A marine mixed flow turbocharger rolling bearing rotor structure

Abstract

The utility model discloses a marine mixed flow turbine supercharger rolling bearing rotor structure, improves the problem that sliding bearing rotor low load response is slow. Including bearing shell, pressure gas impeller, turbine shaft, fixed pressure end bearing seat, vortex end bearing seat in bearing shell, is equipped with damper in each bearing seat respectively, and the clearance of entering oil is left between bearing seat, damper, is equipped with rolling bearing in damper, and turbine shaft is installed on two rolling bearings, pressure end bearing seat is installed with sliding thrust bearing, pressure end bearing cover, and the sliding thrust bearing is positioned on the sliding thrust bearing in the circumferential direction, and the oil throwing disc is established between pressure gas impeller, pressure end bearing cover, and the step is established on the oil throwing disc, and the oil throwing disc step passes through pressure end bearing cover and cooperates with sliding thrust bearing, and the annular thrust bearing is equipped in pressure end bearing seat, and the pressure end rolling bearing is sleeved on the annular thrust bearing, and the oil throwing disc, the annular thrust bearing sleeve is on turbine shaft, and the both ends of annular thrust bearing act on sliding thrust bearing, pressure end rolling bearing.

Description

Technical Field

[0001] This utility model relates to the technical field, and in particular to a rolling bearing rotor structure for a marine mixed-flow turbocharger. Background Technology

[0002] Rapid responsiveness is a crucial performance indicator for diesel engines. As a key component of the turbocharger system, the turbocharger's rotor response capability directly impacts the engine's transient performance. High-power-density diesel engines demand higher pressure ratios from turbochargers. When the single-stage pressure ratio reaches 5.0 or higher, the rotor speed increases, aerodynamic loads rise, and the structural strength of rotating components needs further reinforcement. This leads to increased friction in the existing sliding bearing system, slow rotor start-up response, and poor turbocharger-engine matching performance. Therefore, designing a low-loss rolling bearing rotor structure is an effective solution to improve the slow low-load response of the existing sliding bearing rotor. Summary of the Invention

[0003] The purpose of this invention is to overcome the shortcomings of the prior art and provide a rolling bearing rotor structure for a marine mixed-flow turbocharger, thereby improving the problem of slow low-load response of sliding bearing rotors.

[0004] The purpose of this utility model is achieved as follows: A marine mixed-flow turbocharger rolling bearing rotor structure includes a bearing housing (2), a compressor impeller (1), and a turbine shaft (9). The compressor impeller (1) is mounted on the shaft portion of the turbine shaft (9). The turbine portion of the turbine shaft (9) and the compressor impeller (1) are located on the outer sides of both ends of the bearing housing (2). A pressure end bearing seat (6) and a vortex end bearing seat (7) are fixed inside the bearing housing (2). A pressure end damper (15) is provided inside the pressure end bearing seat (6), and the vortex end bearing seat (7) is... The turbine shaft (9) is equipped with a vortex end damper (12), and there is a lubricating oil inlet gap between the pressure end bearing housing (6) and the pressure end damper (15). There is a lubricating oil inlet gap between the vortex end bearing housing (7) and the vortex end damper (12). The pressure end damper (15) is equipped with a pressure end rolling bearing (16), and the vortex end damper (12) is equipped with a vortex end rolling bearing (11). The shaft portion of the turbine shaft (9) is installed in the pressure end rolling bearing (16) and the vortex end rolling bearing (11). The pressure end of the pressure end bearing housing (6) is equipped with a sliding thrust bearing (5) and a pressure end bearing cover (4). The sliding thrust bearing (5) is circumferentially positioned on the sliding thrust bearing (5) and can slide axially. An oil slinger (3) is provided between the compressor impeller (1) and the pressure end bearing cover (4). The oil slinger (3) has a step. The step of the oil slinger (3) passes through the pressure end bearing cover (4) and cooperates with the sliding thrust bearing (5). An annular thrust bearing (17) is provided inside the pressure end bearing housing (6). The oil slinger (3) and the annular thrust bearing (17) are sleeved on the shaft of the turbine shaft (9). The two ends of the annular thrust bearing (17) act on the sliding thrust bearing (5) and the pressure end rolling bearing (16) respectively. The oil slinger (3), the pressure end bearing cover (4), the sliding thrust bearing (5), the pressure end bearing housing (6) and the annular thrust bearing (17) form an axial bearing pair to balance the axial thrust of the rotor at high speed.

