WO2024227580A1 - Assembly for pumping fluid in an internal compartment of a turbine engine - Google Patents

Abstract

The invention relates to a fluid-pumping assembly (40) intended to be arranged in a compartment (12) of a turbine engine (2), comprising: - a fluid tank (42); and - a pump (44) fluidically coupled to the fluid tank by means of a connection device; characterised in that the connection device comprises: - a normally closed valve, configured to be kept in the open position when the pump is coupled and to close the tank when the pump is uncoupled from the tank.

Description

FLUID PUMPING ASSEMBLY IN AN INTERNAL COMPARTMENT OF A TURBOMACHINE Domain

The invention relates to the field of turbomachine reservoirs. More specifically, the invention relates to the field of fluid reservoirs used to lubricate turbomachine components, in particular comprising an unducted variable-pitch propeller and/or a variable-pitch rectifier.

Prior art

Aircraft turbomachines comprising at least one unducted propeller are known by the English term "open rotor" or "unducted fan". In this category of turbomachine, there are those which have two unducted and counter-rotating propellers (known by the English acronym UDF for "Unducted Dual Fan") or those having a single unducted propeller and a rectifier comprising several stator blades (known by the English acronym USF for Unducted Single Fan).

These turbomachines are turboprops which are distinguished from turbojets by the use of a propeller outside the nacelle (unducted) instead of an internal fan.

The propeller or propellers forming the propulsion part generally include a system for actuating the pitch of the blades of the propeller(s), also referred to as a variable pitch system. Such a system allows the blades of the propeller to be oriented according to the needs of the flight phases of the aircraft (takeoff, cruise, landing, etc.) in order to ensure thrust management in all flight cases of the turbomachine.

In the case of turbomachines with a single unducted propeller and a rectifier, the latter may also include a variable-pitch system so as to improve the performance of the turbomachine. An example of such a turbomachine is disclosed by published patent document FR 3 107 319 A1.

Variable timing systems require a permanent oil supply to enable the blade pitch to be actuated and the engine thrust to be managed in all nominal and extreme turbomachine flight conditions which may require, for example, blade feathering.

In this respect, turbomachines require the presence of a fluid reservoir ideally as close as possible to the variable pitch systems in order to ensure the feathering action of the blades in any flight situation. However, on turbomachines comprising at least one unducted propeller, there is a high density of equipment in a relatively restricted space, which complicates the arrangement of a fluid reservoir close to these systems.

The published patent document FR 3 082 552 A1 discloses a tank arranged in an inter-vein compartment of a shrouded dual-flow turbomachine, the document proposes a solution for filling the tank with an access hatch offset towards a cover internally delimiting a secondary vein of the turbomachine.

However, the solution proposed by the document has room for improvement, as it is not suitable for the architecture of an unducted propeller turbomachine, which has a smaller installation space. In addition, the disclosed turbomachine does not include a blade pitch actuation system.

The present invention aims to overcome at least one of the drawbacks of the aforementioned state of the art. More particularly, the invention aims to propose a means of continuous fluid supply to at least one blade pitch actuation system, in a restricted space requirement of the turbomachine.

The invention relates to a fluid pumping assembly intended to be arranged in a turbomachine compartment, comprising:
- a fluid reservoir;
- a pump fluidically coupled to the fluid reservoir by means of a connection device;
remarkable in that
the connection device includes:
- a normally closed valve, configured to be held in the open position when the pump is coupled and to close the tank when the pump is uncoupled from said tank.

Preferably, the pump is electrically driven, said pump being arranged externally to the fluid reservoir. Advantageously, the pump is fluidically coupled in a removable manner to the fluid reservoir.

According to an advantageous embodiment of the invention, the connection device comprises a seat and a spring pressing the valve towards said seat in the tank closing position.

According to an advantageous embodiment of the invention, the pump comprises a projecting element capable of contacting and moving the valve towards the open position when said pump is coupled to the tank.

According to an advantageous embodiment of the invention, the projecting element comprises a ring integral with the pump by means of at least two feet forming at least two windows for the passage of fluid when the valve is in the open position.

According to an advantageous embodiment of the invention, the valve and the spring are located on one side of the seat corresponding to the tank.

According to an advantageous embodiment of the invention, the connection device comprises a cage capable of guiding the valve between the closed position and the open position.

Advantageously, the valve is connected to a rod slidably mounted with an end wall of the cage.

According to an advantageous embodiment of the invention, the connection device comprises an external portion with a flange for fixing to the tank, the seat being formed on said external portion and the cage being linked to said external portion.

