Axial ring lower lubricating structure and aero-engine with same

Abstract

The invention discloses an axial ring lower lubricating structure and an aero-engine with the axial ring lower lubricating structure. The axial ring lower lubricating structure comprises a switching oil distribution device, a connecting bearing arranged on the outer circle of the switching oil distribution device and a plurality of oil supply nozzles. The first end of the switching oil distribution device is provided with an oil distribution cavity, the spline section behind the first end of the switching oil distribution device is provided with an inner spline, and an inclined oil conveying channel set and an axial oil conveying channel set are further arranged in the spline section. The oil supply nozzles are used for spraying lubricating oil into the oil distribution cavities, and the oil distribution cavities are used for distributing the lubricating oil so that the lubricating oil can correspondingly enter the oblique oil conveying channel set and the axial oil conveying channel set under the rotating centrifugal effect, and the lubricating oil in the oblique oil conveying channel set can continue to enter the connecting bearing for lubrication under the rotating centrifugal effect. And lubricating oil in the axial oil conveying channel group continues to enter the inner spline for lubrication under the rotating centrifugal effect. According to the structure, the whole lubricating oil system is compact in flow path structure, high in reliability, high in lubricating efficiency and high in function integration degree, and the lubricating and cooling problems of high-DN-value bearings and splines of aero-engines are effectively solved.

Description

Technical Field

[0001] The present invention relates to the technical field of aero-engine lubricating oil systems, and in particular, to an axial under-ring lubrication structure. In addition, the present invention also relates to an aero-engine including the above axial under-ring lubrication structure. Background Art

[0002] As a high-speed rotating thermal machine, the rolling bearings and splines inside an aero-engine play a crucial role in the normal and stable operation of the engine. The bearings transmit the loads of rotating components and provide good positioning accuracy and sufficient supporting rigidity; the splines connect random accessories of the engine such as generators, lubricating oil pumps, fuel pumps, and blowers to the transmission gearbox to achieve torque transmission. Both the bearings and the splines will generate heat due to relative friction and wear between components caused by high-speed rotation. Therefore, it is necessary to provide an appropriate amount of clean lubricating oil to timely remove this heat. Otherwise, problems such as reduced operating performance of components, shortened service life, and inability to guarantee reliability will occur.

[0003] At present, under-ring lubrication has gradually replaced traditional injection lubrication and developed into the main lubrication and cooling method for engine bearings. Although its structure is relatively complex, the lubrication effect is better, meeting the lubrication and cooling requirements of bearings with high DN (bearing inner diameter (mm) × rotational speed (r / min)) values. The lubricating oil passes through four stages of oil injection, oil collection, oil transmission, and oil slinging from the oil supply nozzle to the bearing, and is divided into two categories: radial under-ring lubrication and axial under-ring lubrication according to different oil collection forms. Usually, the oil collection efficiency of axial under-ring lubrication is over 90%, and its performance is superior to that of radial under-ring lubrication, having a broad application scenario.

[0004] The lubrication and cooling methods for splines generally include two categories: grease lubrication and oil injection lubrication. The former fills grease at the spline meshing position to form an oil film to reduce friction. This method is limited by the working space and weight and cannot be filled in large quantities, and is not suitable for working environments with high temperature, high rotational speed, and high load. The latter needs to set nozzles at the spline meshing position and is accompanied by oil supply and return channels, relying on a complete oil supply and return circulation pipeline to achieve the lubrication and cooling of the splines. This method makes the flow path layout of the engine lubricating oil system more complex and increases the load and weight of the lubricating oil pump. Summary of the Invention

[0005] The present invention provides an axial under-ring lubrication structure and an aero-engine having the same to solve the technical problems existing in the existing lubrication methods, which make the flow path layout of the engine lubricating oil system more complex and increase the load and weight of the lubricating oil pump.

[0006] The technical solution adopted by the present invention is as follows: An axial under-ring lubrication structure, comprising: a transfer oil distribution device for sleeving on the outer circle of a central shaft, a connecting bearing installed on the outer circle of the transfer oil distribution device, and a plurality of oil supply nozzles for jetting lubricating oil; the first end of the transfer oil distribution device has an oil distribution cavity that extends inwards from the end face and is annular, and an internal spline is provided on the inner circumferential surface where the spline section after the first end of the transfer oil distribution device contacts the central shaft. An inclined oil delivery channel group for communicating the oil distribution cavity and the connecting bearing, and an axial oil delivery channel group for communicating the oil distribution cavity and the internal spline are also provided in the transfer oil distribution device; the plurality of oil supply nozzles are located at the first end of the transfer oil distribution device and are spaced apart from the transfer oil distribution device. The plurality of oil supply nozzles are used to jet lubricating oil into the oil distribution cavity respectively. The oil distribution cavity is used to distribute the lubricating oil so that the lubricating oil enters the inclined oil delivery channel group and the axial oil delivery channel group respectively under the rotational centrifugal force of the transfer oil distribution device, and then the lubricating oil in the inclined oil delivery channel group continues to enter the connecting bearing for lubrication under the rotational centrifugal force, and the lubricating oil in the axial oil delivery channel group continues to enter the internal spline for lubrication under the rotational centrifugal force.

