Bearing lubrication assembly and aeroengine

Abstract

A bearing lubrication assembly for lubricating bearings in an aero-engine, comprising an oil supply pipe in communication with a main oil passage in the aero-engine, the oil supply pipe having a first oil supply outlet and a second oil supply outlet; and a valve unit supported by an elastic unit in the oil supply pipe and movable in the oil supply pipe; wherein the valve unit is movable between a first position and a second position under the combined action of an elastic supporting force of the elastic unit and an oil pressure in the main oil passage, the valve unit opens the first oil supply outlet and closes the second oil supply outlet in the first position, and closes the first oil supply outlet and opens the second oil supply outlet in the second position; when oil is sprayed from the first oil supply outlet, the bearings to be lubricated are jet lubricated, and when oil is sprayed from the second oil supply outlet, the bearings to be lubricated are sub-film lubricated. An aero-engine is also provided.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of aero-engines, in particular to a bearing lubrication assembly and an aero-engine. BACKGROUND

[0002] The bearing assembly in an aero-engine is used to support its components, and the normal operation of the bearing requires lubrication by oil. There are two ways of oil supply for the bearing, namely jet lubrication and under-ring lubrication. The determination of the different oil supply ways is usually based on the DN value of the bearing. For example, for a bearing with a DN value greater than 2.0 x 10 6 mm·rpm, the direct jet oil supply way cannot effectively inject oil into the bearing due to the severe air disturbance caused by high speed, so the bearing must adopt the under-ring oil supply lubrication form. For a bearing with low speed, the oil collection efficiency of the under-ring oil supply is low due to insufficient centrifugal force under its own working condition.

[0003] The rotation speed of the oil pump of an aero-engine is extracted from the rotation speed of the high-pressure shaft. Generally, the higher the rotation speed of the engine, the higher the oil pressure provided by the oil pump.

[0004] In a conventional gas turbine engine, the low-pressure rotor has a low rotation speed, and the No2 fulcrum bearing (low-pressure rotor bearing) usually adopts a direct jet form. For a new type of gear transmission turbofan engine (GTF engine), a star or planetary gear box is installed between the low-pressure rotor composed of a low-pressure compressor and a low-pressure turbine and the fan rotor, so that the fan rotor operates at a low rotation speed, and the low-pressure rotor operates at a high rotation speed. Compared with the transmission configuration engine, the working rotation speed and efficiency of the low-pressure rotor are greatly improved. This change makes the DN value of the No2 fulcrum bearing (low-pressure rotor bearing) of the GTF engine in different working conditions such as take-off, cruising, and slow running to be in a cross-threshold state.

[0005] The No2 fulcrum bearing (low-pressure rotor bearing) of the existing GTF engine usually adopts an under-ring oil supply form to ensure good lubrication under the highest rotation speed. However, the inventors have found that this oil supply way usually causes the bearing at a low rotation speed to have a low oil lubrication efficiency due to insufficient centrifugal force, and in an extreme case, it even causes the bearing to have insufficient oil supply, which has a certain impact on the operation of the engine. SUMMARY

[0006] An object of the present application is to provide a bearing lubrication assembly that can improve the lubrication efficiency of the bearing assembly under all working conditions.

[0007] The bearing lubricating assembly is used for lubricating a bearing in an aero-engine, comprising: an oil supply pipe in communication with a main oil passage in the aero-engine, the oil supply pipe being provided with a first oil supply outlet and a second oil supply outlet; and a valve unit supported by an elastic unit in the oil supply pipe and movable in the oil supply pipe; wherein the valve unit is movable between a first position and a second position under the combined action of the elastic support force of the elastic unit and the oil pressure in the main oil passage, the valve unit opens the first oil supply outlet and closes the second oil supply outlet at the first position, and closes the first oil supply outlet and opens the second oil supply outlet at the second position; when oil is sprayed from the first oil supply outlet, the bearing to be lubricated is jet-lubricated, and when oil is sprayed from the second oil supply outlet, the bearing to be lubricated is sub-lubricated.