[0005] Specifically: the main thrust surface (5a) on the sliding bearing (5) and the oil slinger (3) form a bearing pair to balance the axial thrust from the pressure end to the vortex end; the auxiliary thrust surface (5b) on the sliding bearing (5) and the ring thrust bearing (17) form a bearing pair to balance the axial thrust from the pressure end to the vortex end.

[0006] Preferably, both the pressure end rolling bearing (16) and the vortex end rolling bearing (11) are angular contact rolling bearings.

[0007] Preferably, the pressure end bearing housing (6) has a pressure end bearing housing hole (6d) and a pressure end circumferential limiting groove (6h). The pressure end bearing housing hole (6d) is used to install the pressure end damper (15), and the pressure end circumferential limiting groove (6h) is used to circumferentially limit the pressure end damper (15). The pressure end bearing housing (6) is provided with an oil inlet hole (6a) and a pressure end oil supply ring groove (6f). The oil inlet hole (6a) is a radial through hole, and the pressure end oil supply ring groove (6f) is located on one end of the inner wall of the pressure end bearing housing (6) and communicates with the oil inlet hole (6a). The pressure end oil supply ring groove (6f) inputs lubricating oil into the lubricating oil inlet gap for oil supply to the pressure end rolling bearing (16) and the pressure end damper (15).

[0008] Preferably, the pressure end bearing seat hole (6d) is provided with a positioning pin hole (6c) and a sliding thrust bearing mounting platform (6j), which are used for positioning and installing the sliding thrust bearing (5). The sliding thrust bearing mounting platform (6j) is provided with a sliding thrust bearing oil inlet hole (6g) along the axial direction. The sliding thrust bearing oil inlet hole (6g) is connected to the pressure end oil supply ring groove (6f). The sliding thrust bearing oil inlet hole (6g) is used to supply oil to the sliding thrust bearing (5). The pressure end bearing housing (6) is provided with a pressure end oil return hole (6e). The axial and radial positions of the pressure end oil return hole (6e) are opposite to those of the oil inlet hole (6a). The pressure end oil return hole (6e) is used for the return of oil from the pressure end rolling bearing (6) and the pressure end damper (15).

[0009] Preferably, the vortex end bearing housing (7) is provided with a vortex end bearing housing hole (7g) and a vortex end circumferential limiting groove (7f). The vortex end bearing housing hole (7g) is used to install the vortex end damper (12), and the vortex end circumferential limiting groove (7f) is used to limit the vortex end damper (12) circumferentially. The volute bearing housing (7) is provided with a volute bearing oil supply hole (7e) and a volute oil supply ring groove (7j). The volute bearing oil supply hole (7e) is connected to the volute oil supply ring groove (7j). The volute oil supply ring groove (7j) is used to supply oil to the volute rolling bearing (11) and the volute damper (12). The upper end of the vortex bearing housing (7) is provided with an oil injection hole (7b). The oil injection hole (7b) is a radial through hole. The oil injection hole (7b) is connected to the vortex bearing housing hole (7g). The oil injection hole (7b) is used to cool part of the vortex bearing housing (7) near the high temperature area of ​​the turbine (9). The volute bearing housing (7) is provided with a volute return oil hole (7k) and an oil drain groove (12f) for the return oil of the volute rolling bearing (11) and the volute damper (12).

[0010] The vortex end bearing is located on the gas inlet side, and the high temperature of the gas is transferred to this part of the bearing housing, so oil is injected to cool it down.

[0011] Preferably, the volute end of the volute bearing housing (7) is provided with an oil baffle mounting boss (7c), and an oil baffle (8) is mounted on the mounting boss (7c).

[0012] Preferably, the pressure end damper (12) and the vortex end damper (15) are respectively provided with rolling bearing mounting holes, limiting bosses, spring mounting holes, oil supply ring grooves, damper oil inlets and drain grooves; the two dampers have symmetrical structures.

[0013] The rolling bearing mounting hole is used to install the corresponding rolling bearing; the limiting boss is used to circumferentially limit the fit with the bearing seat at the corresponding end; the spring mounting hole is set along the axial direction, and a cylindrical compression spring is installed in the spring mounting hole. The cylindrical compression spring provides axial preload for the pressure end rolling bearing (16) and the scroll end rolling bearing (11). The oil supply ring groove is set on the outer circular surface of the corresponding damper. The oil inlet of the damper is a radial through hole and is connected to the oil supply ring groove. The oil inlet of the damper is used to guide the lubricating oil to the surface of the corresponding rolling bearing. The oil drain groove is located between the rolling bearing mounting hole and the spring mounting hole (on the step). The oil drain groove is used to return the lubricating oil in the corresponding rolling bearing.