[0007] Further, the transfer oil distribution device includes a lining sleeve transfer shaft for installing on the outer circle of the central shaft, and an annular oil distribution ring for distributing lubricating oil; the end face of the first end of the lining sleeve transfer shaft extends inwards to form a circumferentially annular cavity, an internal spline is provided on the inner circumferential surface of the spline section of the lining sleeve transfer shaft, the connecting bearing is installed on the outer circle of the lining sleeve transfer shaft, and the inclined oil delivery channel group and the axial oil delivery channel group are respectively arranged in the lining sleeve transfer shaft; the oil distribution ring is fixedly installed in the cavity, and an oil distribution cavity is formed by enclosing the inner ring surface of the oil distribution ring, the inner ring surface of the cavity, and the bottom of the cavity.

[0008] Further, a plurality of oil retaining dams protruding towards the center are provided on the inner ring surface of the oil distribution ring. The plurality of oil retaining dams are arranged at intervals in the circumferential direction in sequence, and each oil retaining dam extends axially to divide the oil distribution cavity into a plurality of oil distribution areas arranged in sequence in the circumferential direction; the axial oil delivery channel group includes a plurality of spline lubrication oil collecting ports opened on the bottom of the cavity, and the plurality of spline lubrication oil collecting ports are respectively arranged in the plurality of oil distribution areas; the inclined oil delivery channel group includes a plurality of bearing lubrication oil collecting ports opened on the bottom of the cavity, and the plurality of bearing lubrication oil collecting ports are respectively arranged in the remaining plurality of oil distribution areas.

[0009] Further, the number of the oil retaining dams is even, and they are symmetrically arranged in pairs about the center of the oil distribution ring, so that the plurality of oil distribution areas are symmetrically arranged in pairs about the center of the oil distribution ring; the two symmetrically arranged oil distribution areas commonly correspond to a bearing lubrication oil collecting port or a spline lubrication oil collecting port, and each oil distribution area has at least one bearing lubrication oil collecting port or at least one spline lubrication oil collecting port, so as to correspondingly adjust the oil flow rate in the area by adjusting the circumferential area size of the oil distribution area.

[0010] Further, the inner bushing adapter shaft includes an adapter shaft body for being mounted on the outer circumference of the central shaft, and an inner convex cylinder and an outer convex cylinder that are coaxially arranged inside and outside and spaced apart from each other and are connected to the end face of the first end of the adapter shaft body. An annular cavity is formed in the annular region between the inner convex cylinder and the outer convex cylinder; a plurality of outwardly protruding limiting clamping plates are spaced apart on the outer circumferential surface of the oil distributing ring, and a plurality of limiting grooves that are recessed from the end face are spaced apart in the circumferential direction of the outer convex cylinder. The oil distributing ring is press-fitted into the outer convex cylinder, and the limiting clamping plates thereon are respectively clamped in the corresponding limiting grooves to position the oil distributing ring in the circumferential direction.

[0011] Further, a plurality of oil supply nozzles are sequentially spaced apart in the circumferential direction, and the injection ends of the oil supply nozzles face the first end of the inner bushing adapter shaft, and the injection ends of the oil supply nozzles extend obliquely downward at an inclination angle of 10° to 20° from the horizontal direction to spray the lubricating oil into the oil distribution cavity.

[0012] Further, the connecting bearing includes an inner bearing ring sleeved on the outer circumference of the inner bushing adapter shaft, an outer bearing ring spaced outside the inner bearing ring, a cage connected between the outer bearing ring and the inner bearing ring, and a plurality of spheres sequentially arranged on the cage; the axial under-ring lubrication structure further includes a lock nut and a lock washer sequentially mounted on the outer circumference of the inner bushing adapter shaft. A positioning shoulder is formed by outward protrusion on the outer circumferential surface of the inner bushing adapter shaft; both ends of the inner bearing ring respectively abut against the positioning shoulder and the lock washer for axial limit, and the lock nut is threadedly connected to the outer circumferential surface of the inner bushing adapter shaft to axially tighten the lock washer.

[0013] Further, the inner bearing ring includes a first half inner bearing ring and a second half inner bearing ring sequentially arranged along the axial direction. A plurality of oil throwing holes that are sequentially spaced apart in the circumferential direction and penetrate through are provided at the contact position of the first half inner bearing ring and the second half inner bearing ring; the inner bearing ring has a clearance fit with the outer circumferential surface of the inner bushing adapter shaft to form an oil transmission groove communicating with the plurality of oil throwing holes between the two. An annular oil collecting groove communicating with the oil transmission groove is also machined between the first half inner bearing ring and the lock washer; a plurality of oil transmission channels are also provided in the inner bushing adapter shaft and are sequentially spaced apart in the circumferential direction. Each oil transmission channel extends obliquely along the axial direction to communicate with the corresponding bearing lubrication oil collecting port and the oil collecting groove, and a plurality of bearing lubrication oil collecting ports, a plurality of oblique oil transmission channels, the oil collecting groove, the oil transmission groove and a plurality of oil throwing holes are sequentially communicated to form an oblique oil transmission channel group.