[0008] In one or more embodiments, the bearing to be lubricated comprises a bearing inner ring, a bearing outer ring and a retainer, the bearing inner ring is mounted on an input shaft, the input shaft has an annular groove at an end opposite to the bearing to be lubricated, and the bearing lubricating assembly further comprises a spray hole provided in the annular groove; wherein the first oil supply outlet is arranged relative to a position between the bearing inner ring and the retainer, and the second oil supply outlet is arranged relative to the spray hole.

[0009] In one or more embodiments, the spray hole is an inclined hole.

[0010] In one or more embodiments, the oil supply pipe comprises a first section and a second section, the inner diameter of the first section is smaller than the inner diameter of the second section, so as to form a stop portion between the first section and the second section; the stop portion limits the stroke of the valve unit in the oil supply pipe, and when the valve unit abuts against the stop portion, the valve unit is at the first position.

[0011] In one or more embodiments, the elastic unit is a spring.

[0012] In one or more embodiments, there is a relationship between the stiffness of the spring, the stroke of the valve unit in the oil supply pipe and the oil supply pressure of the main oil passage as follows:

[0013] K=(P2-P1)×A / L;

[0014] wherein K is the stiffness of the spring, L is the stroke of the valve unit in the oil supply pipe, A is the force receiving area of the valve unit along the direction of the oil supply pipe, P1 is the initial oil supply pressure of the main oil passage, and P2 is the critical oil supply pressure of the main oil passage, which is the oil supply pressure of the main oil passage when the valve unit switches between the first position and the second position.

[0015] In one or more embodiments, the valve unit comprises: a first sealing section; a second sealing section; and an annular groove disposed between the first sealing section and the second sealing section; wherein the first sealing section and the second sealing section have an outer diameter corresponding to an inner wall of the oil supply pipe to form a chamber defined by the first sealing section, the second sealing section, the annular groove and the inner wall, the chamber being in communication with the first oil supply outlet when the valve unit is in the first position; and the chamber being in communication with the second oil supply outlet when the valve unit is in the second position.

[0016] In one or more embodiments, the annular groove is uniformly provided with a plurality of oil outlet holes along the axial and circumferential directions of the valve unit.

[0017] The bearing lubrication assembly described above, on the basis of the under-ring oil supply oil path, integrates an oil supply outlet for directly spraying lubricating oil and a valve element that moves with the change of lubricating oil pressure, so that the engine bearing adopts under-ring oil supply at high speed and direct spraying oil supply at low speed, thereby achieving self-adaptive optimal oil supply and ensuring the lubrication efficiency of the bearing under different speed conditions.

[0018] Another object of the present application is to provide an aero-engine capable of improving the lubrication efficiency of the bearing assembly under all working conditions.

[0019] The aero-engine described above comprises a bearing to be lubricated and the bearing lubrication assembly described above, which lubricates the bearing.

[0020] The bearing lubrication assembly adopted by the aero-engine described above, on the basis of the under-ring oil supply oil path, integrates an oil supply outlet for directly spraying lubricating oil and a valve element that moves with the change of lubricating oil pressure, so that the engine bearing adopts under-ring oil supply at high speed and direct spraying oil supply at low speed, thereby achieving self-adaptive optimal oil supply and ensuring the lubrication efficiency of the bearing under different speed conditions. BRIEF DESCRIPTION OF DRAWINGS

[0021] The above and other features, properties, and advantages of the present application will become more apparent by describing in detail the following embodiments with reference to the attached drawings and examples, in which:

[0022] Figure 1 is a structural schematic view of a part of an aero-engine according to an embodiment.

[0023] Figure 2 is a schematic view of a bearing lubrication assembly according to an embodiment.

[0024] Figure 3 is a schematic view of an oil supply pipe of a bearing lubrication assembly according to an embodiment.

[0025] Figure 4 is a schematic view of a valve unit according to an embodiment.

[0026] Figure 5 is a perspective view of a valve unit according to an embodiment.

[0027] Figure 6 is a schematic view of a valve unit according to an embodiment in a first position.

[0028] Figure 7 is a schematic view of a valve unit according to an embodiment between a first position and a second position.

