EP4150199A1

EP4150199A1 - Aircraft turbomachine comprising a device for lubricating a bearing

Info

Publication number: EP4150199A1
Application number: EP21732442.5A
Authority: EP
Inventors: Julien Fabien Patrick Becoulet; Serge René Morreale; Olivier Renon
Original assignee: Safran Aircraft Engines SAS
Current assignee: Safran Aircraft Engines SAS
Priority date: 2020-05-13
Filing date: 2021-05-09
Publication date: 2023-03-22
Also published as: WO2021229167A1; FR3110194A1; CN115516196A; FR3110194B1; US20230184167A1

Abstract

The invention relates to a turbomachine (1) for an aircraft, comprising: a first rotor (8) comprising a first shaft (80), a second rotor (9) comprising a second shaft (90), a mechanical reduction gearing (14) having an epicyclic gear set comprising a sun gear (41) connected to the second shaft (90), a ring gear (42) connected to the first shaft (80), and planet gears (43) located between the sun gear (41) and the ring gear (42) and borne by a planet carrier (43a) attached to a stator of the turbomachine (1), rolling-element bearings (15, 82, 83) for guiding said first shaft (80) and second shaft (90) in rotation, an annular gutter (17) which extends around the ring gear (42) of the reduction gearing (14) and which is configured to recover oil for lubricating the reduction gearing (14) that is sprayed by centrifugal action out from the ring gear (42) during operation, and an annular bearing support (16) which is attached, with the gutter (17), to a stator of the turbomachine and which supports at least one of said bearings (15), characterized in that it also comprises: at least one device (19) for conveying oil recovered by said gutter (17), which device is borne by said annular support (16) and extends as far as said at least one bearing (15) in order to lubricate the latter.

Description

DESCRIPTION

TITLE: AIRCRAFT TURBOMACHINE INCLUDING A BEARING LUBRICATION DEVICE

Technical field of the invention

The invention relates to the technical field of aircraft turbomachines. More particularly, the invention relates to the field of aircraft turbomachines comprising a contra-rotating turbine.

Technical background

The state of the art is illustrated by documents EP-A1-3 575 562, US AI -2015/361829, FR-A1-2 977 636 and EP-A1-3 460 199.

Conventionally, an aircraft turbomachine comprises, from upstream to downstream, in the direction of gas flow, a fan, a low pressure compressor, a high pressure compressor, an annular combustion chamber, a high pressure turbine and a low pressure turbine. The rotor of the low pressure compressor is driven by the rotor of the low pressure turbine, and the rotor of the high pressure compressor is driven by the rotor of the high pressure turbine.

From an engine performance and fuel consumption point of view, it is advantageous to maximize the rotational speed of the low pressure turbine as this results in better turbine efficiency. However, increasing the rotational speed of the turbine involves increasing the centrifugal forces it undergoes, and therefore greatly complicates its design.

One suggestion for increasing the efficiency of a turbine without increasing its rotational speed is to use a counter-rotating turbine. The low pressure turbine is then replaced by a turbine with two rotors, a first rotor of which is configured to rotate in a first direction of rotation and is connected to a first turbine shaft, and a second rotor configured to rotate in an opposite direction of rotation. be linked to a second turbine shaft. The first and second turbine shafts are centered and guided in rotation by a plurality of guide bearings. The first rotor has turbine wheels interposed between turbine wheels of the second rotor. A low-pressure turbine can have a take-off rotational speed of the order of 4,000 revolutions per minute in a conventional architecture where the turbine directly drives the fan or a take-off rotational speed of the order of 10,000 revolutions per minute in a architecture where the turbine drives the fan via a reduction gear. Its replacement by a counter-rotating turbine whose rotors rotate respectively at take-off speeds of the order of 3,000 and 7,000 revolutions per minute makes it possible to have a relative speed of 10,000 revolutions per minute (3000 + 7000) while having an absolute speed in a low slice of the aforementioned speed interval. This contra-rotating turbine thus comprises a slow rotor and a fast rotor, the slow rotor driving the fan and the fast rotor meshing with a mechanical reduction gear with planetary type epicyclic gear whose input and output are counter-rotating (rotating ring, planet carrier fixed, rotating solar). The reducer couples the fast rotor and the slow rotor, allowing a transfer of power from the fast rotor to the slow rotor. We take advantage of the higher yields of a fast turbine while transferring a large part of the power from the turbine to the fan without passing through a reduction gear but through a shaft. This architecture is complex due to its mechanical integration: the mechanical reduction gear is for example located downstream of the turbomachine, radially inside an annular stator casing called the exhaust casing or upstream of the turbomachine. radially inside an annular stator casing called the intermediate casing. In addition, since the reducer releases a considerable amount of energy (of the order of 100 kW) in operation, it must be lubricated continuously in order to maintain an acceptable operating temperature. An oil circuit is therefore implemented in order to supply the gearbox with oil. Evacuation of oil is a major problem. In fact, the quantity of oil necessary for the operation of the reducer is large and its evacuation is therefore complex since it requires cumbersome evacuation devices that are difficult to use in such an environment.

