US3442218A

US3442218A - Dual purpose pump

Info

Publication number: US3442218A
Application number: US542101A
Authority: US
Inventors: Thomas B Wess
Original assignee: General Electric Co
Current assignee: General Electric Co
Priority date: 1966-04-12
Filing date: 1966-04-12
Publication date: 1969-05-06
Anticipated expiration: 1986-05-06

Description

May 6, 1969 T. B. WESS 3,442,218

DUAL PURPOSE PUMP Filed April 12. 196e sheet f of 2 May 6, 1969 T. B. WEss 3,442,218

DUAL PURPOSE PUMP med April 12, 196e sheet 2 of 2 WET-3 3 lL-E4 INVENTOR. 7/4//lli 5 M555 BY United States Patent O 3,442,218 DUAL PURPOSE PUMP Thomas B. Wess, Cincinnati, Ohio, assignor to lGeneral Electric Company, a corporation of New York Filed Apr. 12, 1966, Ser. No. 542,101 Int. Cl. F04b 19/00 U.S. Cl. 103-10 6 Claims ABSTRACT F THE DISCLOSURE A pump assembly delivers liquid at varying rates and selectively supplies high pressure liquid for hydraulic actuation of an auxiliary device. Two positive displacement pumps are employed in parallel. Selectively actuated means throttle the flow through the output passageway of one of the pumps and valve means responsive to increased pressurization, resulting from the actuation of the throttling means, connects the first pump output to the auxiliary device.

The present invention relates to improvements in pumps which serve dual functions as delivering fuel at a varying rate and also supplying the fuel for actuation of hydraulic devices.

It is common practice in gas turbine control systems to utilize the fuel supplied by a fuel pump to a main gas generator, for hydraulic actuation of auxiliary devices. In many instances, auxiliary devices require pressure levels for effective operation which are substantially greater than the pressure requirements of the main gas generator. To attain these levels the output of the pump is continuously throttled when the pressure requirements of the main gas generator are lower than those required by the auxiliary devices.

When the output of the pump is so throttled, the loads imposed on it are substantial which may result in increased wear and reduced operating life.

Accordingly, it is an object of the present invention to minimize the loads imposed on pumps which deliver liquid at varying rates and pressures and supply pressurized liquid for hydraulic actuation to thereby increase pump life.

The above ends are achieved by providing a pump assembly for delivering liquid at a varying rate and forsimultaneously supplying a temporary source of pressurized liquid for hydraulic actuation of an auxiliary device. The pump assembly comprises first and second positive displacement pumps disposed in parallel and having passageways providing fiow paths to a common outlet. Selectively actuated means are provided for throttling the output of the first pump. This is done when it is desired to actuate the auxiliary device during a condition of low flow output and low pressure at the common outlet. The pressure output of the lirst pump is thus maintained at a level necessary for effective operation of the auxiliary device. Valve means responsive to the actuation of the throttling means are provided for connecting the output of the first pump to the auxiliary device.

The above and other related objects and features of the invention will be apparent from a reading of the following description of the disclosure found in the accompanying drawings and the novelty thereof pointed out in the appended claims.

In the drawings:

FIGURE l is a schematic showing of a pump embodying the present invention with the cooperating elements of a gas turbine engine shown in abbreviated diagra-mmatic fashion;

FIGURES 2., 3, and 4 are fragmentary views of the pump in FIGURE 1 showing the operation thereof.

3,442,218 Patented May 6, 1969 FIGURE 5 is a fragmentary view of the pump in FIG- URE 1 showing an alternate embodiment of the present invention.

FIGURE 1 shows in block fashion a fuel control system of a gas turbine engine 10 used for aircraft propulsion. A fuel pump 12 receives fuel from a fuel tank (not shown) by means of a conduit 14 and delivers it through a conduit `16 to a main fuel control 18. Fuel pump 12 is mechanically connected to and driven by the rotor (not Shown) of the gas turbine engine 10. The main fuel control may be any device that is adapted to deliver fuel at a prescheduled rate set by pilot demand and modified by several engine operating parameters. The main fuel control 18 feeds fuel to a series of combustor nozzles 20 (only one of which is shown) through a conduit 22. Fuel is atomized and then ignited by means well known in the art to provide hot gases for operation of the engine 10.

