Rear seat body structure and birotor experiment system

Abstract

The utility model discloses a rear seat body structure and a double-rotor experiment system, and relates to the technical field of aero-engines. The rear seat body structure comprises a seat body and a supporting assembly, the seat body comprises a main body part defining a first cavity, and a rotor assembly is arranged in the first cavity in a penetrating mode; the supporting assembly comprises a first bearing which is arranged in the first cavity and is connected with the high-pressure rotor, and a second bearing and a third bearing which are arranged in the first cavity and are rotationally connected with the low-pressure rotor; wherein the seat body further comprises a support, a radial plate and an annular part, one end of the support is used for being connected with the sliding rail assemblies, the other end of the support is connected with the annular part so that the annular part can be erected between the sliding rail assemblies, and the main body part penetrates through the annular part and is connected with the annular part through the radial plate. The rear seat body structure is provided with the radial plate connecting main body part and the annular part, so that the rear seat body structure can have a good vibration reduction and buffering effect.

Description

Technical Field

[0001] This utility model relates to the field of aero-engine technology, and in particular to a rear seat structure and a dual-rotor experimental system. Background Technology

[0002] The common cavity bearing structure (hereinafter referred to as the common cavity structure) is widely used in high power-to-weight ratio turboshaft engines and is one of the key technologies for engine weight reduction, compact design, improvement of power-to-weight ratio and turbine efficiency. The common cavity structure can simultaneously support the rear support point of the gas generator rotor and the front support point of the power turbine rotor, eliminating the need for the rear bearing cavity and load-bearing frame of the power turbine, reducing the number of load-bearing frames and reducing the axial dimension of the engine.

[0003] In the existing technology, the rear seat structure is a cast, monolithic rigid structure, which is prone to resonance during dual-rotor experiments. Under long-term experimental conditions, the rear seat structure is prone to fatigue damage, resulting in a short service life and making it unsuitable for long-term experimental conditions. Utility Model Content

[0004] This invention aims to solve at least one of the technical problems existing in the prior art. To this end, this invention proposes a rear seat structure that, by incorporating spokes, enables the rear seat structure to have a better vibration damping and cushioning effect.

[0005] This invention also proposes a dual-rotor experimental system having the aforementioned rear seat structure.

[0006] The rear seat structure according to a first aspect embodiment of the present invention includes:

[0007] A base, the base including a main body defining a first chamber, the rotor assembly passing through the first chamber;

[0008] The support assembly includes a first bearing disposed in the first chamber and connected to the high-pressure rotor, a second bearing disposed in the first chamber and rotatably connected to the low-pressure rotor, and a third bearing.

[0009] The seat body further includes a bracket, spokes, and an annular portion. One end of the bracket is connected to the slide rail assembly, and the other end is connected to the annular portion to support the annular portion between the slide rail assemblies. The main body passes through the annular portion and is connected to the annular portion through the spokes.

[0010] The rear seat structure according to the embodiment of this utility model has at least the following beneficial effects:

[0011] To suppress vibration and extend the service life of the seat, this application optimizes the structure of the seat. The main body is inserted through the annular part and connected to the annular part by spokes. It is understood that the annular part and the main body are connected by spokes, so that when the main body vibrates, the spokes can absorb a certain amount of vibration to achieve buffering and vibration reduction, thereby extending the service life of the rear seat structure and enabling it to be used in experimental conditions for a longer period of time.

[0012] According to some embodiments of the present invention, the main body defines an oil supply pipeline, and the support assembly further includes a first elastic support, wherein the first bearing is disposed on the inner wall surface of the first elastic support and is connected to the main body through the first elastic support;

[0013] The oil supply pipeline includes a first oil passage, which is connected to the outer wall surface of the first elastic support.

[0014] According to some embodiments of the present invention, the main body defines an oil supply pipeline, the oil supply pipeline includes a third oil passage, the oil outlet of the third oil passage is located on one side of the axial direction of the second bearing, corresponding to the oil outlet of the third oil passage, the support assembly further includes a first oil slinger ring, the first oil slinger ring defines a first oil passage groove penetrating the first oil slinger ring, and a second oil passage groove disposed on the inner wall surface of the first oil slinger ring and communicating with the first oil passage groove, the second oil passage groove being used to guide lubricating oil to the second bearing.

[0015] According to some embodiments of the present invention, the extension direction of the first oil passage groove is inclined relative to the radial direction of the first oil slinger ring, and the distance from the groove wall of the first oil passage groove to the central axis of the first oil slinger ring gradually increases along the rotation direction of the first oil slinger ring.

[0016] According to some embodiments of the present invention, the outer wall surface of the first oil slinger ring further includes a first flange and a second flange arranged at intervals and side by side, and a first oil storage space is defined between the first flange and the second flange. The support assembly further includes a second elastic support, and the second bearing is connected to the inner wall surface of the second elastic support. The first flange and the inner wall surface of the second elastic support are spaced apart to form an oil passage for lubricating oil to pass through.

[0017] According to some embodiments of the present invention, the base body defines a first opening and a second opening communicating with the first chamber, and the rotor assembly passes through the first opening and the second opening;

[0018] The base body further includes a first sealing member disposed at the first opening and a second sealing member disposed at the second opening. The first sealing member is connected to the high-pressure rotor, and the second sealing member is connected to the low-pressure rotor. Both the first sealing member and the second sealing member are graphite sealing structures.

[0019] According to a second aspect of the present invention, a dual-rotor experimental system includes a rotor assembly and a base assembly; the base assembly includes a first base structure and a second base structure located at both ends of the rotor assembly and serving as supports, wherein the second base structure is the rear base structure described in any of the above embodiments.

