EP1531271A2 - Fuel pump capacity control system for a gas turbine engine - Google Patents
Fuel pump capacity control system for a gas turbine engine Download PDFInfo
- 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.)
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Classifications
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
Abstract
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.
Description
- 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.
- Fixed delivery fuel pumps have often been over-sized to provide excessive fuel flow capacity in order to insure adequate supply to the associated engine. Consequently, under many operating conditions, large amounts of pressurized fuel are returned to the pump inlet for recirculation. The return and recirculation results in significant fuel heating due to additional energy being put into the fuel which is subsequently turned into heat as the pressure drops in the recirculation path. In modem designs, fuel heating is a critical issue because the fuel is typically used as a heat exchanger to maintain proper operating temperature. Other methods of heat exchange are undesirable because of the associated size, weight and cost. Such concerns are magnified in modem engines because the fuel pumps also need to supply fuel to engine geometries. For example, modem mid to large class engines utilize linear pistons as guide vanes. The linear pistons require a significant source of fuel to slew. This slewing is a transient event that can unacceptably starve the supply of fuel to the engine.
- 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. However, the engine operating conditions often include transients such as those caused by engine actuator slewing, start-up and the like as would be appreciated by those of ordinary skill in the pertinent art. Under such rapidly varying operating conditions, prior art pump control systems have been unable to respond quickly and adequately. Moreover, many prior art pump control systems lack the required stability to reliably provide fuel to the engine. So despite the advances of the state of the art, variable displacement pumps are lacking in stability and still do not respond quickly enough to varying engine demands. As a result, poor performance and excess fuel flow are still common.
- Examples of 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.
- In view of the above, it would be desirable to provide a flow control system which has a simple design for quickly regulating the output flow of a variable displacement pump with stability and without the associated drawbacks of the prior art.
- In one embodiment, 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.
- It is an object of the present disclosure to increase the fuel metering unit response while maintaining acceptable stability at all operating conditions.
- It is another object to provide a hydromechanical fuel metering unit for a variable displacement pump. It is still another object to provide a fuel metering unit that achieves quick and accurate response to dynamic flow conditions.
- In another embodiment, 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.
- So that those having ordinary skill in the art to which the subject invention appertains will more readily understand how to make and use the same, reference may be had to the Sole Figure wherein:
- The Sole Figure is a schematic representation of a flow control system constructed in accordance with the subject invention.
- Referring now to the Sole Figure, there is illustrated a schematic representation of a flow control system in accordance with the subject invention which is designated generally by
reference numeral 10. For clarity throughout the following description, arrows are shown within the lines ofsystem 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 thesystem 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. Thesystem 10 maintains the output flow of a variablevane displacement pump 12 to provide fast response to engine needs in a stable manner yet excessive complexity is avoided. - The
pump 12 includes arotor 14 and apivoting cam ring 16. For a detailed description of a variable displacement vane pump, see U.S. Patent Application Publication No. 2002/0103849 published on June 5, 2003 which is incorporated herein by reference in its entirety. Thepump 12 receives fuel flow at an inlet pressure PAF, and delivers fuel flow at an output pressure PF. A piston 18 is operatively connected to thecam ring 16 to control the position of thecam ring 16 relative to therotor 14 and, thereby, vary the output flow of thepump 12. Acam actuator assembly 20 positions thepiston 18 as described below. It should be appreciated by those of ordinary skill in the art that other types of actuators similarly and differently arranged would perform this same function and are, therefore, considered mere design choices well within the scope of the subject invention as claimed. The maximum flow setting of thepump 12 occurs when thepiston 18 is moved the maximum distance to the left. - A