According to an advantageous embodiment of the invention, the connection device comprises a tubular portion extending through the fixing flange and forming the seat at an inner end of the outer portion.

Advantageously, the interior is in reference to a positioning relative to an internal enclosure of the fluid reservoir.

According to an advantageous embodiment of the invention, the tubular portion comprises at an outer end a coupling flange with the pump.

Preferably, the tubular portion extends along a vertical mounting direction and/or extends along a main axis of the fluid reservoir corresponding to the main direction of the extent of the reservoir and which defines the direction of the largest dimension of said reservoir. The exterior is in reference to a positioning relative to the internal enclosure of the fluid reservoir.

According to an advantageous embodiment of the invention, the pump further comprises an annular rib arranged between the projecting element and said pump so that when the pump is connected to the tank, said annular rib bears directly against the coupling flange.

According to an advantageous embodiment of the invention, said assembly further comprises a retaining collar provided with an internal groove having a V-shaped section, intended to ensure axial clamping between the annular rib and the coupling flange when the pump is coupled to the tank.

According to an advantageous embodiment of the invention, at least one of the coupling flanges and the annular rib comprises an indexing pin capable of engaging in a corresponding orifice.

The invention also relates to a turbomachine comprising:
- an unducted propeller propelling an incoming air flow, said propeller comprising a variable pitch system for actuating the pitch of the propeller blades;
- a fluid pumping assembly comprising a fluid reservoir;
remarkable in that the fluid pumping assembly is according to the invention.

According to an advantageous embodiment of the invention, the fluid pumping assembly is arranged radially internally to a primary flow vein, in line with an internal compartment of the turbomachine.

According to an advantageous embodiment of the invention, the variable timing system is a first variable timing system, and said turbomachine further comprises a rectifier comprising a plurality of stator blades extending from an external casing, said rectifier comprising a second variable timing system, the pump being fluidically connected to the components of the first system and/or the second variable timing system of the turbomachine.

Advantages of the invention

The invention is particularly advantageous in that the connection device of the fluid pumping assembly makes it possible to ensure an optimized interface between the pump and the reservoir, which makes it possible to reduce the overall size and mass of the turbomachine.

Advantageously, the simplicity of the architecture of the fluid pumping assembly of the present invention allows it to ensure reliable operation. In addition, said assembly allows for a considerable saving of time during maintenance, since the steps of assembly and disassembly of the pump are facilitated and secured.

The simplified maintenance of the assembly makes it possible to favor its arrangement in line with the internal compartment of the turbomachine of the invention. The latter is thus capable of ensuring continuous and secure operation of its variable timing systems, and this without any presence of air and without interruption of power supply.

Description of the drawings

is a schematic axial sectional view of an aircraft turbomachine according to the invention;

schematically represents an enlarged view of the axial section of the turbomachine of the comprising a fluid pumping assembly according to the invention;

represents a perspective view of the pumping assembly comprising a pump coupled to a fluid reservoir;

represents an exploded view of the pumping assembly of the ;

represents a sectional view of the pumping assembly in which the pump is coupled to the fluid reservoir, and including a valve held in the open position;

represents a sectional view of the pumping assembly in which the pump is uncoupled from the fluid reservoir, and the valve is in the closed position.

Detailed description

The figures show the elements schematically and are not drawn to scale. In particular, some dimensions are enlarged to facilitate reading of the figures.

There schematically illustrates an axial sectional view of an aircraft turbomachine according to the invention. This is a turbomachine known by the English expression “open rotor” or “unducted fan”, and particularly a USF “Unducted Single Fan” turbomachine.

In the following description, the terms "internal" and "external" refer to a positioning relative to the axis of rotation of a turbomachine, and here along the longitudinal axis X (and even from left to right on the ). The terms "radial", "internal" and "external" are defined with respect to a radial direction perpendicular to the longitudinal axis X. Upstream and downstream refer to the direction of flow of a stream in the turbomachine. Furthermore, elements illustrated in the figures which are identical or substantially identical and/or with the same functions are represented by the same reference numerals.

The turbomachine 2 typically comprises, from upstream to downstream, a first compression level, called low pressure compressor 4, as well as a second compression level, called high pressure compressor 6, a combustion chamber 8 followed by a high pressure turbine 9 and a low pressure turbine 10.