[0029] Figure 8 is a schematic view of a valve unit according to an embodiment in a second position.

[0030] Symbol legend

[0031] 1 oil supply pipe

[0032] 2 fixing member

[0033] 3 elastic unit

[0034] 4 valve unit

[0035] 5 bearing

[0036] 6 input shaft

[0037] 7 total oil passage

[0038] 11 first oil supply outlet

[0039] 12 second oil supply outlet

[0040] 13 second section

[0041] 14 first section

[0042] 15 stopper portion

[0043] 16 chamber

[0044] 41 oil inlet

[0045] 42 first sealing section

[0046] 43 oil outlet hole

[0047] 44 annular groove

[0048] 44a width

[0049] 45 pressure receiving surface

[0050] 46 second sealing section

[0051] 51 bearing inner ring

[0052] 52 retainer

[0053] 53 bearing outer ring

[0054] 61 Annular Groove

[0055] 62 nozzles

[0056] F Lubricating oil pressure

[0057] L itinerary

[0058] L1 maximum travel

[0059] P1 Initial oil supply pressure

[0060] P2 Critical Oil Supply Pressure

[0061] P3 maximum oil supply pressure Detailed Implementation

[0062] The following discloses various implementations or embodiments of the described subject matter. To simplify the disclosure, specific examples of the elements and arrangements are described below. Of course, these are merely examples and are not intended to limit the scope of protection of this application. Furthermore, reference numerals and / or letters may be repeated in different examples within these disclosures. This repetition is for brevity and clarity and does not in itself indicate a relationship between the various implementations and / or structures to be discussed.

[0063] To improve lubrication of bearings under different operating conditions, one or more embodiments described below provide a bearing lubrication assembly for lubricating the low-pressure rotor bearing 5 in an aero-engine under different operating conditions.

[0064] like Figure 1 As shown, the bearing lubrication assembly includes an oil supply pipe 1, a valve unit 4, and an elastic unit 3. The oil supply pipe 1 is connected to the main oil passage 7 inside the aero-engine and is used to receive lubricating oil from the engine's lubricating oil pump to lubricate the bearing 5. The valve unit 4 is supported by the elastic unit 3 in the oil supply pipe 1 and is movable within the oil supply pipe 1. The oil supply pipe 1 has a first oil supply outlet 11 and a second oil supply outlet 12, forming a first oil passage and a second oil passage, respectively. The first oil passage is defined by the inlet of the oil supply pipe 1, the internal flow path of the oil supply pipe 1, and the first oil supply outlet 11, while the second oil passage is defined by the inlet of the oil supply pipe 1, the internal flow path of the oil supply pipe 1, and the second oil supply outlet 12. When the low-pressure rotor is operating at high speed, the bearing lubrication assembly provides annular lubrication to the bearing 5 through the first oil passage. When the low-pressure rotor is operating at low speed, it provides direct injection lubrication to the bearing 5 through the second oil passage, thus ensuring lubrication efficiency under different operating conditions.

[0065] As the valve unit 4 is elastically supported by the elastic unit 3 and is subjected to the oil pressure F generated by the oil in the oil supply passage 7, the valve unit 4 moves between the first position and the second position under the combined action of the elastic support force of the elastic unit 3 and the oil pressure F. For reference Figures 6 to 8 The different states of the valve unit 4 during movement are schematically shown.

[0066] As shown in Figure 6 the first position, the valve unit 4 opens the first oil outlet 11 and closes the second oil outlet 12, allowing the oil to be sprayed from the first oil outlet 11 to spray lubricate the bearing 5 to be lubricated; as shown in Figure 7 acted upon by the oil pressure F generated by the oil in the oil supply passage 7, the valve unit 4 moves from the first position towards the second position against the elastic support force of the elastic unit 3 and, when it moves between the first position and the second position, the first oil outlet 11 remains open and the second oil outlet 12 remains closed, at which time the oil is still allowed to be sprayed from the first oil outlet 11 to spray lubricate the bearing 5 to be lubricated; as shown in Figure 8 acted upon by the oil pressure F, the valve unit 4 moves to the second position, closing the first oil outlet 11 and opening the second oil outlet 12 to allow the oil to be sprayed from the second oil outlet 12 to sub-lubricate the bearing 5 to be lubricated.