[0014] Due to the adoption of the above technical solution, this utility model has the following beneficial effects: (1) The present invention provides a rolling bearing rotor structure for a marine mixed-flow turbocharger, which solves the problem of slow response of the original sliding bearing in the high-pressure turbocharger.

[0015] (2) The present invention provides a marine mixed-flow turbocharger rolling bearing rotor structure. By installing a damper on the rolling bearing, the problem of the rolling bearing being sensitive to vibration of the high-speed rotating rotor is solved, and the service life of the rolling bearing reaches more than 12,000 hours.

[0016] (3) The present invention provides a marine mixed-flow turbocharger rolling bearing rotor structure, which adopts an internally supported rolling bearing structure, thereby replacing the rolling bearing rotor with a sliding bearing rotor. The friction coefficient of the rolling bearing is 0.001-0.005, while the friction coefficient of the radial sliding bearing pair (steel and bronze) is 0.08-0.12 during startup. Due to insufficient power input from the turbine under low operating conditions, the turbocharger using the hydrodynamic sliding bearing starts up slowly. Therefore, the turbocharger using the rolling bearing responds quickly under low operating conditions, effectively improving the turbocharger's response capability and solving the problem of black smoke from the diesel engine under low operating conditions.

[0017] (4) This utility model has the advantages of ingenious design, convenient installation and efficient assembly. Attached Figure Description

[0018] Figure 1 Schematic diagram of the rolling bearing rotor structure of a mixed-flow turbocharger; Figure 2 Schematic diagram of the pressure end bearing housing; Figure 3 Schematic diagram of the vortex end bearing housing; Figure 4 Schematic diagram of a vortex / voltage end damper; Figure 5 This is a schematic diagram of a sliding thrust bearing.

[0019] Figure Labels In the attached diagram, 1 is the compressor impeller, 2 is the bearing housing, 3 is the oil slinger, 4 is the pressure end bearing cover, 5 is the sliding thrust bearing, 5a is the main thrust surface, 5b is the auxiliary thrust surface, 5c is the sliding bearing oil inlet, 6 is the pressure end bearing housing, 6a is the oil inlet, 6b is the bearing cover mounting screw hole, 6c is the locating pin hole, 6d is the pressure end bearing housing hole, 6e is the pressure end oil return hole, 6f is the pressure end oil supply ring groove, 6g is the sliding thrust bearing oil inlet, 6h is the pressure end circumferential limiting groove, 6j is the sliding thrust bearing mounting platform, 6k is the pressure end bearing housing mounting hole, 7 is the scroll end bearing housing, 7a is the scroll end bearing housing mounting hole, 7b is the oil injection hole, 7c is the oil baffle mounting platform, 7d is the oil baffle fixing hole, 7e is the scroll end bearing oil supply hole, 7f is the scroll end circumferential limiting groove, and 7g is the scroll end bearing... 7h is the oil drain groove, 7j is the vortex end oil supply ring groove, 7k is the vortex end oil return hole, 8 is the oil baffle plate, 9 is the turbine shaft, 10 is the vortex end bearing bushing, 11 is the vortex end rolling bearing, 12 is the vortex end damper, 12a is the vortex end oil supply ring groove, 12b is the damping outer ring, 12c is the limiting boss, 12d is the damper oil inlet hole, 12e is the vortex end rolling bearing mounting hole, 12f is the vortex end oil drain groove, 12g is the vortex end spring mounting hole, 13 is the spring, 14 is the support sleeve, 15 is the pressure end damper, 15a is the pressure end oil supply ring groove, 15b is the damping outer ring, 15c is the limiting boss, 15d is the oil inlet hole, 15e is the pressure end rolling bearing mounting hole, 15f is the pressure end oil drain groove, 15g is the pressure end spring mounting hole, 16 is the pressure end rolling bearing, and 17 is the ring thrust bearing. Detailed Implementation

