Variable geometries fluid supply circuit for a turbomachine without volumetric pump

Abstract

A system for supplying a turbomachine with fluid, the supply system including a low-pressure pumping unit intended to increase the pressure of the fluid flowing toward a downstream circuit. The downstream circuit divides at an inlet node, situated between the low-pressure pumping unit and the high-pressure volumetric pump, into a circuit supplying an injection system and a variable geometries supply circuit. The circuit supplying the injection system includes a high-pressure volumetric pump. The variable geometries supply circuit is configured to convey the fluid toward variable geometry from the inlet node to an outlet node connecting the variable geometries supply circuit to the upstream circuit between two pumps of the low-pressure pumping unit.

Claims

1. A system for supplying a turbomachine with fluid, comprising: an upstream circuit; and a downstream circuit connected to the upstream circuit, wherein the upstream circuit comprises a low-pressure pumping unit configured to increase a pressure of the fluid flowing toward the downstream circuit and which comprises a first centrifugal pump, wherein the downstream circuit divides at an inlet node into a supply circuit of an injection system for a combustion chamber and into a variable geometries supply circuit configured to convey fluid to variable geometries, the supply circuit of the injection system comprising a high-pressure volumetric pump, wherein the low-pressure pumping unit is devoid of a volumetric pump and comprises at least a second centrifugal pump in series with the first centrifugal pump, the low-pressure pumping unit comprising at least two pumps, wherein the inlet node is situated between the low-pressure pumping unit and the high-pressure volumetric pump, and wherein the variable geometries supply circuit is connected to the upstream circuit at an outlet node situated between the at least two pumps of the low-pressure pumping unit.

2. The system for supplying according to claim 1, wherein said outlet node is situated between the first centrifugal pump and the second centrifugal pump of the low-pressure pumping unit.

3. The system for supplying according to claim 1, wherein the low-pressure pumping unit comprises three, four or live centrifugal pumps in series.

4. The system for supplying according to claim 1, wherein the high-pressure volumetric pump is a gear pump configured to be mechanically driven by a turbomachine gearbox.

5. The system for supplying according to claim 4, wherein the supply circuit of the injection system comprises a fluid metering device and an injection system, and wherein the fluid metering device is configured to adjust a flow in at least one of a direction of the injection system and in a direction of a fluid recirculation loop configured to convey the fluid upstream of the high-pressure volumetric pump.

6. The system for supplying according to claim 1, wherein the high-pressure volumetric pump is an electric pump commanded by an electronic system for regulating the turbomachine.

7. The system for supplying according to claim 1, wherein the high-pressure volumetric pump is commanded by a full-authority electronic control module via an electronic control module.

8. The system for supplying according to claim 1, wherein the variable geometries supply circuit is devoid of a volumetric pump.

9. The system for supplying according to claim 1, wherein the upstream circuit is devoid of a volumetric pump.

10. The system for supplying according to claim 1, wherein the variable geometries supply circuit comprises at least one hydraulic actuator of variable geometries.

11. The system for supplying according to claim 1, wherein the variable geometries supply circuit comprises a set of complementary pumping comprising at least one centrifugal pump.

12. A turbomachine comprising a system for supplying the turbomachine with fluid according to claim 1.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) This invention shall be better understood when reading the description of embodiments, given solely for the purposes of information and in no way limiting, in reference to the annexed drawings wherein:

(2) FIG. 1 is a partial diagrammatical view of a system for supplying an aircraft turbomachine with fuel, according to a known design of prior art;

(3) FIG. 2 is a partial diagrammatical view of a system for supplying a turbomachine with fluid, according to a first embodiment of the invention;

(4) FIG. 3 is a partial diagrammatical view of a system for supplying a turbomachine with fluid, according to a second embodiment of the invention,

(5) FIG. 4 is a partial diagrammatical view of a system for supplying a turbomachine with fluid, according to a third embodiment of the invention.

DETAILED EXPOSURE OF PARTICULAR EMBODIMENTS

(6) Identical, similar or equivalent parts of the various figures bear the same numerical references in such a way as to facilitate the passing from one figure to another.

(7) FIG. 2 shows a system for supplying 10 an aircraft turbomachine 1 with fluid. In the embodiment described, the fluid is fuel. However, when the turbomachine 1 comprises a differential gearbox (not shown) configured to drive in rotation at least one propeller, the fluid can also be lubricant, typically oil.

(8) The turbomachine 1 comprises the system for supplying 10, one or several variable geometries 54 and a combustion chamber 2. These variable geometries 54 are equipment of the turbomachine 1 that require taking hydraulic power in order to operate. The variable geometries 54 can be of various natures, for example a cylinder, a servo valve, an adjustable compressor bleed valve, a transient compressor bleed valve, and/or a valve for commanding the air flow rate for a system for commanding the play at the top of the rotor blades for a low-pressure turbine or high-pressure turbine.