Furthermore, the rotational guide bearings of the first and second turbine shaft must also be lubricated with lubricating oil. The routing of lubricating oil to the guide bearings is also a major problem. Indeed, the quantity of oil to be delivered to the guide bearings is important in this type of configuration. The routing devices are therefore complex to implement in this type of environment, like oil drainage devices.

There is then a need to provide a turbomachine in which the lubricating oil of the reduction gear can be easily recovered and discharged and in which the bearings can be easily lubricated.

Summary of the invention

To this end, the invention proposes a turbomachine for an aircraft, comprising:

- a first rotor comprising a first shaft,

- a second rotor comprising a second shaft,

- a mechanical gearbox with an epicyclic train comprising a sun connected to the second shaft, a crown connected to the first shaft, and satellites located between the sun and the crown and carried by a planet carrier fixed to a stator of the turbomachine,

- rolling bearings for guiding the rotation of said first and second shafts,

- an annular gutter which extends around the crown of the reducer and which is configured to collect lubricating oil from the reducer which is projected by centrifugation outside the ring in operation, and

an annular bearing support (s) which is fixed with the gutter to a stator of the turbomachine and which supports at least one of said bearings. The turbomachine is distinguished in that it further comprises at least one device for conveying oil recovered by said gutter, which is carried by said annular support and which extends to said at least one bearing with a view to its lubrication.

The turbomachine therefore includes a gutter for recovering the lubricating oil from the gearbox. According to the invention, the turbomachine also comprises a device for conveying at least part of the oil recovered by the gutter which extends to the bearing. The routing device thus makes it possible to use the gearbox lubricating oil collected by the gutter to lubricate the bearing. Thanks to the invention, it is therefore possible to dispense with a specific supply of oil to lubricate the bearing, offering considerable cost savings.

Also, since part of the gear lubricating oil is used to lubricate the bearing, the total amount of oil to be injected and discharged is reduced. The oil to be injected and discharged is conveyed by an oil circuit passing through the arms of a casing of the turbomachine. It is therefore possible to reduce the size of the circuit, facilitating its integration into the arms of the turbomachine casing.

The turbomachine according to the invention may include one or more of the following characteristics, taken in isolation from one another or in combination with one another:

- The routing device comprises a sampling scoop configured to take oil recovered by the gutter, the scoop being provided in an annular side wall of the gutter; - the routing device comprises at least one pipe for conveying the oil taken by the scoop up to said at least one bearing, the pipe extending between a first end connected to the gutter and a second end extending to the bearing;

- the delivery pipe has a generally helical shape around a longitudinal axis of the turbomachine;

- the delivery pipe is formed in a rib projecting on an internal annular surface of said annular support, or by a tube carried by the annular support;

- the delivery device comprises at least one oil nozzle towards said at least one bearing, the nozzle being carried by said annular support;

- Said at least one nozzle has a generally rectilinear or angled shape;

- The first shaft is fixed to the crown and extends at least in part between the reduction gear and said annular support, this first shaft being guided by said at least one bearing supported by this annular support and lubricated by said device;

- Said at least one nozzle is interposed axially between said at least one bearing and a dynamic annular seal mounted around the first shaft;

an annular casing which extends at least in part around the reduction gear and to which said annular support and said gutter are fixed, this annular casing comprising arms extending radially with respect to a longitudinal axis of the turbomachine and passing through a duct of flow of a gas flow inside the turbomachine.