[0014] Further, a plurality of axial oil transmission channel groups are also provided in the inner bushing adapter shaft and are sequentially spaced apart in the circumferential direction. Each axial oil transmission channel group extends along the axial direction to communicate with the corresponding spline lubrication oil collecting port and the internal spline, and a plurality of spline lubrication oil collecting ports and a plurality of axial oil transmission channels are sequentially communicated to form an axial oil transmission channel group; an oil outlet penetrating through the wall surface is also provided on the wall surface of the spline section of the inner bushing adapter shaft.

[0015] According to another aspect of the present invention, an aeroengine is also provided, which has the axial under-ring lubrication structure as described in any one of the above.

[0016] The present invention has the following beneficial effects: Compared with the prior art in which the bearing and the spline are lubricated separately, resulting in a complex layout of the flow path structure of the entire lubricating oil system, increased load and weight of the lubricating oil pump, in the axial under-ring lubrication structure of the present invention, the lubricating oil for the bearing and the spline can be respectively achieved through the oil supply nozzle, so that the flow path structure of the entire lubricating oil system is compact, highly reliable, has high lubrication efficiency and high function integration degree, effectively solves the lubrication and cooling problems of the high-DN value bearing and spline of the aero-engine, reduces the load and weight of the lubricating oil pump, and compared with the traditional injection lubrication and grease lubrication, the structure of the present invention can make the spline lubrication more sufficient, while reducing the complexity of the lubrication system, effectively avoiding the wear problems caused by insufficient lubrication of the bearing and the spline, and thus improving the component life and working reliability; on the other hand, through the setting of the oil distribution cavity, not only the purpose of lubricating the bearing and the spline simultaneously is achieved, but also the required lubricating oil amount for the lubricated parts is distributed as needed, thereby improving the lubricating oil utilization efficiency and lubrication effect, and making the bearing and the spline lubricated sufficiently respectively.

[0017] In addition to the purposes, features and advantages described above, the present invention has other purposes, features and advantages. The following will refer to the drawings to further elaborate on the present invention in detail. Description of the Drawings

[0018] The drawings forming a part of this application are used to provide a further understanding of the present invention. The schematic embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation to the present invention. In the drawings: Figure 1 is the three-dimensional structure schematic diagram of the axial under-ring lubrication structure in the preferred embodiment of the present invention; Figure 2 is the front view structure schematic diagram of the axial under-ring lubrication structure in the preferred embodiment of the present invention; Figure 3 is Figure 2 the sectional view structure schematic diagram of A-A in Figure 4 is the side view structure schematic diagram of the axial under-ring lubrication device in the preferred embodiment of the present invention; Figure 5 is Figure 4 the sectional view structure schematic diagram of B-B in Figure 6 is Figure 4 the sectional view structure schematic diagram of C-C in Figure 7 is Figure 5 the sectional view structure schematic diagram of D-D in Figure 8 is Figure 5 the sectional view structure schematic diagram of E-E in

[0019] Legend Explanation: 1. Fuel supply nozzle; 2. Oil separation ring; 3. Limit clamping plate; 4. Oil retaining dam; 5. Inner lining sleeve transfer shaft; 6. Oil separation chamber; 7. Oil collection port; 7a. Spline lubrication oil collection port; 7b. Bearing lubrication oil collection port; 8. Outer convex cylinder; 9. Limit groove; 10. Locking nut; 11. Locking washer; 12. Oblique oil delivery channel; 13. Axial oil delivery channel; 14. First half inner ring of bearing; 15. Oil collection tank; 16. Oil delivery tank; 17. Oil slinging hole; 18. Second half inner ring of bearing; 19. Sphere; 20. Cage; 21. Bearing outer ring; 22. Stop groove; 23. Positioning shoulder; 24. Spline section; 25. Internal spline; 26. Oil outlet. Specific Embodiment

[0020] The embodiments of the present invention will be described in detail below with reference to the accompanying drawings. However, the present invention can be implemented in many different ways defined and covered by the following.

[0021] Refer to Figure 1 , Figure 2 and Figure 4 , a preferred embodiment of the present invention provides an axial under-ring lubrication structure, including: a transfer oil separation device for sleeving on the outer circle of the central shaft, a connecting bearing installed on the outer circle of the transfer oil separation device, and a plurality of fuel supply nozzles 1 for spraying lubricating oil. The first end of the transfer oil separation device has an annular oil separation chamber 6 extending inwards from the end face, and an internal spline 25 is provided on the inner peripheral surface where the spline section 24 after the first end of the transfer oil separation device contacts the central shaft. The transfer oil separation device also has an oblique oil delivery channel group communicating the oil separation chamber 6 and the connecting bearing, and an axial oil delivery channel group communicating the oil separation chamber 6 and the internal spline 25. The plurality of fuel supply nozzles 1 are located at the first end of the transfer oil separation device and are spaced from the transfer oil separation device. The plurality of fuel supply nozzles 1 are used to spray lubricating oil into the oil separation chamber 6 respectively. The oil separation chamber 6 is used to distribute the lubricating oil so that the lubricating oil enters the oblique oil delivery channel group and the axial oil delivery channel group respectively under the rotational centrifugal action of the transfer oil separation device, and then the lubricating oil in the oblique oil delivery channel group continues to enter the connecting bearing for lubrication under the rotational centrifugal action, and the lubricating oil in the axial oil delivery channel group continues to enter the internal spline 25 for lubrication under the rotational centrifugal action.