feedback line 21 in fluid communication with the output of thepump 12 provides fuel at pressure P1W to aline 29 connected to aninlet 22 of thecam actuator 20. Orifices 24 and 26 limit the flow intoline 29. The pressure inline 29 is approximately equal to P1W + PAF divided by two, and designated as PI1 in the Sole Figure. It will be appreciated by those of ordinary skill in the art that the pressure at P1W will be substantially equal to the pressure PF. Thefeedback line 21 also provides fuel at pressure P1W 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 PAF. Anotherinlet 28 of thecam actuator 20 receives fuel at an interim pressure PI2 as will be described hereinbelow. - A
housing 23 of thecam actuator 20 retains thepiston 18 for dividing the interior of thehousing 23. Acoiled spring 30 biases thepiston 18. Within thehousing 23, the pressure on the right side of thepiston 18 is approximately equal to the average of P1W and PAF. The combination of the pressure differential between the right and left sides of thehousing 23 together with the sizing of aspring 30 act to position thepiston 18 within thecam actuator 20. Thecam ring 16 moves correspondingly and the output of thepump 12 varies. Preferably, thespring 30 is sized and configured to position thepiston 18 at maximum flow for start-up of thepump 12. Throughoutsystem 10, 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 awash filter 32 for cleaning debris prior to entering amain metering valve 34 andline 21. Themain metering valve 34 is disposed between thepump 12 and engine (not shown) for providing fuel to the engine at a selected rate and pressure PM. Themain metering valve 34 insures that PF is greater than PM by some preselected, substantially constant value. Suitablemain metering valves 34 are well known in the prior art and therefore not further described herein. Thepreferred metering valve 34 performs the function of selectively varying the amount of fuel passing therethrough. Themain metering valve 34 receives fuel at pressure PF and the fuel exits at pressure PM. - A
line 35 connects the output of thepump 12 to a bypassing pressureregulator valve assembly 36. The flow inline 35 is referred to as the spill return flow at Pressure PF. Theregulator valve assembly 36 includes ahousing 38 defining an interior with a spring-biasedspool 40 operatively disposed therein. A left face of thespool 40 has fuel at pressure PF there against. A meteringhead adjustment screw 42 is attached to thespool 40 for calibrating the position of thespool 40 within theregulator valve assembly 36 during set up. Thehousing 38 defines aninlet 44 connected to line 35 for receiving fuel at pressure PF. Another inlet 46 of thehousing 38 receives fuel at pressure PM fromstatic flow line 37 to dampen the motion of thespool 40. Anorifice 48 is disposed in theline 37 for dampening. Thehousing 38 also defines a restrictingoutlet 50 for the fuel to exit from theregulator valve assembly 36. Theoutlet 50 is in fluid communication with theinlet 28 of thepump 12 vialine 51.Line 51 also connects the low reference pressure PAF, wherein an orifice 52 limits the flow to the low reference pressure PAF. The pressure withinline 51 is approximately equal to the average of PF and PAF, hereinafter designated the interim pressure PI2. The combination of the pressure differential between PF on the left side of thehousing 40 and PM on the right plus the spring-biasing of thespool 40 ultimately positions thespool 40. - During steady-state operation, the left side of
regulator valve assembly 36 and the right side of thecam actuator 20 are at approximately the same pressure. The recirculation flow through theregulator valve assembly 36 is maintained at a low level by thespool 40 partially blocking theoutlet 50 yet thesystem 10 can rapidly and sufficiently respond to transient events. In the preferred embodiment, thespool 40 within theregulator 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. - When a transient event occurs, the
pump 12 must produce more fuel rapidly. For example, a transient event would be an actuator motion by utilization of the slewing source at pressure P1W inline 21. Increased demand by the transient event causes themain 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 thepump 12. Thepump 12 cannot immediately respond with increased displacement so the incremental demand comes from diminished spill return flow inline 35. As a result, the pressure PM increases and the Pressure PF decreases (i.e., a drop of the pressure differential (PF-PM) across the main metering valve 34). Theregulator valve assembly 36 senses the pressure differential drop and thespool 40 strokes to the left. The pressure in theoutlet 50 is decreased and, in turn, the pressure into the left side of thecam actuator 20 drops. The decrease in pressure of the left side of thecam actuator 20 causes thepiston 18 to stroke to the left. When thepiston 18 strokes to the left, the output of thepump 12 increases. The increased pump output raises the pressure PF until the pressure differential across themain metering valve 34 returns to the nominal steady-state level and the steady-state condition is reattained. - In the alternative, when a transient event occurs where the
