059560 A1 WO2023059560 A1 WO 2023059560A1
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WO
WIPO (PCT)
Prior art keywords
flow
fluid
port
actuator
control device
Prior art date
Application number
PCT/US2022/045560
Other languages
English (en)
Inventor
Michael L. Hahn
Brett FLANNERY
Original Assignee
Woodward, Inc.
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 Woodward, Inc. filed Critical Woodward, Inc.
Priority to CN202280063337.XA priority Critical patent/CN117980596A/zh
Priority claimed from US17/958,727 external-priority patent/US11808287B2/en
Publication of WO2023059560A1 publication Critical patent/WO2023059560A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/22—Fuel supply systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C9/00—Controlling gas-turbine plants; Controlling fuel supply in air- breathing jet-propulsion plants
    • F02C9/26—Control of fuel supply
    • F02C9/36—Control of fuel supply characterised by returning of fuel to sump

Definitions

  • This invention generally relates to a fluid flow system and, in particular, to a fluid flow system providing an adjustable leak path to reject disturbances associated with slewing of an actuator.
  • electrohydraulic servo valves are often used to control the amount of flow going through the variable flow device.
  • the variable flow device may be a variable displacement pump, and the EHSV may mechanically position a variable pumping member to increase or decrease the flow.
  • the EHSV often uses high pressure fluid on the outlet side of the variable flow device as a hydraulic fluid for creating the mechanical actuation to position the variable pumping member. This form of actuation creates a slew flow in the EHSV that causes a large disturbance in the outlet flow of the variable flow device.
  • Embodiments of the presently disclosed invention address the foregoing problems and issues associated with conventional variable flow systems.
  • embodiments of the presently disclosed flow system utilize a pressure regulator to set a relatively constant flow across a tunable orifice so that any slew flow to move an EHSV actuator is compensated by having the regulator close, reducing its leakage, to maintain the constant flow across the orifice and therefore constant flow out of the pumping unit.
  • the only input to the compensation provided by the pressure regulator is actual slew flow from the EHSV, making it insensitive to any other changes or disturbances in the system.
  • the compensating pressure regulator Because the only input to the compensating pressure regulator is the slew flow for which the compensation is provided, the potential for error resulting from other system factors is substantially reduced or completely eliminated. Further, the orifice allows the system to be tunable for only the slew flow for which compensation is desired, thereby limiting the amount of additional leakage in the system.
  • the system includes a flow source device having an inlet and an outlet.
  • the inlet is configured to receive fluid at a first pressure
  • the outlet is configured to output the fluid at a second pressure that is higher than the first pressure.
  • the system also includes a fluid control device having an inlet port and a drain port.
  • the inlet port of the fluid control device is configured to receive flow from the outlet of the flow source device.
  • the system includes a constant flow regulator configured to provide a leakage flow to a drain output. The constant flow regulator is configured to decrease the leakage flow in response to the drain port of the fluid control device.
  • the constant flow regulator includes a pressure regulating valve (PRV). Further, the PRV includes a PRV inlet in fluid communication with the outlet of the flow source device and a PRV outlet in fluid communication with a first fluid line extending from the drain port of the fluid control device. In addition, the constant flow regulator incorporates a restriction positioned on a second fluid line downstream of the PRV outlet and the first fluid line.
  • PRV pressure regulating valve
  • the system includes an actuator actuated by the fluid control device, an electro-hydraulic servo valve (EHSV), which uses fluid from the flow source device to actuate the actuator.
  • EHSV electro-hydraulic servo valve
  • the EHSV includes a valve body defining a valve bore, the inlet port, the drain port, a first working port, and a second working port.
  • the EHSV also includes a valve member disposed within the valve bore.
  • the valve member is configured to translate within the valve bore to provide communication between the inlet port and the first working port and between the second working port and the drain port, or between the first working port and the drain port and between the inlet port and the second working port. Further, the fluid flow from the inlet port through the first working port actuates the actuator in a first direction, and the fluid flow from the inlet port through the second working port actuates the actuator piston in a second direction opposite to the first direction.
  • the system includes a position sensor configured to detect the movement of the actuator.
  • the actuator is a linear actuator.
  • the actuator is a rotary actuator.
  • the actuator is disposed within a housing.
  • the housing further includes a first chamber coupled to the first working port and a second chamber coupled to the second working port.