[0067] In one embodiment, the bearing lubrication assembly has a structure as shown in Figure 2 and Figure 3 The internal oil passage of the oil supply pipe 1 is stepped, the oil supply pipe 1 comprises a first section 14 and a second section 13, the inner diameter of the first section 14 is smaller than that of the second section 13 to form a stop portion 15 between the first section 14 and the second section 13.

[0068] The assembly process of the bearing lubrication assembly is as follows: the valve unit 4 is loaded into the second section 13 of the oil supply pipe 1, the valve unit 4 is positioned by the stop portion 15, the elastic unit 3 is then loaded, and then the elastic unit 3 and the valve unit 4 are limited in the second section 13 of the oil supply pipe 1 by the fixing member 2, and the lower end of the second section 13 is blocked. In the assembled state, the valve unit 4 is not subjected to the oil pressure, and as the elastic unit 3 is in a pre-compressed state, it exerts an elastic support force on the valve unit 4 in the direction towards the stop portion 15, the stop portion 15 limits the travel of the valve unit 4 in the oil supply pipe 1, and when the valve unit 4 is abutted against the elastic support force and the stop portion 15, the valve unit 4 is in the first position.

[0069] In one embodiment, the fixing member 2 is a welded plug 2, which is fixedly arranged at the lower end of the second section 13 by welding.

[0070] In Figure 2In the shown embodiment, the elastic unit 3 is a spring, and the diameter of the spring 3 is slightly smaller than the diameter of the second section 13 of the oil supply pipe 1, so that the axis of the elastic unit 3 can be stabilized during the movement of the valve unit 4 between the first position and the second position, and the valve unit 4 can be prevented from being stuck in the oil supply pipe 1.

[0071] In one embodiment, the valve unit 4 has a structure as shown in Figure 4 and Figure 5 The valve unit 4 includes a first sealing section 42, a second sealing section 46, and a ring groove 44. The first sealing section 42 and the second sealing section 46 have an outer diameter corresponding to the inner wall of the second section 13 of the oil supply pipe 1. The ring groove 44 is formed by recessing a portion of the outer periphery of the valve unit 4. The first sealing section 42 is provided with an oil inlet 41, and lubricating oil can flow into the ring groove 44 of the valve unit 4 through the oil inlet 41 from the first section 14 of the oil supply pipe 1 as shown by the arrow 411. One side of the second sealing section 46 is a pressure bearing surface 45 for bearing the pressure of the lubricating oil flowing into the ring groove 44, and the other side is in contact with the elastic unit 3, so as to elastically support the valve unit 4 in the oil supply pipe 1.

[0072] For different engine speed conditions, the oil supply pressure of the lubricating oil pump will change. With the increase or decrease of the speed of the low-pressure rotor under different conditions, the lubricating oil pump pressure will increase or decrease accordingly, so that the lubricating oil pressure applied to the pressure bearing surface 45 increases or decreases. The lubricating oil pressure is transmitted to the elastic unit 3 by the second sealing section 46, so that the elastic unit 3 is compressed to different degrees, and the valve unit 4 slides in the oil supply pipe 1 in the corresponding direction.

[0073] As shown in Figure 4 The ring groove 44 is provided with a plurality of oil outlets 43. Specifically, the plurality of oil outlets 43 are formed in the groove bottom wall of the ring groove 44. The lubricating oil in the ring groove of the valve unit 4 can flow out into the cavity 16 formed by the ring groove 44 and the inner wall of the second section 13 of the oil supply pipe 1 through the plurality of oil outlets 43 as shown by the arrow 412. The lubricating oil flowing into the cavity 16 also generates lubricating oil pressure on the pressure bearing surface 45. The cavity 16 is defined by the lower end surface of the first sealing section 42, the upper end surface (i.e. the pressure bearing surface 45) of the second sealing section 46, the ring groove 44, and the inner wall of the second section 13. Since the first sealing section 42 and the second sealing section 46 have an outer diameter corresponding to the inner wall of the second section 13 of the oil supply pipe 1, they can block the lubricating oil in the cavity 16, and the lubricating oil can only flow out through the first oil outlet 11 or the second oil outlet 12 when the cavity 16 is connected to the first oil outlet 11 or the second oil outlet 12.