[0022] For the axial under-ring lubrication structure of the present invention, when the engine is running, the lubricating oil in the lubricating oil tank enters the oil delivery pipeline of the oil supply circuit through the lubricating oil pump, and is respectively sprayed into the oil distribution cavity 6 by a plurality of oil supply nozzles 1 installed inside the engine bearing cavity. The lubricating oil is broken and splashed under the action of the rotating centrifugal force driven by the central shaft to drive the transfer oil distribution device, and enters the inclined oil delivery channel group and the axial oil delivery channel group respectively under the diversion action of the oil distribution cavity 6. The lubricating oil entering the inclined oil delivery channel group continues to enter the connecting bearing under the action of the rotating centrifugal force to lubricate the connecting bearing with the lubricating oil, while the lubricating oil entering the axial oil delivery channel group also continues to enter the internal spline 25 under the action of the rotating centrifugal force to lubricate the internal spline 25 with the lubricating oil, thereby realizing the lubrication of the bearing and the spline with the lubricating oil.

[0023] Compared with the prior art in which the bearing and the spline are lubricated separately, resulting in a complex layout of the flow path structure of the entire lubricating oil system, increased load and weight of the lubricating oil pump, in the axial under-ring lubrication structure of the present invention, the lubrication of the bearing and the spline can be respectively realized through the oil supply nozzle 1, so that the flow path structure of the entire lubricating oil system is compact, highly reliable, has high lubrication efficiency and high function integration degree, effectively solves the lubrication and cooling problems of high-DN value bearings and splines in aeroengines, reduces the load and weight of the lubricating oil pump, and compared with the traditional injection lubrication and grease lubrication, the structure of the present invention can make the spline lubrication more sufficient, while reducing the complexity of the lubrication system, effectively avoiding the wear problems of the bearing and the spline caused by insufficient lubrication, and further improving the component life and working reliability; on the other hand, through the setting of the oil distribution cavity 6, not only the purpose of lubricating the bearing and the spline simultaneously is realized, but also the required lubricating oil amount of the lubricated parts is distributed as needed, thereby improving the utilization efficiency and lubrication effect of the lubricating oil, and making the lubrication of the bearing and the spline sufficient respectively.

[0024] Optionally, as Figure 1 and Figure 3 shown, the transfer oil distribution device includes a lining sleeve transfer shaft 5 for being installed on the outer circle of the central shaft, and an annular oil distribution ring 2 for distributing the lubricating oil. The end face of the first end of the lining sleeve transfer shaft 5 is recessed and extended to form a circumferential annular cavity. An internal spline 25 is provided on the inner circumferential surface of the spline section 24 of the lining sleeve transfer shaft 5. The connecting bearing is installed on the outer circle of the lining sleeve transfer shaft 5. The inclined oil delivery channel group and the axial oil delivery channel group are respectively arranged inside the lining sleeve transfer shaft 5. The oil distribution ring 2 is fixedly installed in the cavity, and an oil distribution cavity 6 is formed by enclosing the inner ring surface of the oil distribution ring 2, the inner ring surface of the cavity and the bottom of the cavity. In this optional solution, the transfer oil distribution device only includes the lining sleeve transfer shaft 5 that plays an installation and support role, and the oil distribution ring 2 for oil distribution, and its overall structure is simple and easy to process and prepare.

[0025] In this optional solution, as Figure 3 and Figure 5As shown, a plurality of oil retaining dams 4 protruding towards the center are provided on the inner ring surface of the oil separating ring 2. The plurality of oil retaining dams 4 are arranged at intervals in the circumferential direction in sequence, and each oil retaining dam 4 extends axially to divide the oil separating chamber 6 into a plurality of oil separating zones arranged in sequence in the circumferential direction. The axial oil supply channel group includes a plurality of spline lubrication oil collecting ports 7a opened on the bottom of the annular chamber. The plurality of spline lubrication oil collecting ports 7a are respectively arranged in a plurality of oil separating zones. The inclined oil supply channel group includes a plurality of bearing lubrication oil collecting ports 7b opened on the bottom of the annular chamber. The plurality of bearing lubrication oil collecting ports 7b are respectively arranged in the remaining plurality of oil separating zones. In this alternative solution, through the arrangement of the plurality of oil retaining dams 4 on the inner ring surface of the oil separating ring 2, the oil separating chamber 6 can be divided into a plurality of oil separating zones arranged in sequence in the circumferential direction, and only the spline lubrication oil collecting port 7a or the bearing lubrication oil collecting port 7b is arranged in each oil separating zone, so as to realize the diversion of the lubricating oil.