  • the constant flow regulator is configured to decrease the leakage flow in proportion to the fluid flow from the first or second working port to the drain port.
  • the fluid control device is driven by a stepper motor, a direct drive motor, or a hydro-mechanical pilot valve.
  • the flow source device includes a variable displacement pump.
  • variable displacement pump is a vane pump.
  • variable displacement pump is a piston pump.
  • the flow source device is a fuel metering system.
  • embodiments of the present disclosure provide a method of compensating for flow disturbances associated with a changing flow rate in a fluid flow system.
  • fluid at a first pressure is received at an inlet of a flow source device.
  • the fluid is output at a second pressure higher than the first pressure from an outlet of the flow source device.
  • a portion of the fluid at the second pressure is received through an inlet port of a fluid control device to actuate an actuator.
  • a leakage flow is provided to a drain output through a constant flow regulator.
  • the constant flow regulator is configured to decrease the leakage flow in response to a drain flow from a drain port of the fluid control device when the actuator is actuated.
  • the constant flow regulator includes a pressure regulating valve (PRV) and a restriction.
  • PRV pressure regulating valve
  • the leakage flow is provided from a PRV inlet in fluid communication with the outlet of the flow source device through a PRV outlet in fluid communication with a first fluid line extending from an outlet port of the fluid control device. Further, the flow is restricted from the PRV outlet and the drain port of the fluid control device.
  • the fluid control device is electro- hydraulically driven, and the portion of the fluid through the inlet port of the fluid control device is used to move the actuator.
  • the fluid control device includes a valve body defining a valve bore, the inlet port, the drain port, a first working port, and a second working port.
  • the fluid control device further includes a valve member disposed within the valve bore. The valve member is translated within the valve bore to provide fluid communication between the inlet port and the first working port and between the second working port and the drain port, or between the first working port and the drain port and between the inlet port and the second working port. Further, the actuator is moved in a first direction when fluid flows from the inlet port through the first working port or in a second direction when fluid flows from the inlet port through the second working port.
  • the leakage flow is decreased through the constant flow regulator in proportion to the fluid flow from the first working port to the drain port or from the second working port to the drain port.
  • the actuator is linked to the flow source device, and a flow control member of the flow source device is moved in response to movement of the actuator.
  • FIG. 1 is a schematic depiction of a variable flow system, according to an exemplary embodiment
  • FIG. 2 is graph showing disturbances in output flow as a result of slew flow through an actuator valve for the presently disclosed variable flow system, according to an exemplary embodiment, and for a conventional variable flow system;
  • FIG. 3 depicts a generalized schematic of a variable flow system, according to an exemplary embodiment.
  • FIG. 1 depicts an embodiment of a flow system 10, such as a fuel control system (e.g., for an aircraft).
  • the flow system 10 includes a flow source device 12 that receives low pressure fluid PB on a first fuel line 14, and the flow source device 12 ejects high pressure fluid Ps on a second line 16.
  • the high pressure fluid Ps is provided to an output 18 through which the fluid is provided to a downstream process, such as a fuel manifold and combustion chamber (not shown) for an exemplary embodiment of a fuel system.
  • the pressure Ps of the fluid may be set by nozzles of the fuel manifold that eject fuel into the combustion chamber.
  • the downstream process may need fluid of variable pressure, and the flow source device 12 regulates the flow of the fluid.
  • the high pressure fluid Ps ejected from the flow source device 12 is utilized by a fluid control device 20, depicted as an electrohydraulic servo valve (EHSV). While the fluid control device 20 is depicted as being electro-hydraulically driven, the fluid control device 20 could instead be hydraulically driven or hydro-mechanically driven. For example, in embodiments, the fluid control device 20 may be driven by a stepper motor, direct drive motor, or hydro-mechanical pilot valve, among other possibilities.
  • the fluid control device 20 includes an actuator control valve 22 having a valve member 24, such as a spool valve, disposed within a valve bore 26 of a valve body 28. The valve body 26 defines an inlet port 30 and a drain port 34 of the valve bore 26.
  • the valve body 26 also defines a first working port 36 and a second working port 38.
  • the inlet port 30 is in fluid communication with the high pressure fluid Ps through a third line 39.
  • the position of the valve member 24 within the valve bore 26 controls the flow of the high pressure fluid Ps from the inlet port 30 to one of the respective first or second working ports 36, 38 and from the other of the working ports 36, 38 to the drain port 34.