Brief description of the figures

Other characteristics and advantages will emerge from the following description of a non-limiting embodiment of the invention with reference to the accompanying drawings in which:

[Fig.1] Figure 1 is a very schematic representation of an aircraft half turbomachine according to the invention;

[Fig.2] Figure 2 is an enlarged schematic representation of part of the turbomachine of Figure 1; [Fig.3] Figure 3 is an enlarged view of part of Figure 2;

[Fig.4] Figure 4 is a perspective view of an element of the invention shown in Figure 3;

[Fig.5] Figure 5 is another perspective view of an element of the invention shown in Figure 3;

[Fig.6a] Figure 6a is a schematic representation of a first embodiment of a nozzle that can equip the invention;

[Fig.6b] Figure 6b is a schematic representation of a second embodiment of a nozzle that can equip the invention;

Detailed description of the invention

An aircraft turbomachine 1 is for example shown in Figure 1. The turbomachine 1 is for example a turbomachine 1 with a counter-rotating turbine. The turbomachine 1 extends along a longitudinal axis A.

The turbomachine 1 comprises, from upstream to downstream in the direction F of gas flow, a fan 2, a low pressure compressor 3, a high pressure compressor 4, an annular combustion chamber 5, a high pressure turbine 6 and a counter-rotating turbine 7.

The turbomachine 1 further comprises a plurality of structural housings. For example, it comprises an intermediate casing 10 arranged between the low pressure compressor 3 and the high pressure compressor 4. The turbomachine 1 further comprises a turbine casing 12. The turbine casing 12 is for example equipped with arms forming vanes of rectifier and is called TVF (for T urbine Vane Frame in English). The turbine casing 12 is arranged between the high pressure turbine 6 and the counter-rotating turbine 7. The turbomachine 1 further comprises an exhaust casing 13. The exhaust casing 13 is for example the last turbine casing and is called TRF (for Turbine Rear Frame in English).

The high pressure turbine 6 comprises a rotor which drives a rotor of the high pressure compressor 4 in rotation via a high shaft pressure 60. The high pressure shaft 60 is centered and guided in rotation by high pressure bearings, such as an upstream high pressure bearing 61 and a downstream high pressure bearing 62. The upstream high pressure bearing 61 is for example a high pressure bearing. balls and the downstream high pressure bearing 62 is for example a roller bearing. The upstream high pressure bearing 61 is mounted between an upstream end of the high pressure shaft 60 and the intermediate casing 10.

The counter-rotating turbine 7 comprises a first rotor 8 comprising a first shaft 80 and a second rotor 9 comprising a second shaft 90.

More particularly, the first rotor 8 comprises a first series of wheels 81 configured to rotate in a first direction of rotation and connected to the first shaft 80. The second rotor 9 comprises a second series of wheels 91 configured to rotate in a direction opposite to the first. direction of rotation and connected to the second shaft 90. The wheels 91 of the second series are interposed between the wheels 81 of the first series.

Each wheels 81, 91 comprises an annular row of blades each comprising an aerodynamic profile having an intrados and an extrados which meet to form a leading edge and a trailing edge of the gases in a vein of the counter-rotating turbine 7.

The first shaft 80 rotates the fan 2 as well as the rotor of the low pressure compressor 3.

In addition, the turbomachine 1 comprises rolling bearings for guiding the rotation of the first shaft 80 and second shaft 90.

For example, in a manner not shown, the second shaft 90 is centered and guided in rotation by means of two upstream and downstream guide roller bearings.

The first shaft 80 is centered and guided in rotation downstream by at least one guide bearing, for example by at least one downstream guide bearing 15 visible in Figure 2.

The first shaft 80 is centered and guided in rotation upstream by two upstream guide bearings 82, 83 mounted between the upstream end of the first shaft 80 and the intermediate casing 10. In addition, the turbomachine 1 comprises a mechanical reduction gear 14 with an epicyclic train. As best seen in Figure 2, the reducer 14 comprises a sun 41 connected to the second shaft 90, a ring 42 connected to the first shaft 80 and satellites 43 located between the sun 41 and the ring 42 and carried by a satellite carrier 43a fixed to a stator of the turbomachine 1.