[0020] See Figures 1-5 A marine mixed-flow turbocharger rolling bearing rotor structure includes a bearing housing 2, a compressor impeller 1, and a turbine shaft 9. The compressor impeller 1 is mounted on the shaft portion of the turbine shaft 9. The turbine portion of the turbine shaft 9 and the compressor impeller 1 are located on the outer sides of both ends of the bearing housing 2. A pressure end bearing seat 6 and a vortex end bearing seat 7 are fixed inside the bearing housing 2. A pressure end damper 15 is provided inside the pressure end bearing seat 6, and a vortex end damper 12 is provided inside the vortex end bearing seat 7. A lubricating oil inlet gap is left between the pressure end bearing seat 6 and the pressure end damper 15, and a lubricating oil inlet gap is left between the vortex end bearing seat 7 and the vortex end damper 12. A pressure end rolling bearing 16 is provided inside the pressure end damper 15, and a vortex end rolling bearing 11 is provided inside the vortex end damper 12. The shaft portion of the turbine shaft 9 is mounted inside the pressure end rolling bearing 16 and the vortex end rolling bearing 11. The pressure end of the pressure end bearing housing 6 is equipped with a sliding thrust bearing 5 and a pressure end bearing cover 4. The sliding thrust bearing 5 is circumferentially positioned on the pressure end bearing housing 6 and can slide axially. An oil slinger 3 is provided between the compressor impeller 1 and the pressure end bearing cover 4. The oil slinger 3 has a step, which passes through the pressure end bearing cover 4 and cooperates with the sliding thrust bearing 5. An annular thrust bearing 17 is provided inside the pressure end bearing housing 6. The oil slinger 3 and the annular thrust bearing 17 are sleeved on the shaft of the turbine shaft 9. The two ends of the annular thrust bearing 17 act on the sliding thrust bearing 5 and the pressure end rolling bearing 16, respectively. The oil slinger 3, the pressure end bearing cover 4, the sliding thrust bearing 5, the pressure end bearing housing 6 and the annular thrust bearing 17 form an axial bearing pair to balance the axial thrust of the rotor at high speed.

[0021] In this embodiment, the main thrust surface 5a on the sliding bearing 5 and the oil slinger 3 form a bearing pair to balance the axial thrust from the pressure end to the vortex end; the auxiliary thrust surface 5b on the sliding bearing 5 and the ring thrust bearing 17 form a bearing pair to balance the axial thrust from the pressure end to the vortex end.

[0022] As a further technical solution, both the pressure end rolling bearing 16 and the vortex end rolling bearing 11 are angular contact rolling bearings.

[0023] As a further technical solution, the pressure end bearing housing 6 has a pressure end bearing housing hole 6d and a pressure end circumferential limiting groove 6h. The pressure end bearing housing hole 6d is used to install the pressure end damper 15, and the pressure end circumferential limiting groove 6h is used to circumferentially limit the pressure end damper 15. The pressure end bearing housing 6 is provided with an oil inlet hole 6a and a pressure end oil supply ring groove 6f. The oil inlet hole 6a is a radial through hole, and the pressure end oil supply ring groove 6f is located on one end of the inner wall of the pressure end bearing housing 6 and communicates with the oil inlet hole 6a. The pressure end oil supply ring groove 6f inputs lubricating oil into the lubricating oil inlet gap for oil supply to the pressure end rolling bearing 16 and the pressure end damper 15.

[0024] As a further technical solution, the pressure end bearing seat hole 6d is provided with a positioning pin hole 6c and a sliding thrust bearing mounting platform 6j. The positioning pin hole 6c and the sliding thrust bearing mounting platform 6j are used for positioning and installing the sliding thrust bearing 5. The sliding thrust bearing mounting platform 6j is provided with a sliding thrust bearing oil inlet 6g along the axial direction. The sliding thrust bearing oil inlet 6g is connected to the pressure end oil supply ring groove 6f. The sliding thrust bearing oil inlet 6g is used to supply oil to the sliding thrust bearing 5. The pressure end bearing housing 6 is provided with a pressure end oil return hole 6e. The axial and radial positions of the pressure end oil return hole 6e are opposite to those of the oil inlet hole 6a. The pressure end oil return hole 6e is used for the return of oil from the pressure end rolling bearing 6 and the pressure end damper 15.