  • the actuator control valve 22 includes a first nozzle 40 and a second nozzle 42 that each receive high pressure fluid Ps from the third line 39 through the inlet port 30 and through respective restrictions 43.
  • the nozzles 40, 42 inject high pressure fluid into an actuator control valve chamber 44.
  • Disposed within the valve chamber 44 is a flapper 46 that is connected to an armature 48 of a torque motor 50.
  • the torque motor 50 can be actuated to tilt the armature 48, which in turn tilts the flapper 46 towards one of the nozzles 40, 42. If the flapper 46 is tilted toward the first nozzle 40, then the valve member 24 shifts to the right (with respect to the orientation depicted in FIG.
  • actuator 51 which is depicted as a piston 52.
  • the actuator 51 is a linear actuator, such as the depicted piston 52, and in one or more other embodiments, the actuator 51 is a rotary actuator, such as a rotary vane actuator.
  • the piston 52 is disposed within a housing 54 having a first chamber 56 disposed on one side of the piston 52 and a second chamber 58 disposed on the opposite side of the piston 52.
  • the first working port 36 is fluidly coupled to the first chamber 56 through a fourth line 60
  • the second working port 38 is fluidly coupled to the second chamber 58 through a fifth line 62.
  • high pressure fluid Ps is provided, for example, from the inlet port 30 to the second working port 38, the fluid flows through the fifth line 62 into the second chamber 58, forcing the piston 52 to the left (with respect to the orientation depicted in FIG. 1).
  • the movement of the piston 52 decreases the volume of the first chamber 56, forcing fluid through the fourth line 60 into the first working port 36 and out of the drain port 34.
  • the movement of the piston 52 is sensed by a position sensor of a linear actuator, which is depicted as a linear variable differential transformer (LVDT) 64.
  • LVDT linear variable differential transformer
  • the flapper 46 is connected to a feedback spring 66, which is connected to the valve member 24 and which senses the position of the valve member 24.
  • both nozzles 40, 42 inject fluid into the actuator control valve chamber 44, which flows out through the drain port 34. Flow into the valve bore 26 from the inlet port 30 and from the working ports 36, 38 is blocked. Thus, in this configuration, the valve member 24 and the piston 52 are in a centered or null position.
  • the condition of the actuator control valve 22 can be determined and controlled to actuate the actuator 51.
  • the actuator 51 may be used to position flight control surfaces of an aircraft.
  • the actuator control valve 22 and actuator 51 may be used to regulate the flow source device 12.
  • the actuator 51 is mechanically, hydraulically, or pneumatically linked to the flow source device 12.
  • the piston 52 is able to move the rotor or the surrounding cam ring (for a vane pump) or to change the angle of a swash plate (for a piston pump) to increase or decrease the flow supplied by the variable displacement pump flow source device 12.
  • the piston 52 is electrically sensed and used to position the flow source device 12.
  • the LVDT 64 is able to control the flow output through a controller to regulate position and/or pump flow.
  • the flow system 10 includes a constant flow regulator 68 that provides a leak path from the flow source device 12 to a drain output 69, such as the low pressure side of the flow source device 12, a fluid reservoir (e.g., a fuel tank), or a low pressure sump.
  • a constant flow regulator 68 that provides a leak path from the flow source device 12 to a drain output 69, such as the low pressure side of the flow source device 12, a fluid reservoir (e.g., a fuel tank), or a low pressure sump.
  • the constant flow regulator 68 includes a pressure regulating valve 70 and a restriction 72.
  • the pressure regulating valve 70 includes a valve member 74 that translates within a housing 76.
  • On one side of the valve member 74 is a valve chamber 78 and a biasing member, such as a spring 80.
  • the spring 80 biases the valve member 74 towards the closed position to control fluid flow through outlet 81.
  • On the other side of the valve member 74 is a first inlet 82 configured to receive high pressure fluid Ps from the second line 16 on the output side of the flow source device 12.
  • the high pressure fluid Ps bypasses the valve member 74 to the outlet 81 to provide a constant leakage flow.
  • the pressure regulating valve 70 includes a second inlet 84 in fluid communication with the drain port 34 of the fluid control device 20 via a sixth line 86.
  • the second inlet 84 is also in fluid communication with a seventh line 88.
  • Disposed in the seventh line 88 is a restriction 72 leading to the drain output 69.
  • FIG. 2 provides a graph of the change in flow rate between the output 18 and the outlet of the flow source device 12 for a flow system 10 according to the present disclosure and for a conventional flow system.
  • the y-axis of the graph represents the change in flow rate at the output 18 (instantaneous flow rate - initial flow rate) minus the change in flow rate at the outlet of the flow source device 12 (instantaneous flow rate - initial flow rate).
  • the value of “0” means that the changes in flow rates at each location match.