[0026] Preferably, as Figure 5 shown, the number of the oil retaining dams 4 is an even number, and they are symmetrically arranged in pairs about the center of the oil separating ring 2, so that the plurality of oil separating zones are symmetrically arranged in pairs about the center of the oil separating ring 2. The two symmetrically arranged oil separating zones commonly correspond to the bearing lubrication oil collecting port 7b or the spline lubrication oil collecting port 7a, and at least one bearing lubrication oil collecting port 7b or at least one spline lubrication oil collecting port 7a is provided in each oil separating zone, so as to correspondingly adjust the lubricating oil flow rate in the area by adjusting the circumferential area size of the oil separating zone. In this preferred solution, through the arrangement mode of the oil retaining dams 4, the plurality of oil separating zones are symmetrically arranged in pairs about the center of the oil separating ring 2, and the two symmetrically arranged oil separating zones commonly correspond to the bearing lubrication oil collecting port 7b or the spline lubrication oil collecting port 7a, so that the lubricating oil flowing to the bearing or the spline can be circumferentially uniform, thereby improving the lubrication effect of the bearing and the spline; on the other hand, in the preferred embodiment of the present invention, the oil retaining dams 4 on the oil separating ring 2 divide the oil separating chamber 6 into multiple pairs of centrally symmetric regions, and the oil collecting ports in each region lead to the bearing or the spline uniformly. By adjusting the circumferential area of the oil separating zone, the flow rate ratio of the lubricating oil flowing to the bearing and the spline can be correspondingly controlled, which not only realizes the simultaneous lubrication of the bearing and the spline, but also distributes the required lubricating oil amount of the lubricated parts as needed, thereby improving the utilization efficiency and lubrication effect of the lubricating oil.

[0027] In a specific embodiment of this preferred solution, as Figure 5As shown in the figure, four oil retaining dams 4 are arranged inside the oil separating ring 2 and are integrally formed with the oil separating ring 2. The inner lining sleeve transfer shaft 5 is provided with eight oil collecting ports 7 that are circumferentially discrete in the oil separating cavity 6. The oil collecting ports 7 are symmetrically distributed about the center. The four oil retaining dams 4 inside the oil separating ring 2 divide the area where the oil collecting ports 7 are located into four parts. Each of the two centrally symmetric regions has one oil collecting port 7, namely the spline lubrication oil collecting port 7a; each of the remaining two centrally symmetric regions has three oil collecting ports 7, namely the bearing lubrication oil collecting port 7b. The included angles between the four oil retaining dams 4 are α = 28° and β = 152° respectively. In this preferred solution, by adjusting the circumferential angle ratio (α:β) between the four oil retaining dams 4 inside the oil separating ring 2, the flow ratio of the lubricating oil flowing to the bearing and the spline is controlled, not only realizing the simultaneous lubrication of the bearing and the spline, but also achieving the on-demand distribution of the required lubricating oil amount at the lubricated parts.

[0028] In this alternative solution, as Figure 3 shown, the inner lining sleeve transfer shaft 5 includes a transfer shaft body for being installed on the outer circle of the central shaft, and an inner convex cylinder and an outer convex cylinder 8 that are coaxially arranged inside and outside and are spaced apart and connected to the end face of the first end of the transfer shaft body. The annular region between the inner convex cylinder and the outer convex cylinder 8 forms an annular cavity. As Figure 1 shown, a plurality of outwardly protruding limit clamping plates 3 are arranged at intervals on the outer ring surface of the oil separating ring 2. A plurality of limit grooves 9 that are recessed from the end face are arranged at intervals in the circumferential direction of the outer convex cylinder 8. The oil separating ring 2 is press-fitted into the outer convex cylinder 8, and the limit clamping plates 3 thereon are respectively clamped in the corresponding limit grooves 9 to circumferentially position the oil separating ring 2.

[0029] Optionally, as Figure 2 and Figure 3 shown, a plurality of oil supply nozzles 1 are arranged at intervals in sequence along the circumference, and the injection ends of the oil supply nozzles 1 face the first end of the inner lining sleeve transfer shaft 5, and the injection ends of the oil supply nozzles 1 extend obliquely downward by an inclination angle of 10° to 20° from the horizontal to inject the lubricating oil into the oil separating cavity 6. In this alternative solution, the number of the oil supply nozzles 1 is two. The nozzle diameters of the two oil supply nozzles 1 are 1 mm and the injection ends are inclined towards the axis. The inclination angle is 15°, so that the ejected lubricating oil hits the wall surface of the inner lining sleeve transfer shaft 5 in the oil separating cavity 6. The circumferential angle between the two oil supply nozzles 1 is 120°.