[0025] As a further technical solution, the vortex end bearing seat 7 is provided with a vortex end bearing seat hole 7g and a vortex end circumferential limiting groove 7f. The vortex end bearing seat hole 7g is used to install the vortex end damper 12, and the vortex end circumferential limiting groove 7f is used to limit the vortex end damper 12 circumferentially. The volute bearing housing 7 is provided with a volute bearing oil supply hole 7e and a volute oil supply ring groove 7j. The volute bearing oil supply hole 7e is connected to the volute oil supply ring groove 7j, and the volute oil supply ring groove 7j is used to supply oil to the volute rolling bearing 11 and the volute damper 12. The upper end of the turbine bearing housing 7 is provided with an oil injection hole 7b, which is a radial through hole. The oil injection hole 7b is connected to the turbine bearing housing hole 7g. The oil injection hole 7b is used to cool part of the turbine bearing housing 7 near the high temperature area of ​​the turbine 9. The volute bearing housing 7 is provided with a volute return oil hole 7k and an oil drain groove 12f for oil return from the volute rolling bearing 11 and the volute damper 12.

[0026] The vortex end bearing is located on the gas inlet side, and the high temperature of the gas is transferred to this part of the bearing housing, so oil is injected to cool it down.

[0027] As a further technical solution, the scroll end of the scroll bearing housing 7 is provided with an oil baffle mounting boss 7c, and an oil baffle 8 is mounted on the mounting boss 7c.

[0028] As a further technical solution, the pressure end damper 15 and the vortex end damper 12 are respectively provided with rolling bearing mounting holes, limiting bosses, spring mounting holes, oil supply ring grooves, damper oil inlets and drain grooves; the two dampers have a symmetrical structure.

[0029] The rolling bearing mounting hole is used to install the corresponding rolling bearing; the limiting boss is used to limit the circumferential fit with the bearing seat at the corresponding end; the spring mounting hole is set along the axial direction, and a cylindrical compression spring is installed in the spring mounting hole. The cylindrical compression spring provides axial preload for the pressure end rolling bearing 16 and the scroll end rolling bearing 11. The oil supply ring groove is set on the outer circular surface of the corresponding damper. The oil inlet of the damper is a radial through hole and is connected to the oil supply ring groove. The oil inlet of the damper is used to guide the lubricating oil to the surface of the corresponding rolling bearing. The oil drain groove is located between the rolling bearing mounting hole and the spring mounting hole (on the step). The oil drain groove is used to return the lubricating oil in the corresponding rolling bearing.

[0030] Specifically: like Figure 1As shown, a marine mixed-flow turbocharger rolling bearing rotor structure includes a compressor impeller 1, an oil slinger 3, a pressure end bearing cover 4, a sliding thrust bearing 5, a pressure end bearing housing 6, a vortex end bearing housing 7, a vortex end bearing bushing 10, a pressure end rolling bearing 11, a vortex end rolling bearing 16, a turbine shaft 9, a support sleeve 14, and an annular thrust bearing 17. The pressure end rolling bearing 16 and the vortex end rolling bearing 11 are angular contact rolling bearings, mounted face-to-face on the pressure end damper 15 and the vortex end damper 12 respectively; the pressure end damper 15 and the vortex end damper 12 are then mounted on the pressure end bearing housing 6 and the vortex end bearing housing 7 respectively, for radial support of the rolling bearing rotor structure. like Figure 1 As shown, the pressure-end damper 15 and the volute-end damper 12 have certain radial clearances with the pressure-end bearing seat hole 6d and the volute-end bearing seat hole 7a, respectively, allowing lubricating oil to enter and function as oil film dampers to provide damping for vibrations during the rotation of the rolling bearing rotor, thereby increasing the stability of the rolling bearing rotor operation. The oil slinger 3, pressure-end bearing cover 4, sliding thrust bearing 5, pressure-end bearing seat 6, and annular thrust bearing 17 form the axial bearing pair of the rolling bearing rotor structure, used to balance the axial thrust of the rotor at high speeds.

[0031] like Figure 2 As shown, the pressure end bearing seat 6 has a bearing seat hole 6d (center hole) and three pressure end circumferential limiting grooves 6h for the installation and circumferential limiting of the pressure end damper 15, realizing the function of the external oil film extrusion damper; the pressure end bearing seat 6 has three oil inlet holes 6a and one pressure end oil supply ring groove 6f (connected, oil can be distributed circumferentially) in the circumferential direction for the oil supply of the pressure end rolling bearing 16 and the pressure end damper 15.