  • x-axis represents time. At time, Ti the fluid control device 20 is actuated in a first direction by providing current flow to the torque motor 50, and at time T2, the fluid control device 20 is actuated in a second direction by providing opposite current flow to the torque motor 50.
  • the first actuation of the fluid control device at time Ti causes a significant change in flow rates between the outlet of the flow control device and the output for the conventional flow system.
  • the negative value of the change in flow rate demonstrates that the change in flow rate at the outlet of the flow source device is much greater than the change in flow rate at the output.
  • the lower change in the flow rate at the output is attributed to the slew flow associated with actuation of the actuator control valve preventing the output from experiencing the same change in flow rate.
  • the fluid control device is again actuated (in the reverse direction), and this actuation creates slew flow through the actuator, which again creates a substantial disturbance in the flow at the output.
  • the changes in flow rates between the output and the outlet of the flow control system again equalize. Any further actuation of the conventional flow system would causes a similar disturbance in the rate of the flow system.
  • FIG. 2 demonstrates that the changes in flow rates for the presently disclosed flow system 10 are much smaller in magnitude.
  • the fluid control device 20 is actuated, creating a slew flow, but in contrast to the conventional flow system, the slew flow is compensated because of the leakage flow already present in the system. That is, the consistent leakage flow built into the system is replaced by the slew flow caused by actuation of the fluid control device 20.
  • the constant flow regulator 68 provides a consistent leak path, and the pressure regulating valve 70 senses the slew flow from the fluid control device 20 and shuts off or diminishes leakage flow from the second line 16 in response to the sensed slew flow.
  • the changes in flow rates between the output 18 and the outlet of the flow source device 12 is positive at the first actuation of the actuator control valve at time Ti, meaning that the change in flow rate at the output 18 is actually greater than at the outlet of the flow source device 12 primarily due to the compressibility effects of the fluid (although system size and total compressibility will affect magnitude of this phenomenon).
  • the magnitude of the changes is significantly smaller than in the conventional flow control system.
  • the fluid control device 20 is actuated in the reverse direction at time T2
  • the presently disclosed flow system 10 experiences changes in flow rates that are much smaller in magnitude than in the conventional system.
  • the absolute value of the magnitude of the changes in flow rate is 50% or less, preferably 30% or less, more preferably 25% or less, and most preferably 20% or less, than the absolute value of the magnitude of the changes in flow rate for the conventional system.
  • FIG. 3 provides a generalized schematic diagram of the flow control concept.
  • the flow source device 12 receives input flow of a fluid at a first pressure PB and outputs fluid flow at a second pressure Ps that is higher than the first pressure.
  • the flow source device 12 is a pump, such as a variable displacement pump (e.g., a rotary vane or piston pump), or a fuel metering valve, amongst other possibilities.
  • the fluid control device 20 utilizes flow from the flow source device 12 to control an actuator 51.
  • the fluid control device 20 is driven electro- hydraulically, electro-mechanically, pneumatically, hydraulically, or mechanically to position the actuator.
  • the fluid control device 20 includes an actuator control valve 22 that is translated using, e.g., a stepper motor, a direct drive motor, or a hydro-mechanical pilot valve.
  • the actuator control valve 22 may be translated by a stepper motor having a drive shaft mechanically connected to a cam (e.g. in place of flapper 46 shown in FIG. 1) to directly position the cam in relation to the nozzles 40, 42 of the actuator control valve 22 (as shown in FIG. 1).
  • the constant flow regulator 68 positioned at the outlet of the fluid control device 20.
  • the constant flow regulator 68 provides leakage flow to a drain output, such as the inlet of the flow source device 12, a fluid reserve tank (e.g., a fuel tank), or another low pressure sump.
  • a drain output such as the inlet of the flow source device 12, a fluid reserve tank (e.g., a fuel tank), or another low pressure sump.
  • the leakage flow through the constant flow regulator 68 is present regardless of the state fluid control device 20 (that is, there is always at least some leakage flow through the constant flow regulator 68).
  • the leakage flow Prior to actuation of the fluid control device 20, the leakage flow is provided from the outlet of flow source device 12 through the constant flow regulator 68.
  • the slew flow associated with actuation of the fluid control device 20 replaces the leakage flow of the outlet of the flow source device 12. In this way, the reduction in the leakage flow from the outlet of the flow source device 12 compensates for fluid from the outlet of the flow source device 12 utilized to actuate the fluid control device 20.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Flow Control (AREA)