The turbomachine 2 comprises a propeller 14 arranged upstream of a separation nozzle 16 carried by an external casing 24 and capable of separating the air flow F into a secondary flow F2 and a primary flow F1 circulating in a primary vein 18 and crossing the various aforementioned levels of the turbomachine 2.

The primary vein 18 is delimited radially by a radially internal wall 20 and a radially external wall 22. The radially internal wall 20 is carried by the internal casing 12. The radially external wall 22 is carried by the external casing 24. The primary air flow F1 enters the primary vein 18 through an annular air inlet 17 and escapes through a primary nozzle 19 which is arranged downstream of said primary vein 18. The primary flow F1 can be accelerated by the primary nozzle 19 so as to generate a thrust reaction necessary for the flight of the aircraft.

The turbomachine comprises a rotating casing 26 centered on the longitudinal axis X and rotating around the latter. The rotating casing 26 carries a crown of movable blades 28 forming the propeller 14. The rotating casing 26 is mounted movable relative to the internal casing 12 which carries it.

The air flow F entering the turbomachine passes through the blades 28 of the propeller 14 to form the secondary air flow F2. The latter circulates around the external casing 24. Each blade 28 of the propeller 14 comprises a root 30 and an aerodynamic part extending radially outwards from the root 30, the latter comprising a pivot. Indeed, the root 30 is pivotally mounted about an axis A (perpendicular to X) thus allowing the blades 28 of the propeller 14 to pivot. This pivoting is managed by a first variable-pitch system of the turbomachine 2 allowing actuation of the pitch of the blades 28, in particular to ensure their feathering and control their pitch, in order to be able to put said blades 28 back into operation (exit the flag position).

The low pressure compressor 4 and the low pressure turbine 10 are mechanically connected by a low pressure shaft 11, the latter drives the propeller 14 via a reducer 32, the propeller 14 compresses the air outside the external casing 24 and provides the majority of the thrust of the turbomachine 2. The reducer 32 can be of the planetary gear type.

The turbomachine 2 comprises a rectifier 34 crossed by the secondary flow F2, the latter being a part of the air flow F propelled radially outwardly to the longitudinal axis X. The rectifier 34 comprises a plurality of stator blades 36 (or stator vanes or fixed vanes) known by the English acronym “OGV” (Outlet Guide Vane). The stator vanes 36 are regularly distributed around the longitudinal axis X and extend radially in the secondary air flow F2. The stator blades 36 are carried by a fixed structure secured to the external casing 24. In particular, each stator blade 36 extends radially from a foot 38, the latter is pivotally mounted about an axis B (perpendicular to X) allowing the stator blades 36 of the rectifier 34 to pivot. This pivoting is managed by a second variable-pitch system of the turbomachine 2 allowing the pitch of said stator blades 36 to be actuated.

The turbomachine 2 further comprises a fluid pumping assembly 40 for lubricating and/or cooling the components of said turbomachine 2. For this purpose, the assembly 40 comprises a fluid reservoir which preferably corresponds to an auxiliary oil reservoir of the turbomachine 2 arranged in the latter in addition to a main reservoir for supplying its components, i.e. heat exchangers, bearing lubrication chambers, reducers, bearings, etc. Indeed, the auxiliary oil reservoir for its part makes it possible to supply oil to the first and second variable timing systems of the turbomachine 2. Alternatively, the auxiliary oil reservoir can also provide lubrication for some of the components of the turbomachine.

Preferably, the fluid pumping assembly 40 is arranged radially internally to the primary flow vein 18, at right angles to an internal compartment preferentially corresponding to the internal casing 12. The architecture and operation of the assembly 40 will be detailed later in this description.

There schematically represents an enlarged view of the axial section of the turbomachine 2 of the , comprising the fluid pumping assembly 40 according to the invention arranged in the internal casing 12.

In this configuration, the reservoir 42 of the assembly 40 is arranged directly under the internal wall 20, and said assembly 40 comprises a pump 44 fluidly coupled to the reservoir 42 and which is arranged radially under said reservoir 42.

We can see at the a dotted line 50 illustrating a fluid connection between an outlet 46 of the pump 44 and the foot 30 of the blades 28 of the propeller 14. This is a schematic representation of the supply of the first variable-pitch system provided by the assembly 40.

In this regard, the pump 44 may correspond to a pitch actuating pump provided with a by-pass valve allowing the choice between a cooling function or a pitch actuating function of the variable timing system. The latter may comprise a hydraulic actuator driving the pivoting of the feet 30.