pump 12 must rapidly decrease the output to prevent excessive recirculation, themain 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 thepump 12. Thepump 12 cannot immediately respond with decreased displacement so the decreased demand results in a decrease of pressure PM and an increase in Pressure PF (i.e., a rise of the pressure differential (PF-PM) across the main metering valve 34) to allow thesystem 10 to immediately respond. Theregulator valve assembly 36 senses the pressure differential rise and thespool 40 strokes to the right. As a result, the pressure in theoutlet 50 is increased and, in turn, the pressure into the left side of thecam actuator 20 rises. The rise in pressure of the left side of thecam actuator 20 causes thepiston 18 to stroke to the right. When thepiston 18 strokes to the right, the output of thepump 12 decreases until the pressure differential (PF-PM) across themain metering valve 34 returns to the nominal steady-state level with thespool 40 substantially at a nominal position with theregulator valve assembly 36. - In summary, the
regulator valve assembly 36 is used to minimize the recirculation flow, while allowing thesystem 10 to respond quickly to transient demands. The recirculation flow is regulated and the position of thespool 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. - While the subject invention has been described with respect to preferred embodiments, those skilled in the art will readily appreciate that various changes and/or modifications can be made to the invention without departing from the spirit or scope of the invention as defined by the appended claims.
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.
Claims (22)
- A high-stability flow control system for controlling a variable displacement pump, the flow control system comprising:a metering valve in fluid communication with the pump for metering a pump output;a regulating valve assembly for maintaining a pressure differential across the metering valve, the regulating valve assembly receiving a portion of the pump output of the pump as a bypass flow at a first pressure, wherein a valve output from the regulating valve assembly is at an interim pressure approximately equal to an average of the first pressure and a low reference pressure; andan actuator connected to the variable displacement pump for setting a displacement of the variable displacement pump, the actuator receiving the valve output for determining a setting of the actuator and, thereby, the pump output.
- A fuel metering unit as recited in Claim 1, wherein a second pressure within the actuator opposes the interim pressure.
- A fuel metering unit as recited in Claim 1, wherein the second pressure is approximately equal to the interim pressure during steady-state operation.
- A fuel metering unit as recited in Claim 1, further comprising a filter in fluid communication with the output of the pump for cleaning debris.
- A fuel metering unit as recited in Claim 1, further comprising a first line connected between the metered output of the metering valve and regulator valve assembly for dampening a response of the regulating valve assembly.
- A fuel metering unit as recited in Claim 5, wherein the first line is a static flow line.
- A fuel metering unit as recited in Claim 5, further comprising an orifice in the first line.
- A fuel metering unit as recited in Claim 1, further comprising a second line connected between the regulating valve assembly and cam actuator for providing the interim pressure to the cam actuator.
- A fuel metering unit as recited in Claim 1, wherein the actuator includes a piston connected to a movable cam ring of the pump.
- A fuel metering unit for controlling a variable displacement pump wherein the variable displacement pump receives fuel at a low reference pressure and produces an output at an elevated pressure, the fuel metering unit comprising:first means in fluid communication with the pump for metering the output of the pump;second means in fluid communication with the first means for maintaining a substantially constant pressure differential across the third means, and producing an interim pressure approximately equal to an average of the elevated pressure and the low reference pressure;third means operatively connected to the variable displacement pump for controlling the output of the pump, a setting of the third means being based upon a difference between the interim pressure and an opposing pressure; andfuel lines connected between the output of the variable displacement pump and the third means for providing the opposing pressure to the third means.