[0030] Optionally, as Figure 3As shown in the figure, the connecting bearing includes an inner bearing ring sleeved on the outer circumference of the inner liner transfer shaft 5, an outer bearing ring 21 spaced outside the inner bearing ring, a cage 20 connected between the outer bearing ring 21 and the inner bearing ring, and a number of spheres 19 sequentially arranged on the cage 20. The axial ring lower lubrication structure further includes a lock nut 10 and a lock washer 11 sequentially installed on the outer circumference of the inner liner transfer shaft 5, and a positioning shoulder 23 is formed by the outward protrusion of the outer circumferential surface of the inner liner transfer shaft 5. The two ends of the inner bearing ring respectively abut against the positioning shoulder 23 and the lock washer 11 for axial limitation, and the lock nut 10 is threadedly connected to the outer circumferential surface of the inner liner transfer shaft 5 to axially tighten the lock washer 11. In this alternative solution, the lock washer 11 has four protruding gaskets in the circumferential direction, and the lock nut 10 presses the gaskets to fix the lock washer 11; two symmetrically arranged stop grooves 22 are provided on the side wall of the outer bearing ring 21 for cooperating with the clamping components on the casing to realize the installation and fixation of the outer bearing ring 21.

[0031] Furthermore, as shown in Figure 5 , Figure 6 and Figure 8 the figure, the inner bearing ring includes a first half inner bearing ring 14 and a second half inner bearing ring 18 sequentially arranged along the axial direction. A plurality of oil slinging holes 17 are provided at the contact portion of the first half inner bearing ring 14 and the second half inner bearing ring 18, which are sequentially arranged at intervals along the circumferential direction and penetrate through. The inner bearing ring is in clearance fit with the outer circumferential surface of the inner liner transfer shaft 5 to form an oil delivery groove 16 communicating with a plurality of oil slinging holes 17 therebetween. An annular oil collecting groove 15 communicating with the oil delivery groove 16 is also machined between the first half inner bearing ring 14 and the lock washer 11. A plurality of oil delivery channels are also provided in the inner liner transfer shaft 5, which are sequentially arranged at intervals along the circumferential direction. Each oil delivery channel extends obliquely along the axial direction to communicate with the corresponding bearing lubrication oil collecting port 7b and the oil collecting groove 15, and a plurality of bearing lubrication oil collecting ports 7b, a plurality of oblique oil delivery channels 12, the oil collecting groove 15, the oil delivery groove 16 and a plurality of oil slinging holes 17 are sequentially communicated to form an oblique oil delivery channel group. In this alternative solution, six axially symmetric oblique oil delivery channels 12 are provided on the inner liner transfer shaft 5. The diameter of the oblique oil delivery channel 12 is 1.5 mm, and the inclination angle towards the axis is 39°.

[0032] Furthermore, as shown in Figure 1 , Figure 5 and Figure 7As shown, the inner sleeve adapter shaft 5 is also provided with a plurality of axially spaced oil supply channel groups arranged circumferentially. Each axially oil supply channel group extends axially to communicate with the corresponding spline lubrication oil collection port 7a and the internal spline 25, and a plurality of spline lubrication oil collection ports 7a and a plurality of axially oil supply channels 13 are sequentially connected to form an axially oil supply channel group. An oil outlet 26 penetrating the wall surface is also provided on the wall surface of the spline section 24 of the inner sleeve adapter shaft 5. In this alternative solution, the inner sleeve adapter shaft 5, the outer convex cylinder 8, the positioning shoulder 23, the internal spline 25 and the oil outlet 26 are integrally manufactured; two axially symmetrically arranged axially oil supply channels 13 are provided on the inner sleeve adapter shaft 5, and the axially oil supply channel 13 is composed of pipes with diameters of 1.5 mm and 3 mm, connecting the spline lubrication oil collection port 7a with the spline section 24.

[0033] The working principle of the axial sub-ring lubrication structure for bearings and splines of the present invention is as follows: When the engine is running, the lubricating oil in the lubricating oil tank enters the oil supply pipeline of the oil supply circuit through the lubricating oil pump, and is simultaneously sprayed onto the wall surface of the inner sleeve adapter shaft 5 in the oil distribution cavity 6 through the spray holes of the two oil supply nozzles 1 installed inside the engine bearing cavity. Under the action of the rotation and centrifugation of the central shaft, it breaks and splashes. The lubricating oil contacts the oil retaining dam 4 inside the oil distribution ring 2. After being diverted by the oil retaining dam 4, it enters the eight oil collection ports 7 provided on the inner sleeve adapter shaft 5. Since the radial height of the bearing lubrication oil collection port 7b is less than the radial height of the oil collection groove 15, the centrifugal potential energy at the bearing lubrication oil collection port 7b is lower than the centrifugal potential energy at the oil collection groove 15. The lubricating oil preferentially flows from the six bearing lubrication oil collection ports 7b into the inclined oil supply channels 12 leading to the oil collection groove 15; after a certain amount of lubricating oil is stored in the oil collection groove 15, it flows along the oil supply groove 16 between the inner sleeve adapter shaft 5 and the first half inner ring 14 and the second half inner ring 18 of the bearing, and flows to the sphere 19 through the eight oil throwing holes 17 between the first half inner ring 14 and the second half inner ring 18 of the bearing, and is thrown out from the bearing raceway surface after lubrication and cooling; after a certain amount of lubricating oil exists in the oil distribution cavity 6, the lubricating oil then flows from the two spline lubrication oil collection ports 7a into the axially oil supply channel 13, and is thrown into the internal spline 25 located in the spline section 24 under the rotation of the inner sleeve adapter shaft 5, and is discharged from the oil outlet 26 after lubrication and cooling, so as to achieve the effect of simultaneously supplying lubricating oil to the bearing and the spline, and improving the lubrication efficiency.