[0074] In Figure 4In the shown embodiment, the ring groove 44 is provided with a plurality of oil outlet holes 43 uniformly along the axial and circumferential direction of the valve unit 4, so that the oil outflow is more uniform.

[0075] As shown in the figure, in one embodiment, the bearing 5 to be lubricated comprises a bearing inner ring 51, a bearing outer ring 53 and a retainer 52, the bearing inner ring 51 is mounted on the input shaft 6, the input shaft 6 has a ring groove 61 at the end opposite to the bearing 5 to be lubricated, and the bearing lubricating assembly further comprises a spray hole 62 provided in the ring groove 61. Figure 1

[0076] In the embodiment, the spray hole 62 is a plurality of inclined holes provided in the ring groove 61, so that the oil can be sprayed obliquely from the spray hole 62, and the bearing inner ring 51 can be better lubricated.

[0077] As shown in the figure, in the low-speed working condition of the low-pressure rotor, the valve unit 4 is in the first position, the chamber 16 is in communication with the first oil outlet 11, and the oil flows along the first oil path in the direction indicated by the arrow 111 in the figure, at this time, the second oil outlet 12 is in a closed state, and the oil cannot enter the second oil outlet 12, and only the first oil path can be used to lubricate the bearing 5. The oil is sprayed out between the bearing inner ring 51 and the retainer 52 of the bearing 5 by direct injection under the action of the oil supply pressure, and the bearing 5 is lubricated. Figure 6

[0078] As shown in the figure, in the process of increasing the speed of the low-pressure rotor, the oil pressure increases, the DN value of the bearing reaches a threshold value, and the valve unit 4 is between the first position and the second position, at this time, the chamber 16 is still in communication with the first oil outlet 11, and the second oil outlet 12 is closed by the second sealing section 46, and the oil flows along the first oil path in the direction indicated by the arrow 112 in the figure, and the bearing 5 is still lubricated by direct injection since the DN value of the bearing is in a critical state at this time. It can be understood that the first position described herein refers to the position of the valve unit 4, which closes the second oil outlet 12 and opens the first oil outlet 11, Figure 7 Figure 6 and Figure 7 respectively show two states of the valve unit 4 in the first position.

[0079] As shown in the figure, in the process of increasing the speed of the low-pressure rotor, the oil pressure increases, the DN value of the bearing reaches a threshold value, and the valve unit 4 is between the first position and the second position, at this time, the chamber 16 is still in communication with the first oil outlet 11, and the second oil outlet 12 is closed by the second sealing section 46, and the oil flows along the first oil path in the direction indicated by the arrow 112 in the figure, and the bearing 5 is still lubricated by direct injection since the DN value of the bearing is in a critical state at this time. It can be understood that the first position described herein refers to the position of the valve unit 4, which closes the second oil outlet 12 and opens the first oil outlet 11, Figure 8 ​​​As shown, in the high-speed working condition of the low-pressure rotor, the DN value of the bearing exceeds the threshold value, the valve unit 4 is in the second position under the action of the oil pressure F, the chamber 16 is connected with the second oil supply outlet 12, and the oil flows along the second oil path as indicated by the arrow 121 in the figure. At this time, since the first sealing section 42 closes the first oil supply outlet 11, the oil cannot enter the first oil supply outlet 11 and can only lubricate the bearing 5 through the second oil path. The oil flows to the jet hole 62 in the annular groove 61 through the second oil supply outlet 12, and under the action of the centrifugal force, the oil from the second oil supply outlet 12 is introduced into the bearing inner ring 51 of the bearing 5 to lubricate the bearing 5. It can be understood that the second position described herein refers to the position of the valve unit 4, which closes the first oil supply outlet 11 and opens the second oil supply outlet 12, Figure 8 Only one of the states in which the valve unit 4 is in the second position is shown.