Fuel pump 12 provides a second pressure output through a conduit 24 for actuation of a thrust reverser system 26 which directs pressurized fuel through

conduits

27, 29 to position a thrust reverser actuator 31. The actuator 31 is connected by suitable means to a thrust reverser 33 (shown in simplified fashion). The thrust reverser system 26 may be mechanically actuated by a pilot controlled lever 28 which is also mechanically connected to the pump 12 and actuates mechanism for selectively pressurizing conduit 24 when the thrust reverser system 26 is to be actuated as will be apparent from the following description.

Reference is now had to FIG. 2, which is a diagrammatical section showing in detail the fuel pump y12 of FIGURE 1. A housing 30 has journaled therein a rotatable shaft 32 which drives a pair of parallel

positive displacement pumps

34, 36, and a centrifugal impeller 38.

o The conduit 14 is connected to the axial inlet to impeller 38 whereby the fuel is initially pressurized and discharged to a passageway 40. Passageway 4-0 is connected to a pair of passageways 42, 44, for

gear pumps

34 and 36 respectively. A passageway 46 connects the output of gear pump 34 with an outlet passageway 48.

The output of pump 36 is also connected to the outlet passageway 48 by way of a passageway 50, through the interior of a valve 52, ports 54 therein an annular chamber 56 surrounding the valve 52. A pressure relief valve 58 is disposed in a passageway 60 which connects passageway 40 with passageway 48.

The valve 52 is in the form of a sleeve reciprocable in a cylindrical chamber 62 and normally maintained in its i1- lustrated lower position by means of a spring 64. A second annular chamber 66 surrounds the lower end of valve 52 and connects with the high pressure discharge conduit 24. A control valve 68 has a first diameter 70 adapted to slide in a bore 72 at the upper end of chamber 62 and a smaller second diameter 74 slidable in the sleeve 52. A further passageway 76 extendst from bore 72 and has a slidable therein a valve 78. Valve 78 is displaceable in response to a mechanical input to a shaft 80, journaled in housing 30, by means of a link 82. A hole 84 extends through control valve 68. A passageway 86 connects the yupper end of the valve 68 to the intake sides of

pumps

34 and 36 by way of the pressure relief passageway 88.

In normal operation, as illustrated by FIGURE 1, fuel from conduit 14 is initially pressurized by centrifugal impeller 38 and passed through conduits 40, 42, to gear pump 34. The output of gear pump 34 flows through passage 46 to the outlet passageway 48. The output from gear pump 36 passes through passageway Si) to the interior of the pressure regulating piston. 52 and from there through ports 54 to annular chamber 56. Fuel then flows from annular chamber 56 to the outlet passageway 48 and if a predetermined outlet pressure is exceeded, fuel is bypassed to the passageway 40 by means of passageway 60 and pressure relief valve 58. The combined output of the two pumps then flows through conduit 16 to the main fuel control 18 of FIGURE l where fuel is scheduled for delivery to the fuel nozzles 20. At this time valve 52 is seated at the bottom of chamber 62 to prevent pressurization of conduit 24. The hole 84 in control valve 68 and

passageways

86, 88, provide a bleed flow path from the interior of valve 52 to passageway 60. The cross sectional area of hole 84 is smaller than that of passageways 86, S8, so that the pressure drop across valve 68 is much greater than the pressure drop along the length of

passageways

86, 88. The pressure acting on the upper end of the valve 68 is nearly that of the centrifugal impeller 38 output and the pressure acting on the bottom is that of the pump 36 output. Since the output pressure of pump 36 is much greater than the output pressure of centrifugal impeller 38, the force acting on the bottom area of valve 68 is larger than on the upper, thus maintaining valve 68 against the top of bore '70 as shown in FIGURE 2.