[0034] In the present invention, by adopting the above-mentioned axial sub-ring lubrication structure to lubricate and cool the bearings and splines in the aeroengine, while simplifying the internal structure and reducing the complexity of the lubricating oil system, the spline lubrication is more sufficient, effectively avoiding the wear problems caused by insufficient lubrication of the bearings and splines, improving the service life of the components and the reliability of the lubricating device, with a high degree of functional integration, and being suitable for wide promotion and application.

[0035] A preferred embodiment of the present invention further relates to an aero-engine, characterized in that it has an axial sub-annular lubrication structure as described in any one of the above. Thus, the aero-engine of the present invention simplifies the internal structure, reduces the complexity of the lubricating oil system, while making the spline lubrication more sufficient, effectively avoiding the wear problems of bearings and splines caused by insufficient lubrication, improving the service life of components and the reliability of the lubricating device, with high functional integration, and is suitable for wide promotion and application.

[0036] The above are only preferred embodiments of the present invention and are not intended to limit the present invention. For those skilled in the art, the present invention can have various changes and modifications. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included within the protection scope of the present invention.

Claims

1. An axial under-ring lubrication structure, characterized in that, Including: A transfer oil distribution device for sleeving on the outer circle of a central shaft, a connecting bearing installed on the outer circle of the transfer oil distribution device, and a plurality of oil supply nozzles (1) for injecting lubricating oil; The first end of the transfer oil distribution device has an oil distribution cavity (6) that extends inwards from the end face and is annular. An internal spline (25) is provided on the inner peripheral surface where the spline section (24) after the first end of the transfer oil distribution device contacts the central shaft. An inclined oil delivery channel group communicating the oil distribution cavity (6) and the connecting bearing, and an axial oil delivery channel group communicating the oil distribution cavity (6) and the internal spline (25) are also provided in the transfer oil distribution device; The plurality of oil supply nozzles (1) are located at the first end of the transfer oil distribution device and are spaced from the transfer oil distribution device. The plurality of oil supply nozzles (1) are used to inject lubricating oil into the oil distribution cavity (6) respectively. The oil distribution cavity (6) is used to distribute the lubricating oil so that the lubricating oil enters the inclined oil delivery channel group and the axial oil delivery channel group respectively under the rotational centrifugal action of the transfer oil distribution device. Furthermore, the lubricating oil in the inclined oil delivery channel group continues to enter the connecting bearing for lubrication under the rotational centrifugal action, and the lubricating oil in the axial oil delivery channel group continues to enter the internal spline (25) for lubrication under the rotational centrifugal action.

2. The axial under-ring lubrication structure according to claim 1, wherein The transfer oil distribution device includes a lining sleeve transfer shaft (5) for sleeving on the outer circle of the central shaft, and an annular oil distribution ring (2) for distributing lubricating oil; the end face of the first end of the lining sleeve transfer shaft (5) extends inwards to form a circumferentially annular cavity. An internal spline (25) is provided on the inner peripheral surface of the spline section (24) of the lining sleeve transfer shaft (5). The connecting bearing is installed on the outer circle of the lining sleeve transfer shaft (5). The inclined oil delivery channel group and the axial oil delivery channel group are respectively arranged in the lining sleeve transfer shaft (5); the oil distribution ring (2) is fixedly installed in the cavity, and an oil distribution cavity (6) is formed by enclosing the inner ring surface of the oil distribution ring (2), the inner ring surface of the cavity, and the bottom of the cavity.

3. The axial under-ring lubrication structure according to claim 2, characterized in that, A plurality of oil retaining dams (4) protruding towards the center are provided on the inner ring surface of the oil distribution ring (2). The plurality of oil retaining dams (4) are sequentially spaced along the circumference, and each oil retaining dam (4) extends axially to divide the oil distribution cavity (6) into a plurality of oil distribution areas arranged sequentially along the circumference; the axial oil delivery channel group includes a plurality of spline lubrication oil collection ports (7a) opened on the bottom of the cavity, and the plurality of spline lubrication oil collection ports (7a) are respectively arranged in the plurality of oil distribution areas; the inclined oil delivery channel group includes a plurality of bearing lubrication oil collection ports (7b) opened on the bottom of the cavity, and the plurality of bearing lubrication oil collection ports (7b) are respectively arranged in the remaining plurality of oil distribution areas.