(9) The combustion chamber 2 is supplied with fuel by a plurality of fuel injectors cooperating with the corresponding fuel injector systems 62.

(10) The system for supplying 10 comprises an upstream circuit 100 and a downstream circuit 50, 60. The downstream circuit 50, 60 is connected to the upstream circuit 100 and situated downstream of the upstream circuit 100. The terms upstream and downstream are defined in reference to the general direction of flow of the flow in the system for supplying 10 in the direction of the combustion chamber 2.

(11) The upstream circuit 100 comprises a low-pressure pumping unit 101 that increases the pressure of the fuel flowing toward a downstream circuit 50, 60. The low-pressure pumping unit 101 increases the pressure of the fuel, in such a way as to limit/prevent the risks of cavitation inside a high-pressure pump 102 that delivers a constant flow rate of fuel according to the engine rotation speed.

(12) The upstream circuit 100 can include a hydraulic resistance 104, such as that shown in FIG. 1, between the low-pressure pumping unit 101 and the downstream circuit 50, 60 or between two stages of the low-pressure pumping unit 101. The term hydraulic resistance is used to define in this document, by analogy with the field of electricity, the magnitude resulting from the relationship between the difference in pressure of fluid between the inlet and the outlet of an element of the system for supplying on the flow rate of fluid passing through the element. By metonymy and still by analogy with the field of electricity, the term hydraulic resistance is also used to designate an element of the system for supplying characterised by this magnitude. The hydraulic resistance 104 of the upstream circuit 100 comprises for example an exchanger, a fuel filter, a cut-off valve and/or a flow meter.

(13) The downstream circuit 50, 60 comprises a supply circuit 60 of the injection systems 62 for a combustion chamber 2, and a variable geometries supply circuit 50. The variable geometries supply circuit 50 and the supply circuit 60 of the injection systems 62 are separated at the level of an inlet node E located downstream of the low-pressure pumping unit 101.

(14) The variable geometries supply circuit 50 is configured to convey the fluid that passes through the variable geometries 54, from the inlet node E to an outlet node S that connects the variable geometries supply circuit 50 to the upstream circuit 100.

(15) The systems for supplying 10 shown in FIGS. 2 to 4 can be distinguished mainly from the one of FIG. 1 in that the upstream circuit 100 is devoid of a high-pressure volumetric pump, in that the low-pressure pumping unit 101 is constituted of a plurality of centrifugal pumps 110a, 111a, 111b, and in that the downstream circuit 50, 60 comprises a high-pressure volumetric pump 102.

(16) The low-pressure pumping unit 101, which can be seen in FIGS. 2 to 4, further increases the pressure of the fluid in the direction of the high-pressure pump 102 with respect to the low-pressure centrifugal pump 11 of FIG. 1. The high-pressure volumetric pump 102 of FIG. 2 then supplies an increase in the pressure of the fluid that is all the more so low. This results in an overall reduction in the thermal losses of the system for supplying 10.

(17) The displacement of the high-pressure volumetric pump 102 from the upstream circuit 100 to the supply circuit 60 of the injection systems 62 makes it possible to decrease the flow rate of fuel supplied by the volumetric pump 102. The overall thermal losses of the system for supplying 10 are still reduced. The variable geometries supply circuit 50 is devoid of a volumetric pump.

(18) The low-pressure pumping unit 101 of FIGS. 2 to 4 comprises a plurality of centrifugal pumps 101a, 111a, 111b. As such, it should be noted that it would not have been fully satisfactory to only replace the low-pressure pump 11 of FIG. 1 with a low-pressure pump 11 of greater capacity. Indeed, the difference in pressure at the terminals of a centrifugal pump is proportional to the square of the radius of the pump. Above all, the energy efficiency of a centrifugal pump is proportional to the cube of the radius of this pump. Replacing the low-pressure pump 11 of FIG. 1 with a centrifugal low-pressure pump, configured to further increase the pressure of the fluid that passes through it, would therefore not have produced as significant advantages in terms of overall thermal balance of the system for supplying 10.

(19) The outlet node S of the system for supplying 10 of FIGS. 2 to 4 is situated between two pumps 101a, 111a of the low-pressure pumping unit 101, in such a way as to retain a sufficient difference in pressure between the downstream of the set of complementary pumping 51 and the outlet node S and while still limiting the dissipation of thermal energy in the system for supplying 10. The system for supplying 10 of FIGS. 2 and 3 is in particular configured so that the difference in pressure between the downstream of the set of complementary pumping 51 and the outlet node S of the system for supplying of these figures is substantially identical to that of FIG. 1, during the operation of the system for supplying 10.