- A fuel metering unit as recited in Claim 10, wherein the fuel lines are also connected to the low reference pressure such that the interim pressure and the opposing pressure are substantially equal during steady-state operations.
- A fuel metering unit as recited in Claim 10, wherein the first means is a metering valve.
- A fuel metering unit as recited in Claim 10, wherein the second means is a regulating valve.
- A fuel metering unit as recited in Claim 10, wherein the third means is a cam actuator.
- A fuel metering unit as recited in Claim 10, further comprising a filter in fluid communication with the output of the pump for cleaning debris.
- A fuel metering unit as recited in Claim 10, further comprising a first line connected between the metered output of the first means and third means for dampening a response of the third means.
- A fuel metering unit as recited in Claim 15, wherein the first line is a static flow line.
- A fuel metering unit as recited in Claim 15, further comprising an orifice in the first line.
- A fuel metering unit as recited in Claim 10, further comprising a second line connected between the third means and the second means for dampening a response of the second means.
- A method for metering a variable displacement pump that provides fuel to an engine, the method comprising 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 being in fluid communication with the spill return flow, wherein the regulating valve generates an interim pressure substantially equal to an average of the spill return and the low reference pressure; andadjusting 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.
- A method as recited in Claim 20, further comprising the step of providing a second pressure to the cam actuator in opposition to the interim pressure.
- A method as recited in Claim 20, further comprising the step of damping a response of the regulating valve by inputting a metered output of the metering valve to the regulating valve.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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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 (en) | 2005-05-18 |
Family
ID=34435609
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04026703A Withdrawn EP1531271A2 (en) | 2003-11-11 | 2004-11-10 | Fuel pump capacity control system for a gas turbine engine |
Country Status (2)
Country | Link |
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US (1) | US20050100447A1 (en) |
EP (1) | EP1531271A2 (en) |
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EP1819914A2 (en) * | 2004-11-19 | 2007-08-22 | Goodrich Pump & Engine Control Systems, Inc. | Two-stage fuel pump for gas turbines |
CA2663123C (en) * | 2006-09-26 | 2016-10-25 | Magna Powertrain Inc. | Control system and method for pump output pressure control |
US8127524B2 (en) * | 2007-01-10 | 2012-03-06 | Hamilton Sundstrand Corporation | Gas turbine fuel metering unit |
US8348630B2 (en) * | 2008-08-18 | 2013-01-08 | Woodward, Inc. | Flow compensated proportional bypass valve combined with a control valve |
US9435311B2 (en) * | 2014-05-07 | 2016-09-06 | Woodward, Inc. | Regulator flow damping |
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FR3068114B1 (en) * | 2017-06-27 | 2019-08-16 | Safran Aircraft Engines | FLUID SUPPLY SYSTEM FOR TURBOMACHINE, COMPRISING A VARIABLE CYLINDER PUMP FOLLOWED BY A FLUID DOSER |
US11674455B2 (en) | 2021-03-26 | 2023-06-13 | Hamilton Sundstrand Corporation | Variable displacement pump with active bypass feedback control |
US20230130997A1 (en) * | 2021-10-22 | 2023-04-27 | Hamilton Sundstrand Corporation | Variable displacement pumps |
US11788476B1 (en) | 2022-06-01 | 2023-10-17 | Honeywell International Inc. | Fluid system with variable pump discharge pressure and method |
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-
2003
- 2003-11-11 US US10/705,362 patent/US20050100447A1/en not_active Abandoned
-
2004
- 2004-11-10 EP EP04026703A patent/EP1531271A2/en not_active Withdrawn
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
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WO2015189524A1 (en) * | 2014-06-11 | 2015-12-17 | Snecma | Lubrication device for a turbine engine |
FR3022300A1 (en) * | 2014-06-11 | 2015-12-18 | Snecma | LUBRICATION DEVICE FOR A 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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