4. The axial sub-ring lubrication structure according to claim 3, characterized in that, The number of the oil retaining dams (4) is even, and they are symmetrically arranged in pairs about the center of the oil distribution ring (2). Furthermore, the plurality of oil distribution areas are symmetrically arranged in pairs about the center of the oil distribution ring (2); two symmetrically arranged oil distribution areas commonly correspond to a bearing lubrication oil collection port (7b) or a spline lubrication oil collection port (7a), and each oil distribution area has at least one bearing lubrication oil collection port (7b) or at least one spline lubrication oil collection port (7a) to correspondingly adjust the oil flow rate in the area by adjusting the circumferential area size of the oil distribution area.

5. The axial under-ring lubrication structure according to claim 2, characterized in that, The inner liner adapter shaft (5) includes an adapter shaft body for being mounted on the outer circumference of the central shaft, and an inner convex cylinder and an outer convex cylinder (8) which are coaxially arranged inside and outside and spaced apart and connected to the end face of the first end of the adapter shaft body. An annular cavity is formed in the annular region between the inner convex cylinder and the outer convex cylinder (8); a plurality of outwardly protruding limit clamping plates (3) are spaced apart on the outer circumferential surface of the oil distribution ring (2), and a plurality of limit grooves (9) recessed from the end face are spaced apart in the circumferential direction of the outer convex cylinder (8). The oil distribution ring (2) is press-fitted into the outer convex cylinder (8), and the limit clamping plates (3) thereon are respectively clamped in the corresponding limit grooves (9) to position the oil distribution ring (2) circumferentially.

6. The axial sub-ring lubrication structure according to claim 1, characterized in that, A plurality of oil supply nozzles (1) are sequentially spaced apart in the circumferential direction, and the injection ends of the oil supply nozzles (1) face the first end of the inner liner adapter shaft (5), and the injection ends of the oil supply nozzles (1) extend obliquely downward at an angle of 10° to 20° from the horizontal to spray the lubricating oil into the oil distribution cavity (6).

7. The axial under-ring lubrication structure according to claim 2, characterized in that, The connecting bearing includes an inner bearing ring sleeved on the outer circumference of the inner liner adapter shaft (5), an outer bearing ring (21) spaced outside the inner bearing ring, a cage (20) connected between the outer bearing ring (21) and the inner bearing ring, and a plurality of spheres (19) sequentially arranged on the cage (20); the axial ring lower lubrication structure further includes a lock nut (10) and a lock washer (11) sequentially mounted on the outer circumference of the inner liner adapter shaft (5), and a positioning shoulder (23) is formed by outward protrusion on the outer circumferential surface of the inner liner adapter shaft (5); both ends of the inner bearing ring respectively abut against the positioning shoulder (23) and the lock washer (11) for axial positioning, and the lock nut (10) is threadedly connected to the outer circumferential surface of the inner liner adapter shaft (5) to axially tighten the lock washer (11).

8. The axial under-ring lubrication structure according to claim 7, characterized in that, The inner bearing ring includes a first half inner bearing ring (14) and a second half inner bearing ring (18) sequentially arranged along the axial direction. A plurality of oil throwing holes (17) which are sequentially spaced apart in the circumferential direction and penetrate through are provided at the contact position of the first half inner bearing ring (14) and the second half inner bearing ring (18); the inner bearing ring is in clearance fit with the outer circumferential surface of the inner liner adapter shaft (5) to form an oil delivery groove (16) communicating with the plurality of oil throwing holes (17) therebetween. An annular oil collecting groove (15) communicating with the oil delivery groove (16) is also machined between the first half inner bearing ring (14) and the lock washer (11); a plurality of oil delivery channels are also provided in the inner liner adapter shaft (5) and are sequentially spaced apart in the circumferential direction. Each oil delivery channel extends obliquely along the axial direction to communicate with the corresponding bearing lubricating oil collecting port (7b) and the oil collecting groove (15), and a plurality of bearing lubricating oil collecting ports (7b), a plurality of oblique oil delivery channels (12), the oil collecting groove (15), the oil delivery groove (16) and a plurality of oil throwing holes (17) are sequentially communicated to form an oblique oil delivery channel group.

9. The axial under-ring lubrication structure according to claim 2, characterized in that, The inner lining sleeve adapter shaft (5) is also provided with a plurality of axial oil supply channel groups which are arranged at intervals in the circumferential direction in sequence. Each axial oil supply channel group extends axially to communicate with the corresponding spline lubrication oil collection port (7a) and the internal spline (25), and a plurality of spline lubrication oil collection ports (7a) and a plurality of axial oil supply channels (13) are communicated in sequence to form an axial oil supply channel group; an oil outlet (26) penetrating through the wall surface is also arranged on the wall surface of the spline section (24) of the inner lining sleeve adapter shaft (5).

10. An aeroengine, characterized in that, It has the axial lubrication structure under the ring as described in any one of claims 1-9.

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