EP1531271A2 - Système de contrôle de capacité d'une pompe à combustible - Google Patents

Système de contrôle de capacité d'une pompe à combustible Download PDF

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Publication number
EP1531271A2
EP1531271A2 EP04026703A EP04026703A EP1531271A2 EP 1531271 A2 EP1531271 A2 EP 1531271A2 EP 04026703 A EP04026703 A EP 04026703A EP 04026703 A EP04026703 A EP 04026703A EP 1531271 A2 EP1531271 A2 EP 1531271A2
Authority
EP
European Patent Office
Prior art keywords
pressure
pump
output
fuel
recited
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP04026703A
Other languages
German (de)
English (en)
Inventor
Mihir C. Desai
William H. Dalton
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Goodrich Pump and Engine Control Systems Inc
Original Assignee
Goodrich Pump and Engine Control Systems 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 Goodrich Pump and Engine Control Systems Inc filed Critical Goodrich Pump and Engine Control Systems Inc
Publication of EP1531271A2 publication Critical patent/EP1531271A2/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • F04C14/226—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam by pivoting the cam around an eccentric axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1204—Position of a rotating inclined plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1205—Position of a non-rotating inclined plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1213—Eccentricity of an outer annular cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/20—Flow

Definitions

  • the subject invention is directed generally to a system for regulating fluid flow, and more particularly, to a system for regulating the flow of liquid fuel from a variable displacement pump to a gas turbine by utilizing bypass flow.
  • Variable displacement fuel pumps have partially overcome the drawbacks of fixed delivery pumps by being able to vary the amount of fuel output. By varying the fuel output, the fuel delivered more closely matches engine demand. Thus, the recirculated flow, along with the heat generated thereby, is reduced.
  • Variable displacement fuel pumps are known in the art as disclosed in U.S. Patent No. 5,833,438 to Sunberg, the disclosure of which is herein incorporated by reference in its entirety.
  • a variable displacement pump typically includes a rotor having a fixed axis and pivoting cam ring. Controlling the position of the cam ring with respect to the rotor controls the output of the pump. The output flow may be controlled by a torque motor operated servo valve.
  • variable displacement pump control arrangements are disclosed in U.S. Patent Nos. 5,716,201 to Peck et al. and 5,715,674 to Reuter et al., the disclosures of which are herein incorporated by reference in their entirety.
  • These pump control systems attempt to maintain accurate fuel flow throughout the range of engine operating conditions. However, as noted above, such systems still contain inadequacies such as complexity. Moreover, such systems can only achieve adequate bandwidth by delivering excessive fuel which must be recirculated. It is also undesirable for pump control systems to include sophisticated electronics and numerous additional components that undesirably increase costs and complexity.
  • the subject invention is directed to a flow control system for controlling a variable displacement pump including a metering valve in fluid communication with the pump for metering an output of the pump.
  • a regulating valve for maintaining a pressure differential across the metering valve receives a portion of the output of the pump as a bypass flow at a first pressure, wherein an output of the regulating valve is at an interim pressure, wherein the interim pressure is equal to an approximate average of the first pressure and a low reference pressure.
  • An actuator sets a displacement of the pump by acting on a piston connected to a cam ring of the pump. The setting of the actuator is determined by a differential between the interim pressure and a second portion of the output of the pump at the first pressure.
  • the subject invention is directed to a method for metering a variable displacement pump that provides fuel to an engine, the method includes the steps of receiving fuel at a low reference pressure into the variable displacement pump, pumping the fuel through the pump such that an output of the pump is at an elevated pressure, metering the output of the variable displacement pump with a metering valve, creating a spill return flow from the output of the variable displacement pump to allow for quick response when additional fuel is required by the engine, regulating a pressure differential across the metering valve with a regulating valve.
  • the regulating valve is in fluid communication with the spill return flow to generate an interim pressure substantially equal to an average of the spill return and the low reference pressure.
  • the method also includes the step of adjusting a displacement of the pump with a cam actuator connected to a cam ring of the variable displacement pump for adjusting the output, wherein the cam actuator receives the interim pressure to determine a setting of the cam actuator.