[0080] To ensure that at least one oil supply outlet is in the oil supply state, the width 44a of the annular groove 44 needs to match the distance between the first oil supply outlet 11 and the second oil supply outlet 12, so that when one of the first oil supply outlet 11 and the second oil supply outlet 12 is in the closed state, the other can be connected with the chamber 16 and be in the oil supply state.

[0081] In addition, the position of the stop portion 15 of the oil supply pipe 1 and the maximum compression position of the elastic unit 3 also need to match the oil supply situation to ensure that at least one oil supply outlet is in the oil supply state in any state.

[0082] In an embodiment, by setting the stiffness K of the elastic unit 3 and the stroke L of the valve unit 4 to match the oil supply requirements, the oil supply pressure required for the bearing lubrication assembly to switch between the first oil supply outlet 11 and the second oil supply outlet 12 can be determined, that is, the low-pressure rotor speed corresponding to the switching of the oil supply outlet can be determined. By adaptively selecting the appropriate oil supply mode through the oil supply pressure, in the case of a working condition lower than the threshold requirement of the bearing DN value, the first oil supply outlet 11 is in the oil supply state, and the bearing 5 is lubricated in the form of direct injection; in the case of a working condition higher than the threshold requirement of the bearing DN value, the second oil supply outlet 12 is in the oil supply state, and the bearing 5 is lubricated in the form of under-ring oil supply.

[0083] In an embodiment, the elastic unit 3 is a spring, and the following relationship exists between the stiffness K of the spring, the stroke L of the valve unit 4 in the oil supply pipe 1, and the oil supply pressure of the total oil path 7:

[0084] K = (P2-P1) x A / L

[0085] Where K is the stiffness of the spring, L is the stroke of the valve unit 4 in the oil supply pipe 1, A is the force-bearing area of ​​the valve unit 4 along the direction of the oil supply pipe 1, that is, the area of ​​the end face of the valve unit 4 in contact with the elastic unit 3, P1 is the initial oil supply pressure of the main oil circuit 7, P2 is the critical oil supply pressure of the main oil circuit 7, and the critical oil supply pressure is the oil supply pressure of the main oil circuit 7 when the valve unit 4 is switched between the first position and the second position.

[0086] refer to Figures 6 to 8 Valve unit 4 in Figure 6 In the first position shown, the bearing 5 is supplied with initial oil pressure P1 from the main oil circuit 7. As the low-pressure rotor speed increases, the oil supply pressure of the main oil circuit 7 rises from the initial oil supply pressure P1 to the critical oil supply pressure P2. The valve unit 4 moves a stroke L within the oil supply pipe 1, and the spring compression is the same as the stroke L. At this time, the first oil circuit is still in the oil supply state, and the second sealing section 46 just closes the second oil supply outlet 12. When the oil supply pressure of the main oil circuit 7 rises above the critical oil supply pressure P2, the valve unit 4 moves to the second position, the first oil circuit is closed, and lubricating oil is supplied to the bearing 5 through the second oil circuit for ring lubrication. When the oil supply pressure of the main oil circuit 7 drops from above the critical oil supply pressure P2 to below it, the second oil circuit is closed, and lubricating oil is supplied to the bearing 5 again through the first oil circuit for jet lubrication.

[0087] When subjected to the maximum oil supply pressure P3 of the total oil circuit 7, such as Figure 8 As shown, valve unit 4 moves a maximum stroke L1 within oil supply pipe 1. The compression of the spring is the same as the maximum stroke L1. This maximum stroke L1 must be less than (spring compression limit - spring initial compression) to avoid spring crushing failure.

[0088] The aforementioned bearing lubrication assembly, based on the under-ring oil supply circuit, integrates a direct-injection lubricating oil outlet and a valve-like element that moves with changes in lubricating oil pressure. This allows the engine bearing 5 to use under-ring oil supply at high speeds and direct injection oil supply at low speeds, achieving an adaptive optimal oil supply effect and ensuring the lubrication efficiency of bearing 5 under different speed conditions. Furthermore, this configuration does not require extensive modifications to the original under-ring oil supply circuit, resulting in lower costs. It utilizes a simple elastic element, leveraging the inherent characteristics of the aircraft engine's lubricating oil pump to control the oil circuit switching, eliminating the need for additional control mechanisms, thus ensuring high structural reliability and stability.