[0032] like Figure 2 As shown, the pressure end bearing seat hole 6d is provided with a positioning pin hole 6c and a sliding thrust bearing mounting platform 6j for positioning and installing the sliding thrust bearing 5; the pressure end bearing seat 6 is provided with a sliding thrust bearing oil inlet hole 6g, which connects to the pressure end oil supply ring groove 6f for supplying oil to the sliding thrust bearing 5. The pressure end bearing seat 6 is also provided with a pressure end oil return hole 6e for returning the cooling and lubricating oil of the pressure end rolling bearing 6 and the pressure end damper 15; the pressure end bearing seat 6 is provided with a pressure end bearing seat mounting hole 6k for mounting the pressure end bearing seat 6 on the bearing housing 2; the pressure end bearing seat 6 is provided with a bearing cover mounting screw hole 6b for fixing the pressure end bearing cover 4.

[0033] like Figure 3As shown, the volute end rolling bearing housing 7 has a volute end bearing housing hole 7g and three volute end circumferential limiting grooves 7f for mounting and circumferentially limiting the volute end damper 12, realizing the function of an external oil film extrusion damper; the volute end bearing housing 7 has three volute end bearing oil supply holes 7e and one volute end oil supply ring groove 7j for supplying oil to the volute end rolling bearing 11 and the volute end damper 12; two oil injection holes 7b are provided directly above the volute end bearing housing 7 for... The volute bearing housing 7 is located near the high-temperature area of ​​the turbine 9 to cool down the area of ​​the volute rolling bearing 11 and prevent coking due to excessive temperature. The volute bearing housing 7 is provided with a volute oil return hole 7k, and the volute oil return hole 7k and the oil drain groove 12f are used for the return of cooling lubricating oil from the volute rolling bearing 11 and the volute damper 12. At the same time, the volute bearing housing 7 is provided with an oil baffle mounting boss 7c for the installation of the oil baffle 8 to prevent the lubricating oil of the volute rolling bearing 11 from leaking to the turbine side.

[0034] like Figure 4 As shown, the pressure end damper 15 and the volute end damper 12 are respectively provided with pressure end rolling bearing mounting holes and volute end rolling bearing mounting holes for mounting the pressure end rolling bearing 16 and the volute end rolling bearing 11; the pressure end damper 15 and the volute end damper 12 are respectively provided with an oil supply ring groove, two damper oil inlet holes and six oil drain grooves for oil inlet and return for lubrication of the pressure end rolling bearing 15 and the volute end rolling bearing 11; the pressure end damper 15 and the volute end damper 12 are each provided with three limiting bosses, which are circumferentially limitingly matched with the pressure end bearing seat 6 and the volute end bearing seat 7.

[0035] like Figure 4 As shown, the pressure end damper 15 and the volute end damper 12 are provided with spring mounting holes for mounting cylindrical compression springs 13, which provide axial preload for the pressure end rolling bearing 15 and the volute end rolling bearing 11, ensuring the stability of the pressure end rolling bearing 15 and the volute end rolling bearing 11 at high rotor speeds.

[0036] Finally, it should be noted that the above preferred embodiments are only used to illustrate the technical solution of this utility model and are not intended to limit it. Although the utility model has been described in detail through the above preferred embodiments, those skilled in the art should understand that various changes can be made to it in form and detail without departing from the scope defined by the claims of this utility model.

Claims

1. A rolling bearing rotor structure for a marine mixed-flow turbocharger, characterized in that: The device includes a bearing housing, a compressor impeller, and a turbine shaft. The compressor impeller is mounted on the shaft portion of the turbine shaft. The turbine portion of the turbine shaft and the compressor impeller are located on the outer sides of both ends of the bearing housing. A pressure end bearing seat and a volute end bearing seat are fixed inside the bearing housing. A pressure end damper is installed inside the pressure end bearing seat, and a volute end damper is installed inside the volute end bearing seat. An oil inlet gap is left between the pressure end bearing seat and the pressure end damper. An oil inlet gap is left between the volute end bearing seat and the volute end damper. A pressure end rolling bearing is installed inside the pressure end damper, and a volute end rolling bearing is installed inside the volute end damper. The shaft portion of the turbine shaft is installed inside the pressure end rolling bearing and the volute end rolling bearing. The pressure end of the pressure end bearing housing is equipped with a sliding thrust bearing and a pressure end bearing cover. The sliding thrust bearing is circumferentially positioned on the pressure end bearing and can slide axially. An oil slinger is provided between the compressor impeller and the pressure end bearing cover. The oil slinger has a step, which passes through the pressure end bearing cover and cooperates with the sliding thrust bearing. An annular thrust bearing is provided inside the pressure end bearing housing. A pressure end rolling bearing is sleeved on the annular thrust bearing. The oil slinger and the annular thrust bearing are sleeved on the shaft portion of the turbine shaft. The two ends of the annular thrust bearing act on the sliding thrust bearing and the pressure end rolling bearing, respectively. The oil slinger, the pressure end bearing cover, the sliding thrust bearing, the pressure end bearing housing, and the annular thrust bearing form an axial bearing pair to balance the axial thrust of the rotor at high speeds.