  • the Sole Figure is a schematic representation of a flow control system constructed in accordance with the subject invention.
  • a flow control system in accordance with the subject invention which is designated generally by reference numeral 10.
  • arrows are shown within the lines of system 10 to indicate the direction in which the fuel flows and an annotated letter "P" is shown to indicate a pressure at certain locations. All relative descriptions herein such as left, right, up, and down are with reference to the system 10 as shown in the Sole Figure and not meant in a limiting sense. Additionally, for clarity common items such as filters and shut off solenoids have not been included in the Sole Figure.
  • the system 10 maintains the output flow of a variable vane displacement pump 12 to provide fast response to engine needs in a stable manner yet excessive complexity is avoided.
  • the pump 12 includes a rotor 14 and a pivoting cam ring 16.
  • the pump 12 receives fuel flow at an inlet pressure P AF , and delivers fuel flow at an output pressure P F .
  • a piston 18 is operatively connected to the cam ring 16 to control the position of the cam ring 16 relative to the rotor 14 and, thereby, vary the output flow of the pump 12.
  • a cam actuator assembly 20 positions the piston 18 as described below.
  • the maximum flow setting of the pump 12 occurs when the piston 18 is moved the maximum distance to the left.
  • a feedback line 21 in fluid communication with the output of the pump 12 provides fuel at pressure P 1W to a line 29 connected to an inlet 22 of the cam actuator 20. Orifices 24 and 26 limit the flow into line 29.
  • the pressure in line 29 is approximately equal to P 1W + P AF divided by two, and designated as P I1 in the Sole Figure. It will be appreciated by those of ordinary skill in the art that the pressure at P 1W will be substantially equal to the pressure P F .
  • the feedback line 21 also provides fuel at pressure P 1W to other locations not shown such as the engine geometry, main metering valve and bleed band servos (not shown) as required. Line 29 also connects to low reference pressure P AF .
  • Another inlet 28 of the cam actuator 20 receives fuel at an interim pressure P I2 as will be described hereinbelow.
  • a housing 23 of the cam actuator 20 retains the piston 18 for dividing the interior of the housing 23.
  • a coiled spring 30 biases the piston 18.
  • the pressure on the right side of the piston 18 is approximately equal to the average of P 1W and P AF .
  • the combination of the pressure differential between the right and left sides of the housing 23 together with the sizing of a spring 30 act to position the piston 18 within the cam actuator 20.
  • the cam ring 16 moves correspondingly and the output of the pump 12 varies.
  • the spring 30 is sized and configured to position the piston 18 at maximum flow for start-up of the pump 12.
  • springs are sized as a function of the product of piston area and fuel pressure as would be appreciated by those of ordinary skill in the art and therefore not further described herein.
  • the output of the pump 12 passes through a wash filter 32 for cleaning debris prior to entering a main metering valve 34 and line 21.
  • the main metering valve 34 is disposed between the pump 12 and engine (not shown) for providing fuel to the engine at a selected rate and pressure P M .
  • the main metering valve 34 insures that P F is greater than P M by some preselected, substantially constant value. Suitable main metering valves 34 are well known in the prior art and therefore not further described herein.
  • the preferred metering valve 34 performs the function of selectively varying the amount of fuel passing therethrough.
  • the main metering valve 34 receives fuel at pressure P F and the fuel exits at pressure P M .
  • a line 35 connects the output of the pump 12 to a bypassing pressure regulator valve assembly 36.
  • the flow in line 35 is referred to as the spill return flow at Pressure P F .
  • the regulator valve assembly 36 includes a housing 38 defining an interior with a spring-biased spool 40 operatively disposed therein. A left face of the spool 40 has fuel at pressure P F there against.
  • a metering head adjustment screw 42 is attached to the spool 40 for calibrating the position of the spool 40 within the regulator valve assembly 36 during set up.
  • the housing 38 defines an inlet 44 connected to line 35 for receiving fuel at pressure P F .
  • Another inlet 46 of the housing 38 receives fuel at pressure P M from static flow line 37 to dampen the motion of the spool 40.
  • An orifice 48 is disposed in the line 37 for dampening.
  • the housing 38 also defines a restricting outlet 50 for the fuel to exit from the regulator valve assembly 36.
  • the outlet 50 is in fluid communication with the inlet 28 of the pump 12 via line 51.
  • Line 51 also connects the low reference pressure P AF , wherein an orifice 52 limits the flow to the low reference pressure P AF .
  • the pressure within line 51 is approximately equal to the average of P F and P AF , hereinafter designated the interim pressure P I2 .
  • the combination of the pressure differential between P F on the left side of the housing 40 and P M on the right plus the spring-biasing of the spool 40 ultimately positions the spool 40.