More particularly, the first shaft 80 has a downstream end 80a fixed to an upstream end of a ring holder 42a of the ring 42 and an upstream end 80b fixed to the last stage of the first rotor 81 of the first turbine 8 as shown in FIG. 1.

The turbine housing 12 and the exhaust housing 13 comprise a central hub, as well as an outer ring which surrounds the hub and which is connected to it by a series of arms 13a. The arms 13a are substantially radial or inclined relative to the longitudinal axis A of the turbomachine 1 and pass through the vein of the turbine. The central hub of the exhaust housing 13 extends around at least a portion of the reduction gear 14.

The downstream bearing 15 is located downstream of the reduction gear 14. The downstream bearing 15 is supported by an annular bearing support 16 fixed to a stator of the turbomachine 1, for example to the exhaust casing 13. The first shaft 80 extends. at least partly between the reducer 14 and the support 16.

Furthermore, an annular dynamic seal 23 is mounted around the first shaft 80. The dynamic seal 23 is for example a segmented radial seal (JRS). The dynamic seal 23 is for example made of carbon. The dynamic seal 23 is for example housed in a groove 231 formed in a flange 232 of a fixed structure connected to the stator of the turbomachine 1, for example to the exhaust casing 13 and to the support 16.

In operation, the reducer 14 is lubricated and the oil which lubricated the reducer must be recovered and removed for recycling to prevent this oil from accumulating in the reducer 14 and turning into coke under the effect of high temperatures.

For this purpose, the turbomachine 1 comprises an annular gutter 17 which extends around the ring 42 of the reducer 14 and which is configured to recover the lubricating oil from the reducer 14 which is projected by centrifugation outside the ring gear 42 in operation as illustrated by the rounded arrow in FIG. 2.

More particularly, the oil is centrifuged and is found in the ring 42 of the reducer 14. As best seen in FIG. 3, passages 42b can be provided at the outer periphery of the ring 42 so as to project the oil by centrifugation. on the gutter 17 extending opposite these passages 42b. The passages 42b are for example oriented radially with respect to the longitudinal axis A of the turbomachine 1.

The gutter 17 is fixed with the annular bearing support 16 to the stator of the turbomachine 1, for example to the exhaust casing 13.

As best seen in Figures 4 and 5, the gutter 17 has a side annular wall 17c. The gutter 17 also has an internal annular surface 17d and an external annular surface 17e.

The gutter 17 is for example formed by assembling a first annular wall 17a and a second annular wall 17b mounted coaxially one inside the other. The first annular wall 17a is for example formed by the support 16.

Each of the walls 17a, 17b includes an annular discharge rib 174 projecting radially inward.

The annular discharge ribs 174 axially define between them an oil recovery space E. The space E is radially delimited by the internal annular surface 17d.

In addition, the outer annular surface 17e is advantageously coated with an annular coating 24 of thermal insulation. The annular coating 24 is thus arranged radially between the exhaust casing 13 and the gutter 17. The annular coating 24 is separated from the exhaust casing 13 by an annular space free of air circulation and ventilation, for example.

The second wall 17b comprises an upstream end 171 and a downstream end 172. The upstream end 171 of the second wall 17b is engaged. axially in an annular groove 18a of a member 18 fixed to an upstream flange 13b of the exhaust casing 13 by means of a fixing flange 18b. The upstream flange 13b of the exhaust casing 13 is located substantially in line with the arms 13a of the exhaust casing 13. Preferably, an annular seal is arranged in the groove 13a and is in axial abutment against the upstream end 171 of the second. wall 17b. The downstream end 172 of the second wall 17b comprises a flange fixing to a downstream flange 13c of the exhaust casing 13, located substantially to the right of the arms 13a. The first wall 17a comprises a flange for fixing to the downstream flange 13c of the exhaust casing 13.

The fixing flange forms a cylindrical rim 173 facing upstream intended to cooperate with the second wall 17b.