Although set 40 is illustrated in the as supplying only the first variable timing system, the assembly 40 according to the invention can for example supply both the first and the second variable timing system of the turbomachine 2. Thus, in this alternative not shown, the outlet 46 of the pump 4 can also be connected to a hydraulic actuator driving the pivoting of the feet 38 of the stator blades 36 of the rectifier 34 of the . In another alternative, assembly 40 may supply only the second variable timing system with a direct connection from output 46 to the latter.

The arrangement of the pump 44 radially under the tank 42 advantageously makes it possible to ensure permanent feeding of the pump 44 by gravity, which makes it possible to prevent said pump 44 from sucking in air bubbles. For this purpose, the first system and/or the second variable timing system of the turbomachine 2 is free of air bubbles.

Indeed, the blade pitch control must be free of air bubbles so that the fluid remains essentially incompressible, so as to avoid any risk of elasticity in the actuation chain of the hydraulic actuators, to ensure reliable blade pitch control.

Advantageously, the position of the assembly 40 in the internal casing 12 directly below the internal wall 20 of the primary vein 18, and preferably in a position axially upstream of the low-pressure compressor, allows both said assembly 40 to be close to the hydraulic actuators of the variable valve timing systems, and to be close to the other components of the turbomachine 2 requiring cooling and/or lubrication. This proximity makes it possible to considerably reduce pressure losses by limiting the presence of long or bent fluid connections. However, traditional pumping systems do not allow access to such an arrangement in the turbomachine 2.

The support of the assembly 40 is preferably achieved by fixing the reservoir 42 to the internal casing 12, but can also be achieved by the pump 44, or both.

Advantageously, the assembly 40 of the invention is capable of being integrated into the internal compartment of the turbomachine 2 having limited space, because it compactly brings together the tank 42 and the pump 44, and this thanks to a connection device visible in FIGS. 3 to 6.

There represents a perspective view of the fluid pumping assembly 40 with the pump 44 coupled to the reservoir 42 illustrated in dotted lines in order to be able to visualize the connection device 52. The represents an exploded view of the assembly 4 of the .

With reference to Figures 3 and 4, the reservoir 42 preferably comprises a narrow lower part 41 receiving the connection device 52 by insertion through an orifice 43 formed in the reservoir 42.

The pump 44 is preferably electrically driven by an electric motor 45 directly connected to the pump 44, which makes it possible to further optimize the space requirement. In an alternative not shown, the electric motor 45 can be positioned on either side of the pump 44, so as to balance the assembly and improve the mechanical strength at the connection device 52.

Preferably, the pump 44 comprises an inlet 47 for the fluid provided with a projecting element 48 extending from said pump 44 and forming a supply channel 49 intended to convey the fluid from an internal enclosure for the fluid of the reservoir 42 towards the outlet 46.

The connection device 52 corresponds to an interface between the pump 44 and the tank 42, said device 52 comprises an external portion 54 provided with a fixing flange 56 ensuring a fixing, preferably, by screwing to the tank 42. The external portion 54 is intended to remain outside the enclosure of the tank 42 when the pump 44 is coupled to said tank 42.

In this configuration, the outer portion 54 is provided with a tubular portion extending through the flange 56 and comprising at an outer end 55 a coupling flange 58 for ensuring attachment to the pump 44.

In this regard, the pump 44 advantageously comprises an annular rib 60 arranged between the projecting element 48 and the pump 44, so that when the pump is connected to the reservoir 42, said annular rib 60 bears directly against the coupling flange 58. Preferably, the coupling flange 58 and the rib 60 comprise an identical diameter and a similar shape.

Advantageously, the coupling of the pump 44 with the reservoir 42 is securely maintained by means of a retaining collar 62 provided with an internal groove having a V-shaped section. The collar 62 preferably corresponds to a “V-band” type collar, and makes it possible to ensure axial clamping between the annular rib 60 and the coupling flange 58 when the pump 44 is coupled to the reservoir 42 (the term axial here refers to an axis of revolution of each of the flange 58 and rib 60).

The direct attachment of the pump 44 to the tank 42 secured by the retaining collar 62 advantageously allows the assembly 40 to be free of pipes between these two elements. Thus, the assembly 40 requires few components, which allows it to be compact. In addition, the disassembly (uncoupling) of the pump 44 is possible by simply unscrewing a clamping screw mounted on the collar 62. Alternatively, the retaining collar 62 may be free of clamping screws and may instead comprise a manual quick-tightening system of the flange and/or lever type. This would ensure manual and tool-free uncoupling of the pump 44.