  • the left side of regulator valve assembly 36 and the right side of the cam actuator 20 are at approximately the same pressure.
  • the recirculation flow through the regulator valve assembly 36 is maintained at a low level by the spool 40 partially blocking the outlet 50 yet the system 10 can rapidly and sufficiently respond to transient events.
  • the spool 40 within the regulator valve assembly 36 is maintained substantially at a nominal position during normal operation. In most modem engines, the variation in fuel demand as a result of running the engine is relatively minor compared to that associated with the slewing of engine geometries.
  • a transient event When a transient event occurs, the pump 12 must produce more fuel rapidly.
  • a transient event would be an actuator motion by utilization of the slewing source at pressure P 1W in line 21.
  • Increased demand by the transient event causes the main metering valve 34 to respond by opening to immediately increase flow to the engine and starts a chain of events which leads to an increase in the output of the pump 12.
  • the pump 12 cannot immediately respond with increased displacement so the incremental demand comes from diminished spill return flow in line 35.
  • the pressure P M increases and the Pressure P F decreases (i.e., a drop of the pressure differential (P F -P M ) across the main metering valve 34).
  • the regulator valve assembly 36 senses the pressure differential drop and the spool 40 strokes to the left.
  • the pressure in the outlet 50 is decreased and, in turn, the pressure into the left side of the cam actuator 20 drops.
  • the decrease in pressure of the left side of the cam actuator 20 causes the piston 18 to stroke to the left.
  • the output of the pump 12 increases.
  • the increased pump output raises the pressure P F until the pressure differential across the main metering valve 34 returns to the nominal steady-state level and the steady-state condition is reattained.
  • the main metering valve 20 responds by closing to decrease flow to the engine and starts a chain of events which leads to a decrease in the output of the pump 12.
  • the pump 12 cannot immediately respond with decreased displacement so the decreased demand results in a decrease of pressure P M and an increase in Pressure P F (i.e., a rise of the pressure differential (P F -P M ) across the main metering valve 34) to allow the system 10 to immediately respond.
  • the regulator valve assembly 36 senses the pressure differential rise and the spool 40 strokes to the right. As a result, the pressure in the outlet 50 is increased and, in turn, the pressure into the left side of the cam actuator 20 rises.
  • the regulator valve assembly 36 is used to minimize the recirculation flow, while allowing the system 10 to respond quickly to transient demands.
  • the recirculation flow is regulated and the position of the spool 40 is at a substantially nominal position during steady-state operation. Pressures substantially equal to the average of the low reference pressure and output pressure of the pump are utilized to set the regulator valve and cam actuator.
  • a flow control system for controlling a variable displacement pump including a metering valve in fluid communication with the pump for metering an output of the pump.
  • a regulating valve receives a portion of the output of the pump as a bypass flow at a first pressure, wherein an output of the regulating valve is at an interim pressure.
  • the interim pressure is substantially equal to an average of the first pressure and a low reference pressure.
  • An actuator sets a displacement of the pump by acting on a piston connected to a cam ring of the pump. The actuator receives the interim pressure and, thereby, the output of the variable displacement pump is determined.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
EP04026703A 2003-11-11 2004-11-10 Système de contrôle de capacité d'une pompe à combustible Withdrawn EP1531271A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US705362 2003-11-11
US10/705,362 US20050100447A1 (en) 2003-11-11 2003-11-11 Flow control system for a gas turbine engine

Publications (1)

Publication Number Publication Date
EP1531271A2 true EP1531271A2 (fr) 2005-05-18

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Application Number Title Priority Date Filing Date
EP04026703A Withdrawn EP1531271A2 (fr) 2003-11-11 2004-11-10 Système de contrôle de capacité d'une pompe à combustible

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US (1) US20050100447A1 (fr)
EP (1) EP1531271A2 (fr)

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Cited By (5)

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WO2015189524A1 (fr) * 2014-06-11 2015-12-17 Snecma Dispositif de lubrification pour une turbomachine
FR3022300A1 (fr) * 2014-06-11 2015-12-18 Snecma Dispositif de lubrification pour une turbomachine
GB2541605A (en) * 2014-06-11 2017-02-22 Safran Aircraft Engines Lubrication device for a turbine engine
GB2541605B (en) * 2014-06-11 2020-04-29 Safran Aircraft Engines Lubrication device for a turbine engine
US10677095B2 (en) 2014-06-11 2020-06-09 Safran Aircraft Engines Lubrication device for a turbine engine

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