The gutter 17 includes openings (not shown) which allow the passage of oil to the discharge ducts (not shown). The ducts pass through the arms 13a of the exhaust casing 28. The gutter 17 advantageously comprises an oil recovery chamber (not shown) located in the lower part. The recovery chamber ensures the tranquilization of the oil, that is to say part of its degassing or deaeration in order to reduce the number of air bubbles in the oil. Thus, the oil passes through the openings which communicate with the recovery chamber before being discharged through the ducts through the arms 13a of the exhaust housing 13 for example.

In order to reduce the total quantity of oil to be conveyed and the quantity of oil to be discharged through the arms 13a, and thus reduce the size of the ducts passing through the arms 13a, according to the invention, the turbomachine further comprises at least a device 19 for conveying oil recovered by the gutter 17 carried by the annular support 16 and which extends to at least one guide bearing, for example up to the downstream guide bearing 15 with a view to its lubrication . As shown in Figure 4, the device 19 comprises for example a scoop 20 for sampling, at least one pipe 21 for conveying the oil and at least one nozzle 22 of oil (Figure 2) to the guide bearing such than the downstream guide bearing 15 in rotation of the first shaft 80.

The scoop 20 is configured to take oil collected by the gutter 17. The scoop 20 is provided in the side annular wall 17c of the gutter 17, for example of the first wall 17a.

The scoop 20 is in fluid communication with the pipe 21. The pipe 21 allows the oil taken by the scoop 20 to be conveyed to the guide bearing, for example to the downstream guide bearing 15.

As shown for example in Figure 5, the pipe 21 has a helical shape around the longitudinal axis A of the turbomachine 1. The helical shape of the pipe 21 makes it possible to limit the pressure drops of the oil taken by the scoop 20 during its delivery to the guide bearing. The pipe 21 extends between a first end 21a connected to the gutter 17 and a second end 21b extending to the downstream bearing 15. The second end 21b is connected to the nozzle 22. More particularly, the first end 21a is connected to the first wall 17a of the gutter 17 and the second end 21b is connected to the nozzle 22, the pipe 21 extending along the support 16 between the first end 21a and the second end 21b.

In the example of FIG. 5, the pipe 21 is formed in a rib projecting on the internal annular surface 17d of the support 16. For example, the pipe 21 is formed in the rib 174 of the first wall 17a of the gutter 17. and extends into the holder 16.

According to another example not shown, the pipe 21 is formed by a tube carried by the support 16.

The nozzle 22 makes it possible to distribute the oil conveyed by the pipe 21 to the bearing 15. The nozzle 22 is for example carried by the support 16. The nozzle 22 is fixed to a downstream end of the support 16. The nozzle 22 is interposed axially between the bearing 15 and the dynamic seal 23. In order to limit the projections of oil on the dynamic seal 23, a worm can be placed against the dynamic seal 23.

More particularly, the nozzle 22 comprises a cylindrical body 22a and an ejection nozzle 22b.

According to a first exemplary embodiment shown in FIG. 6a, the nozzle 22 has a generally rectilinear shape. Thus, the cylindrical body 22a and the ejection nozzle 22b extend along the same axis perpendicular to the axis of the turbomachine 1. According to another exemplary embodiment shown in FIG. 6b, the nozzle 22 has a generally angled shape. The ejection nozzle 22b thus extends radially relative to the cylindrical body 22a so that the ejection nozzle 22b extends parallel to the longitudinal axis A of the turbomachine 1. The ejection nozzle 22b is according to this example oriented towards the bearing 15. This configuration makes it possible to maximize the quantity of oil distributed to the bearing 15 in particular in the event of a pressure drop during the delivery of the oil in the pipe 21 resulting in too much pressure. weak in the nozzle 22.