(20) More precisely and in reference to the embodiment of FIGS. 2 to 4, the low-pressure pumping unit 101 comprises three centrifugal pumps 101a, 111a, 111b or four centrifugal pumps 101a, 111a, 111b, 111c mounted in series. The outlet node S is located between an upstream pumping unit 101a comprising a centrifugal pump and a downstream pumping unit 110 comprising two centrifugal pumps 111a, 111b or three centrifugal pumps 111a, 111b, 111c.

(21) Generally, the upstream pumping unit 101a may include several centrifugal pumps and the number of centrifugal pumps of the downstream pumping unit 110 may vary, according to the needs in hydraulic power and in flow rate of the fluid of the turbomachine 1. Likewise, the pumps of the low-pressure pumping unit 101 are not necessarily identical.

(22) Moreover, the increase in the pressure supplied by the low-pressure pumping unit 101 of FIGS. 2 to 4 with respect to the system for supplying 10 of FIG. 1 is all the more so advantageous that the needs in hydraulic pressure of the variable geometries supply circuit 50 of these systems for supplying 10 are substantially identical to those variable geometries of the system for supplying of FIG. 1.

(23) In the embodiments of FIGS. 2 and 3, the high-pressure pump 102 is a volumetric gear pump configured to be driven mechanically by a gearbox of a turbomachine 1. The removal node B is situated between the low-pressure pumping unit 101 and the high-pressure volumetric pump 102.

(24) The high-pressure volumetric pump 102 delivers a constant flow rate of fuel according to the engine rotation speed. The flow rate of fuel at the outlet of the high-pressure volumetric pump 102 is, in a known manner, greater than the flow rate required to supply the injection systems 62, regardless of the phase concerned of the flight of the turbomachine 1. In particular, the constant flow rate supplied by the high-pressure volumetric pump 102 is determined according to the flow rates required for the most constraining operating speeds of the turbomachine 1, i.e. the flow rates for the low speeds for example. Consequently, there is a flow rate of fluid circulating in the recirculation loop 610, which generates thermal losses. This recirculation loop 610 is situated between a first node A downstream of the inlet node E and a removal node B situated downstream of the low-pressure pumping unit 101.

(25) The supply circuit 60 of the injection systems comprises a bleed valve and a fuel metering device which are represented by the unit 64 and which regulate the flow rate in the direction of the injection system 62. The bleed valve and the fuel metering device 64 are designed to redirect the excess fuel in the supply circuit 60 of the injection systems 62 to the upstream circuit 100 through the fuel recirculation loop 610.

(26) The variable geometries supply circuit 50 of FIG. 2 can be distinguished from that of FIG. 3 in that it comprises a set of complementary pumping 51. The set of complementary pumping 51 makes it possible to suppress any drop in pressure coming from the suppression of the volumetric pump 102 in the upstream circuit 100, and which would not be entirely offset by the plurality of centrifugal pumps 101a, 111a and 111b of the low-pressure pumping unit 101.

(27) The set of complementary pumping 51 makes it possible to respond to a one-off substantial need in flow rate of the variable geometries 54, for example during a displacement of the actuator hydraulic cylinder.

(28) The set of complementary pumping 51 comprises one or several centrifugal pumps, or other types of pumps other than a volumetric pump. In the embodiment of FIG. 2, the set of complementary pumping 101 consists of a centrifugal pump.

(29) In reference specifically to FIG. 4, the supply circuit 60 of the injection systems comprises a hydraulic resistance 69, such as a fuel filter, and a supply duct 68 of the injection systems between the hydraulic resistance 69 and the injection systems 62.

(30) The volumetric pump 102 is electrical, which makes it possible to suppress the fuel metering device 64 that commands the flow rate in the direction of the combustion chamber 2. The recirculation loop of fuel 610 also disappears. From this stems a gain in the mass of the system for supplying 10, as well as a suppression of the thermal losses generated by the recirculation of the fuel in the recirculation loop 610.

(31) The decrease in the power supplied by the high-pressure volumetric pump 102 makes it possible to command the electric volumetric pump 102 without having recourse to massive power electronics. Having recourse to a high-pressure electric volumetric pump 102, rather than to a more conventional volumetric gear pump driven in rotation by a turbomachine gearbox, therefore provides advantages in terms of mass, encumbrance and thermal power dissipated in the system for supplying 10.

(32) The electric volumetric pump 102 is commanded by the full-authority electronic control module 120 of the turbomachine, also known under the name of FADEC or Full Authority Digital Engine Control, via an electronic control module 122. Conventionally, the electronic control module 120 comprises an engine control unit with two symmetrical and redundant channels and with full-authority. This engine control unit is intended to take many parameters into account in order to control the flow rate delivered by the high-pressure volumetric pump 102, such as for example: a command of a pilot of an aircraft, the rotation speed of the high-pressure body of turbomachine 1 and a measuring of the flow rate in the direction of the injection systems 62 measured by a flow meter 67.

(33) Of course, various modifications can be made by those skilled in the art to the invention that has just been described without leaving the scope of the disclosure of the invention.