When it is desired to actuate the thrust reverser system 26 (FIGURE l), the lever 80 is displaced causing valve plunger 78 to block off bleed passageway 86 so that there is no further flow of pressurized fuel through valve 68. Without flow through the hole 84 the pressure on the upper end of valve 68 now becomes the same as that effective on its lower end, viz. essentially the discharge pressure of pump 36. Since the area of the upper end of the valve 68 is greater than that of its lower end, it iS displaced downwardly, thus causing the diameter 74 to block ports 54 of valve 52, as shown in FIGURE 3.

The shoulder defining the larger diameter of valve 68 now engages the top of valve 52 and is maintained thereagainst by the force differential on its opposite ends and by the force differential on opposite ends of valve 52. In this connection it will be noted that a passageway 90 connects with the bleed passageway 88 so that the upper end valve 52 is essentially at the inlet pressure to pump 36 while the higher discharge pressure of pump 36 1s effective on the lower end of valve 52.

The

valves

52 and 68 now function as an integral valve with a larger force on the bottom, which is sufficient to overcome the force of spring 64 and displace both upwardly, thus uncovering annular chamber 66 to make fuel under pressure available in conduit 24 for actuation of the thrust reverser system 26 as shown in FIGURE 4. Bleed passageway 90 allows exit of the normal leakage of the fuel past piston 52.

It will be apparent that the lower end of valve 52 cooperates with the lower edge of annular chamber 56 to form a variable area orifice which provides -a predeterminable and preferably higher restriction to flow to pump discharge flow than the ports 54. Because the output of the positive displacement pump 36 is restricted, the pressure in passageway 50 can be greatly increased, thus making a high pressure source of fuel available in conduit 24 for hydraulic actuation of the thrust reverser system. Spring 64 regulates the area of the orice formed by the cooperation between piston 52 and annular chamber `56 to -maintain the pressure in passageway 50 at the minimum level necessary for effective operation of the thrust reverser system 26.

With conduit 24 thus pressurized, the flo-w into outlet passageway 48 'contributed by gear pump 36 will at least, at times, be reduced. Parallelly disposed pump 34 generally supplies the additional flow to meet the requirements of the main fuel control 18 (FIGURE l). It will be apparent that the means thus described have particular utility in actuating a thrust reverser `system because engine fuel demands during its operation are generally low.

When the lever 80 is displaced to inactivate the thrust reverser system, valve plunger 78 will be raised and fuel will again flow through the hole S4 dropping pressure on the upper end of valve 63 and the resultant force will displace it upwardly relative to valve 52 to uncover ports 54. This in turn causes a force differential on valve 52 (including spring 64) which seats the valve `52 in the position shown in FIGURE l, allowing depressurization of thethrust reverser system.

Reference is now had to FIGURE 5 which shows a modified control valve 68 which is slidable in bore 72' and in the interior of hollow pressure regulating piston S2. Control valve 68 has extending therefrom a shaft 92 slidable in a bore 94 and connecting with a piston 95 slidable in a chamber 96.

Passageways

97 and 98 direct flow of servo fluid from a suitable control source (not shown) to opposite sides of piston 95.

In normal operation piston 95 is maintained against the upper end of chamber 96 (FIGURE 5), and ow of fuel is through the assembly as described before. When it is deisred to operate thrust reverser system (FIGURE l), servo fluid is directed into passageway 97 thus displacing piston 95 downward against the lower end of chamber 96 to cause valve 68' to cover ports 54 of valve 52. The output of pump 36 is now restricted, causing an increased pressure to act on the bottom area of valve 52. The force acting on the bottom of valve l52 is now sufficient to overcome the downward force 0f spring 64, thus displacing valve 52 upwardly to uncover annular chamber 66 making available a high pressure source of fuel in passageway 24. The regulation of pressure in passageway 24 before described is essentially the same and will not be repeated. When actuator operation is terminated, the piston 95 is returned to its illustrated position by means of servo fluid directed through conduit 98-to chamber 96. Pressure regulating piston 52 thus returns to its illustrated position and normal flow is resumed.

The pump thus described is not limited to use `in the actuation of a thrust reverser in a gas turbine fuel system but .may be used in any system wherein a fluid is to be pumped at a varying flow rate while at the same time providing a temporary high pressure source of fluid for actuation of auxiliary devices during flow conditions that are similar to those existing during thrust reverser operation.