2. The marine mixed-flow turbocharger rolling bearing rotor structure according to claim 1, characterized in that: Both the pressure end rolling bearing and the scroll end rolling bearing are angular contact rolling bearings.

3. The marine mixed-flow turbocharger rolling bearing rotor structure according to claim 1, characterized in that: The pressure end bearing housing has a pressure end bearing housing hole and a pressure end circumferential limiting groove. The pressure end bearing housing hole is used to install the pressure end damper, and the pressure end circumferential limiting groove is used to limit the pressure end damper circumferentially. The pressure end bearing housing is provided with an oil inlet hole and a pressure end oil supply ring groove. The oil inlet hole is a radial through hole, and the pressure end oil supply ring groove is located on one end of the inner wall of the pressure end bearing housing and communicates with the oil inlet hole.

4. The marine mixed-flow turbocharger rolling bearing rotor structure according to claim 3, characterized in that: The pressure end bearing seat hole is provided with a positioning pin hole and a sliding thrust bearing mounting platform. The positioning pin hole and the sliding thrust bearing mounting platform are used for positioning and installing the sliding thrust bearing. The sliding thrust bearing mounting platform is provided with an axial oil inlet hole for the sliding thrust bearing. The oil inlet hole is connected to the oil supply ring groove at the pressure end and is used to supply oil to the sliding thrust bearing. The pressure end bearing housing is provided with a pressure end oil return hole. The axial and radial positions of the pressure end oil return hole are opposite to those of the oil inlet hole. The pressure end oil return hole is used for oil return from the pressure end rolling bearing and the pressure end damper.

5. The rolling bearing rotor structure for a marine mixed-flow turbocharger according to claim 1, characterized in that: The vortex end bearing housing is provided with a vortex end bearing housing hole and a vortex end circumferential limiting groove. The vortex end bearing housing hole is used to install the vortex end damper, and the vortex end circumferential limiting groove is used to limit the vortex end damper circumferentially. The volute bearing housing is provided with a volute bearing oil supply hole and a volute oil supply ring groove. The volute bearing oil supply hole is connected to the volute oil supply ring groove, which is used to supply oil to the volute rolling bearing and the volute damper. The turbine bearing housing is provided with an oil injection hole, which is a radial through hole and is connected to the turbine bearing housing hole. The oil injection hole is used to cool the part of the turbine bearing housing near the turbine area. The volute bearing housing is provided with a volute return oil hole, which is used for oil return from the volute rolling bearing.

6. The rolling bearing rotor structure for a marine mixed-flow turbocharger according to claim 5, characterized in that: The scroll end of the bearing housing is provided with an oil baffle mounting boss, and an oil baffle is installed on the mounting boss.

7. The marine mixed-flow turbocharger rolling bearing rotor structure according to claim 1, characterized in that: The pressure end damper and the vortex end damper are respectively provided with rolling bearing mounting holes, limiting bosses, spring mounting holes, oil supply ring grooves, damper oil inlets and oil drain grooves. The rolling bearing mounting hole is used to install the corresponding rolling bearing; the limiting boss is used to limit the circumferential fit with the bearing seat at the corresponding end; the spring mounting hole is set along the axial direction, and a cylindrical compression spring is installed in the spring mounting hole. The cylindrical compression spring provides axial preload for the pressure end rolling bearing and the scroll end rolling bearing. The oil supply ring groove is set on the outer circular surface of the corresponding damper. The oil inlet of the damper is a radial through hole and is connected to the oil supply ring groove. The oil inlet of the damper is used to guide the lubricating oil to the surface of the corresponding rolling bearing. The oil drain groove is located between the rolling bearing mounting hole and the spring mounting hole. The oil drain groove is used to return the lubricating oil in the corresponding rolling bearing.

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