[0089] While the present invention has been disclosed above with reference to preferred embodiments, it is not intended to limit the invention. Any variations and modifications can be made by those skilled in the art without departing from the spirit and scope of the invention. Therefore, any modifications, equivalent changes, and alterations made to the above embodiments based on the technical essence of the present invention, without departing from the scope of the invention, fall within the protection scope defined by the claims of the present invention.

Claims

1. A bearing lubrication assembly for lubricating a bearing within an aeroengine, characterised in that, include: The fuel supply pipe is connected to the main fuel line in the aircraft engine, and the fuel supply pipe has a first fuel supply outlet and a second fuel supply outlet. as well as The valve unit is supported by an elastic unit in the oil supply pipe and is movable in the oil supply pipe; The valve unit moves between a first position and a second position under the combined action of the elastic support force of the elastic unit and the lubricating oil pressure in the main oil circuit. In the first position, the valve unit opens the first oil supply outlet and closes the second oil supply outlet, and in the second position, it closes the first oil supply outlet and opens the second oil supply outlet. When lubricating oil is sprayed out from the first oil supply port, it provides jet lubrication to the bearing to be lubricated; when lubricating oil is sprayed out from the second oil supply port, it provides under-ring lubrication to the bearing to be lubricated.

2. The bearing lubrication assembly of claim 1, wherein, The bearing to be lubricated includes an inner ring, an outer ring, and a cage. The inner ring is mounted on an input shaft. The end of the input shaft opposite to the bearing to be lubricated has an annular groove. The bearing lubrication assembly also includes a spray hole formed in the annular groove. The first oil supply outlet is positioned relative to the position between the bearing inner ring and the cage, and the second oil supply outlet is positioned relative to the nozzle.

3. The bearing lubrication assembly of claim 2, wherein, The nozzle is an oblique hole.

4. The bearing lubrication assembly of claim 1, wherein, The oil supply pipe includes a first section and a second section, wherein the inner diameter of the first section is smaller than the inner diameter of the second section, so as to form a stop between the first section and the second section; The stop portion restricts the travel of the valve unit within the oil supply pipe. When the valve unit abuts against the stop portion, the valve unit is in the first position.

5. The bearing lubrication assembly of claim 4, wherein, The elastic element is a spring.

6. The bearing lubrication assembly of claim 5, wherein, The following relationship exists between the stiffness of the spring, the stroke of the valve unit within the oil supply pipe, and the oil supply pressure of the main oil circuit: K = (P2 - P1) × A / L; Wherein, K is the stiffness of the spring, L is the stroke of the valve unit in the oil supply pipe, A is the force-bearing area of ​​the valve unit along the direction of the oil supply pipe, P1 is the initial oil supply pressure of the main oil circuit, P2 is the critical oil supply pressure of the main oil circuit, and the critical oil supply pressure is the oil supply pressure of the main oil circuit when the valve unit is switched between the first position and the second position.

7. The bearing lubrication assembly of claim 1, wherein, The valve unit includes: First sealing section; The second sealing section; and An annular groove is provided between the first sealing section and the second sealing section; The first sealing section and the second sealing section have outer diameters corresponding to the inner wall of the oil supply pipe, forming a chamber defined by the first sealing section, the second sealing section, the annular groove, and the inner wall. When the valve unit is in the first position, the chamber is connected to the first oil supply outlet; when the valve unit is in the second position, the chamber is connected to the second oil supply outlet.

8. The bearing lubrication assembly of claim 7, wherein, The annular groove is provided with multiple oil outlet holes evenly distributed along the axial and circumferential directions of the valve unit.

9. An aeroengine characterised in that, It includes a bearing to be lubricated and a bearing lubrication assembly as described in any one of claims 1-8, through which the bearing is lubricated.

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