Having thus described the invention what is claimed as novel and desired to be secured by Letters Patent of the United States is:

1. A pump assembly for delivering liquid at a varying rate and for simultaneously supplying a temporary source of pressurized liquid for hydraulic actuation of an auxil-iary device, said pump assembly comprising:

rst and second positive displacement pumps disposed lin parallel and each having an outlet passageway for providing a fiow path, for the respective pump, to a common outlet,

selectively-actuated means for throttling the flow through the output passageway of said first pump when it is desired to actuate said auxiliary device during a condition of low flow output and low pressure at said common outlet to thereby maintain the pressure output of said first pump at a level necessary for effective operation of said auxiliary device, sa-id selectively-actuated means comprising an element disposed in the passageway from said first pump to said common outlet, said element being displaceable between a first position, providing a relatively low resistance flow path through said passageway, and a second position, providing a throttling of flow therethrough.

valve means responsive to increased pressurization of the output of said first pump, resul-ting from movement of said element yto said second position for connecting said first pump output to said auxiliary device and means for blocking the flow to said auxiliary device when said element is in its first position.

2. A pump assembly as in claim 1 wherein said element selectively activated by means which comprise:

yieldable means for urging said element into said first position,

means for at least substantially reducing fiow through the relatively low resistance fiow path, the output pressure of said first pump on said element being increased thereby.

said element being displaced against the action of said yieldable means to said throttling position in response to increased pump pressure thereon.

3. A pump assembly as in claim 2 wherein said passageway includes a cylindr-ical chamber receiving at one end the output of said first pump,

" said element comprises a sleeve slidable in said cham ber and maintained against said end by said yieldable means,

said sleeve having at least one radial port providing the relatively low resistance flow path therethrough,

said means for substantially reducing the fiow through said low resistance flow pa-th comprises a piston received at one end in said sleeve and slidable therein between a first position which permits fiow through said port and a second position which blocks the fiow therethrough,

said chamber having an outlet said common outlet,

said chamber outlet being disposed for cooperating with said sleeve to provide a relatively low resistance fiow path when said port is open and further cooperating with said sleeve when the sleeve is displaced by the output pressure of said first pump when said port is blocked to throttle the output of said first pump.

4. A pump assembly as 4in claim 3 wherein:

said valve means is formed in part by said sleeve and further comprises a connecting passageway which cooperates with said sleeve to connect `the out-put of said first pump with said auxiliary device when said sleeve is displaced to the throttle position and cooperates to block the flow to said auxiliary device when the sleeve is in the position providing the relattively low resistance fiow path.

providing a fiow path to 5. A pump assembly as in claim 3 wherein:

the other end of said piston has an enlarged diameter,

a bore at the other end of said chamber slidably receives said enlarged diameter,

said piston having a passageway providing a bleed ow path from the interior of said sleeve to said bore,

means for discharging bleed liquid from said bore to thereby cause a pressure differential across said piston, the action of which maintains said piston in a position which allows flow through said sleeve port, and

means for terminating the discharge of liquid from said bore when it is desired to actuate said auxiliary device, whereby said piston is displaced by the increased force on said enlarged diameter to engage said sleeve and block 4the fiow of liquid through said port.

6. A pump assembly as in claim 3 wherein said piston is actuated by means comprising:

a rod extending from said chamber,

means for displacing said rod between a first position in which said piston permits fiow through said port `and a second position in which said piston blocks flow of liquid through said port.

piston and out of said References Cited UNITED STATES PATENTS 2,905,191 9/1958 Vander Kaay l37-l08 3,279,558 10/1966 Allen et al. 137-108 2,643,516 6/1953 Carlson 103-11 X 2,778,191 1/1957 Thompson 60-39.28 X 2,769,394 11/1956 Lauck 103-4 2,805,038 9/1957 Towler 103--11 X 3,033,277 5/1962 Cowles et al. 103-11 X 3,034,292 5/ 1962 Binford et al 60-39.28

WILLIAM L. FREEH, Primary Examiner.

U.S. Cl X.R.