In parallel with the attachment system between the pump 44 and the tank 42, the connection device 52 further comprises a cage 64 for guiding a self-sealing safety valve 66, the latter being normally closed and configured to be held in the open position when the pump 44 is coupled to the tank 42 and to close the tank 42 when the pump 44 is uncoupled from said tank 42. The operation of the valve 66 is detailed below according to FIGS. 5 and 6.

There represents a sectional view of the assembly 40 in which the pump 44 is coupled to the reservoir 42, the valve 66 being held in the open position.

It can be seen that the cage 64 of the connection device 52 extends entirely within the enclosure of the tank 42, said cage 64 comprises an end wall 65 making it possible to ensure the guiding of the valve 66 between the open and closed position.

The valve 66 preferably corresponds to a disk rigidly connected to a spring 68 extending into the enclosure of the tank 42, the spring 68 being centered around a rod 70 fixed to the valve 66 and slidably mounted with the end wall 65.

The connecting device 52 comprises a seat 72 formed at an inner end 57 of the outer portion 54. Thus, the valve 66 is in the closed position when it is in direct contact with the seat 72 (as illustrated in ).

In the configuration illustrated in the , the suction channel 49 is inserted into the tubular portion 53 until the annular rib 60 rests with the coupling flange 58 for holding the latter two by the collar 62. The projecting element 48 pushes the valve 66 in order to ensure a fluid connection between the pump 44 and the reservoir 42.

In this regard, the projecting element 48 preferably comprises a ring integral with the pump 44 by means of at least two feet 74 forming at least two windows 76 for the passage of the fluid when the valve 66 is in the open position. More preferably, the projecting element 48 extends in the extension of the extent of the suction channel 49, by means of three or four feet 74.

The windows 76 for the passage of the fluid are preferably four in number, and can be covered by a strainer or a filter capable of preventing the circulation of possible impurities towards the variable timing systems of the turbomachine.

Advantageously, the 76 windows make it possible to maximize the fluid passage section to ensure suction flow rates ranging from 1 to 2000 l/h, and also make it possible to achieve a pressure of up to 10 bars.

Advantageously, the fluid connection between the pump 44 and the reservoir 42 can be optimized as needed, for example, the lengths of the feet 74 can be greater to present windows 76 of larger sections and thus ensure a greater flow rate of fluid circulation, and vice versa.

The cage 64 is connected to the external portion 54, and particularly to its internal end 57. For this purpose, the cage 64 is attached to the external portion 54 or formed with it. Preferably, the cage 64 is integral with the device 52.

In this configuration, the end wall 65 extends in the extension of the extent of the tubular portion 53, by means of at least two supports 78 forming auxiliary windows 80, the latter being wider than the windows 76 formed at the level of the fluid inlet 47 of the pump 44. The supports 78 may be three or four in number, or even more, and are preferably the same number as the feet 74.

The coupling of the pump 44 with the tank 42 is sealed. Indeed, the sealing is guaranteed by the integration of O-rings in grooves 82 provided around the suction channel 49, the sealing is also ensured at the level of the fixing of the flange 56 comprising a sealing plate interposed between the tank 42 and said flange 56.

Furthermore, the coupling flange 58 and/or the annular rib 60 may comprise an indexing pin (not shown) capable of engaging in a corresponding orifice, said pin may facilitate the coupling of the pump 44 to the reservoir 42 and makes it possible to guarantee a fixed and precise position in which the assembly 40 does not risk coming into conflict with its environment within the turbomachine.

Alternatively, and as required, the pump 44 is capable of reversing direction and thus filling the reservoir 42 with fluid. In this regard, the connection device 52 advantageously makes it possible to ensure circulation of the fluid through the windows 76 in both directions (to and from the reservoir 42).

There represents a sectional view of the assembly 4 in which the pump 44 is uncoupled from the reservoir 42, and the valve 66 is in the closed position.

In this configuration, the valve 66 is pressed by the spring 68 against the seat 72 and takes its shape. The contact between the valve 66 and the seat 72 is preferably of the metal-to-metal type, not allowing the passage of fluid through the tubular portion 53.

Advantageously, the pump 44 is uncoupled by simply removing the retaining collar and manually disengaging the suction channel 49 from the reservoir 42. This directly causes the valve 66 to be pressed against the seat 72. Thus, the pumping assembly 40 has no need for secondary safety or the need to drain the reservoir 42 prior to uncoupling the pump 44.