The invention thus implements the gutter 17 which makes it possible to recover the lubricating oil from the reducer 14 in order to limit the risks of coke formation in the reducer 14. A part of this oil is conveyed by the device 19 to the device. guide bearing, for example to the downstream guide bearing 15 in rotation of the first shaft 80 in order to lubricate it. In particular, the part of the oil conveyed is first taken from the gutter 17 by the scoop 20 which communicates with the pipe 21 allowing the oil to be conveyed to the nozzle 23 distributing the oil taken from the bearing. downstream guide 15. Consequently, the amount of oil remaining in the gutter 17 and discharged is less. The ducts of the gutter 17 extending into the arms 13a of the exhaust casing 13 can thus be sized to evacuate a smaller quantity of oil. This results in less bulky ducts which can be integrated into the exhaust casing 13. Also, the costs associated with the lubrication of the reducer 14 and of the bearing are reduced since the total quantity of oil introduced is reduced thanks to the reuse of part of the lubricating oil of the reducer 14. Furthermore, the invention has been described in relation to a turbomachine 1 in which the reducer 14 is located downstream of the turbomachine 1 and is surrounded by the exhaust casing 13. The invention also applies to a turbomachine in which the reducer 14 is located upstream of the turbomachine 1 and is surrounded by the intermediate casing 10 According to this embodiment, the gutter 17 and the support 16 are fixed to the intermediate casing 10. The same advantages result from this embodiment.

Claims

1. Turbomachine (1) for an aircraft, comprising:

- a first rotor (8) comprising a first shaft (80),

- a second rotor (9) comprising a second shaft (90),

- a mechanical gearbox (14) with a planetary gear comprising a solar (41) connected to the second shaft (90), a ring (42) connected to the first shaft (80), and satellites (43) located between the solar (41) and the ring gear (42) and carried by a planet carrier (43a) fixed to a stator of the turbomachine (1),

- bearings (15, 82, 83) with rolling guide bearings in rotation of said first (80) and second shafts (90),

- an annular gutter (17) which extends around the crown (42) of the reducer (14) and which is configured to recover lubricating oil from the reducer (14) which is projected by centrifugation outside of the crown (42) in operation, and

- a support (16) annular bearing (s) which is fixed with the gutter (17) to a stator of the turbomachine (1) and which supports at least one of said bearings (15), characterized in that it comprises in outraged :

- at least one device (19) for conveying oil recovered by said gutter (17), which is carried by said annular support (16) and which extends to said at least one bearing (15) with a view to its lubrication.

2. Turbomachine (1) according to claim 1, characterized in that the delivery device (19) comprises a scoop (20) for sampling configured to take oil recovered by the gutter (17), the scoop ( 20) being formed in a lateral annular wall (17c) of the gutter (17).

3. Turbomachine (1) according to the preceding claim, characterized in that the delivery device (19) comprises at least one pipe (21) for routing the oil taken by the scoop (20) to at least one bearing (15), the pipe (21) extending between a first end (21a) connected to the gutter (17) ) and a second end (21b) extending to the bearing (15).

4. Turbomachine (1) according to the preceding claim, characterized in that the delivery pipe (21) has a generally helical shape around a longitudinal axis (A) of the turbomachine (1).

5. Turbomachine (1) according to one of claims 3 or 4, characterized in that the delivery pipe (21) is formed:

- in a rib (174) projecting on an internal annular surface (17d) of said annular support (16), or

- By a tube carried by the annular support (16).

6. Turbomachine (1) according to any one of the preceding claims, characterized in that the delivery device (19) comprises at least one nozzle (22) of oil to said at least one bearing (15), the nozzle (22) being carried by said annular support (16).

7. Turbomachine (1) according to the preceding claim, characterized in that said at least one nozzle (22) has a generally rectilinear or bent shape.

8. Turbomachine (1) according to any one of the preceding claims, characterized in that the first shaft (80) is fixed to the crown (42) and extends at least in part between the reduction gear (14) and said support. annular (16), this first shaft (80) being guided by said at least one bearing (15) supported by this annular support (16) and lubricated by said device (19).

9. Turbomachine (1) according to all of claims 7 and 8, characterized in that said at least one nozzle (22) is interposed axially between said at least one bearing (15) and a dynamic annular seal (23) mounted around of the first tree (80).

10. Turbomachine (1) according to one of the preceding claims, characterized in that it further comprises an annular casing (13) which extends at least in part around the reducer (14) and to which said annular support are fixed. (16) and said gutter (17), this annular casing (13) comprising arms (13a) extending radially with respect to a longitudinal axis (A) of the turbomachine (1) and passing through a flow duct of a gas flow inside the turbomachine (1).