Abstract

L'invention concerne un système conçu pour compenser des perturbations d'écoulement lors du changement d'un débit dans le système, le système incluant un dispositif de source d'écoulement (12) ayant une entrée et une sortie. L'entrée est conçue pour recevoir un fluide à une première pression et la sortie est conçue pour délivrer le fluide à une seconde pression qui est supérieure à la première pression. Le système inclut également un dispositif de commande de fluide (20) ayant un orifice d'entrée (30) et un orifice de vidange (34). L'orifice d'entrée du dispositif de commande de fluide est conçu pour recevoir un écoulement à partir de la sortie du dispositif de source d'écoulement. En outre, le système inclut un régulateur de débit constant (68) conçu pour fournir un écoulement de fuite à une sortie de vidange (69). Le régulateur de débit constant est conçu pour réduire l'écoulement de fuite en réponse à l'orifice de vidange du dispositif de commande de fluide.
PCT/US2022/045560 2021-10-04 2022-10-03 Régulateur de débit constant WO2023059560A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202280063337.XA CN117980596A (zh) 2021-10-04 2022-10-03 恒流调节器

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US202163252031P 2021-10-04 2021-10-04
US63/252,031 2021-10-04
US17/958,727 US11808287B2 (en) 2021-10-04 2022-10-03 Constant flow regulator
US17/958,727 2022-10-03

Publications (1)

Publication Number Publication Date
WO2023059560A1 true WO2023059560A1 (fr) 2023-04-13

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6102001A (en) 1998-12-04 2000-08-15 Woodward Governor Company Variable displacement pump fuel metering system and electrohydraulic servo-valve for controlling the same
US20180038503A1 (en) * 2016-08-04 2018-02-08 Woodward, Inc. Stepper motor driven proportional rotary actuator
US20210079855A1 (en) * 2019-07-04 2021-03-18 GE Aviation Czech S.R.O. Propeller assembly and pitch control unit
US20210277920A1 (en) * 2020-03-05 2021-09-09 Honeywell International Inc. System that maintains the last commanded position of device controlled by a two-stage, four-way electrohydraulic servo valve upon power interruption

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6102001A (en) 1998-12-04 2000-08-15 Woodward Governor Company Variable displacement pump fuel metering system and electrohydraulic servo-valve for controlling the same
US20180038503A1 (en) * 2016-08-04 2018-02-08 Woodward, Inc. Stepper motor driven proportional rotary actuator
US20210079855A1 (en) * 2019-07-04 2021-03-18 GE Aviation Czech S.R.O. Propeller assembly and pitch control unit
US20210277920A1 (en) * 2020-03-05 2021-09-09 Honeywell International Inc. System that maintains the last commanded position of device controlled by a two-stage, four-way electrohydraulic servo valve upon power interruption

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