In order to avoid any minor leakage of fluid when uncoupling the pump 44, the retaining collar may comprise a collar having, for example, a gutter shape placed under its internal V-shaped groove, to collect the fluid which may escape between the flange 58 and the rib 60.

The fluid pumping assembly 40 makes it possible to ensure a considerable saving of time during maintenance, because the steps of assembly and disassembly of the pump 44 are facilitated and secured, which makes it possible to promote a presence of the assembly 40 at the level of the internal compartment which previously presented a difficult space for traditional assemblies whose maintenance is not as facilitated as that of the assembly 40 of the invention.

Advantageously, the assembly 40 includes reduced installation clearances by means of the connection device 52 ensuring an optimized interface between the pump 44 and the tank 42 which do not require any routing of additional pipes. The assembly 40 advantageously ensures a gain in mass and compactness.

The turbomachine of the invention is capable of ensuring continuous and secure operation of its variable timing systems thanks to the fluid pumping assembly 40 according to the invention making it possible to ensure a supply of such systems with pure fluid without any presence of air and without interruption of supply.

Claims (15)

Fluid pumping assembly (40) intended to be arranged in a compartment (12) of a turbomachine (2), comprising:
- a fluid reservoir (42);
- a pump (44) fluidically coupled to the fluid reservoir (42) by means of a connection device (52);
characterized in that
the connecting device (52) comprises:
- a normally closed valve (66), configured to be maintained in the open position when the pump (44) is coupled and to close the reservoir (42) when the pump (44) is uncoupled from said reservoir (42). Assembly (40) according to claim 1, in which the connecting device (52) comprises a seat (72) and a spring (68) pressing the valve (66) towards said seat (72) in the closed position of the tank (42). An assembly (40) according to claim 2, wherein the pump (44) comprises a projecting element (48) adapted to contact and move the valve (66) towards the open position when said pump (44) is coupled to the reservoir (42). Assembly (40) according to claim 3, in which the projecting element (48) comprises a ring integral with the pump (44) by means of at least two feet (74) forming at least two windows (76) for the passage of fluid when the valve (66) is in the open position. Assembly (40) according to one of claims 2 to 4, in which the valve (66) and the spring (68) are located on one side of the seat (72) corresponding to the reservoir (42). Assembly (40) according to one of claims 1 to 5, in which the connection device (52) comprises a cage (64) capable of guiding the valve (66) between the closed position and the open position. Assembly (40) according to one of claims 2 to 5 and according to claim 6, in which the connection device (52) comprises an external portion (54) with a fixing flange (56) to the tank (42), the seat (72) being formed on said external portion (54) and the cage (64) being linked to said external portion (54). An assembly (40) according to claim 7, wherein the connecting device (52) comprises a tubular portion (53) extending through the fixing flange (56) and forming the seat (72) at an inner end (57) of the outer portion (54). Assembly (40) according to claim 8, in which the tubular portion (53) comprises at an outer end (55) a coupling flange (58) with the pump (44). An assembly (40) according to claim 9, wherein the pump (44) further comprises an annular rib (60) disposed between the projecting element (48) and the pump (44), such that when the pump (44) is connected to the reservoir (42), said annular rib (60) bears directly against the coupling flange (58). An assembly (40) according to claim 10, wherein said assembly (40) further comprises a retaining collar (62) provided with an internal groove having a V-shaped section, intended to provide axial clamping between the annular rib (60) and the coupling flange (58) when the pump (44) is coupled to the reservoir (42). An assembly (40) according to claim 11, wherein at least one of the coupling flange (58) and the annular rib (60) comprises an indexing pin capable of engaging in a corresponding orifice. Turbomachine (2) comprising:
- an unducted propeller (14) propelling an incoming air flow (F), said propeller (14) comprising a variable pitch system for actuating the pitch of the blades (28) of the propeller (14);
- a fluid pumping assembly (40) comprising a fluid reservoir (42);
characterized in that the fluid pumping assembly is according to one of claims 1 to 12. Turbomachine (2) according to claim 13, in which the fluid pumping assembly (40) is arranged radially internally to a primary flow vein (18), at right angles to an internal compartment (12) of the turbomachine (2). Turbomachine (2) according to one of claims 13 or 14, in which the variable timing system is a first variable timing system, and said turbomachine (2) further comprises a rectifier (34) comprising a plurality of stator vanes (36) extending from an external casing (24), said rectifier (34) comprising a second variable timing system, the pump (44) being fluidically connected to the components of the first system and/or of the second variable timing system of the turbomachine (2).