[0020] According to some embodiments of the present invention, the first base structure includes a first base and a first driving member and a second driving member connected to the first base. The first driving member is driven to the low-pressure rotor, and the second driving member is driven to the high-pressure rotor. The drive shaft of the first driving member is coaxial with the axis of the low-pressure rotor, and the drive shaft of the second driving member is inclined relative to the axis of the high-pressure rotor.

[0021] According to some embodiments of the present invention, the dual-rotor experimental system further includes a slide rail assembly and a third seat structure. The first seat structure and the second seat structure are slidably connected to the slide rail assembly, and the third seat structure is disposed between the first seat structure and the second seat structure and connected to the second driving member to support the second driving member.

[0022] According to some embodiments of the present invention, the high-pressure rotor includes a tie rod and a plurality of discs, each of the discs being sequentially sleeved on the tie rod along the axial direction, adjacent discs being connected by end teeth, and the two ends of the tie rod being fixed to lock each of the discs onto the tie rod.

[0023] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0024] The present invention will be further described below with reference to the accompanying drawings and embodiments, wherein:

[0025] Figure 1 This is a schematic diagram of the structure of the dual-rotor experimental system according to an embodiment of the present invention;

[0026] Figure 2 This is a schematic diagram of the rear seat structure according to an embodiment of the present utility model;

[0027] Figure 3 This is a side view of the rear seat structure according to an embodiment of the present utility model;

[0028] Figure 4 for Figure 3 Schematic diagram of the cross section along the AA direction;

[0029] Figure 5 for Figure 4 Enlarged view of region C in the middle;

[0030] Figure 6 for Figure 3 Enlarged schematic diagram of the section along the BB direction;

[0031] Figure 7 for Figure 6 Enlarged schematic diagram of region E in the middle;

[0032] Figure 8 for Figure 6 Enlarged schematic diagram of region F in the middle;

[0033] Figure 9 This is a schematic diagram of the structure of the first oil-slinging ring in an embodiment of the present invention;

[0034] Figure 10 for Figure 9 Cross-sectional view of the first oil slinger ring;

[0035] Figure 11 for Figure 5 A magnified diagram of region D in the middle.

[0036] Figure label:

[0037] Rear seat structure 10; front seat structure 20; first drive component 21; second drive component 22; rotor assembly 30; low-pressure rotor 31; turbine shaft 32; high-pressure rotor 33; tie rod 34; wheel 35; third seat structure 40; slide rail assembly 50;

[0038] Seat 100; Main body 110; First chamber 111; First oil passage 112; Second oil passage 113; First oil outlet 114; Third oil passage 116; Annular part 120; Support 130; Spoke plate 140; First opening 150; Second opening 160;

[0039] Support assembly 200; first bearing 210; first inner ring 211; first oil guide hole 2111; third oil passage groove 2112; first rolling element 212; second bearing 220; second inner ring 221; second rolling element 222; third bearing 230; first elastic support 240; second elastic support 250; first oil slinger ring 260; first oil passage groove 261; second oil passage groove 262; first flange 263; second flange 264; second oil slinger ring 270;

[0040] First sealing piece: 300; Second sealing piece: 350; Detailed Implementation

[0041] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this utility model, and should not be construed as limiting this utility model.

[0042] In the description of this utility model, it should be understood that the directional descriptions, such as up, down, front, back, left, right, etc., indicate the directional or positional relationship based on the directional or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0043] In the description of this utility model, "several" means one or more, "multiple" means two or more, "greater than," "less than," and "exceeding" are understood to exclude the stated number, while "above," "below," and "within" are understood to include the stated number. The use of "first" and "second" in the description is merely for distinguishing technical features and should not be construed as indicating or implying relative importance, or implicitly indicating the number of indicated technical features, or implicitly indicating the order of the indicated technical features.

[0044] In the description of this utility model, unless otherwise explicitly defined, terms such as "setting," "installation," and "connection" should be interpreted broadly, and those skilled in the art can reasonably determine the specific meaning of the above terms in this utility model in conjunction with the specific content of the technical solution.

[0045] In the description of this utility model, the terms "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of this utility model. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0046] The common cavity bearing structure (hereinafter referred to as the common cavity structure) is widely used in high power-to-weight ratio turboshaft engines and is one of the key technologies for engine weight reduction, compact design, improvement of power-to-weight ratio and turbine efficiency. The common cavity structure can simultaneously support the rear support point of the gas generator rotor and the front support point of the power turbine rotor, eliminating the need for the rear bearing cavity and load-bearing frame of the power turbine, reducing the number of load-bearing frames and reducing the axial dimension of the engine.

[0047] In the existing technology, the rear seat structure is a cast, monolithic rigid structure, which is prone to resonance during dual-rotor experiments. Under long-term experimental conditions, the rear seat structure is prone to fatigue damage, resulting in a short service life and making it unsuitable for long-term experimental conditions.

[0048] To address the aforementioned problems, the first aspect of this application proposes a rear seat structure 10. It should be noted that, as... Figure 1 As shown, the dual-rotor experimental system using the rear seat structure 10 also includes a front seat structure 20. The front seat structure 20 and the rear seat structure 10 jointly support the rotor assembly 30. Both the front seat structure 20 and the rear seat structure 10 are rotatably connected to the rotor assembly 30 to provide a platform for the rotational experiment of the rotor assembly 30. Specifically, the rotor assembly 30 includes a high-pressure rotor 33 and a low-pressure rotor 31. The low-pressure rotor 31 includes a turbine shaft 32. The high-pressure rotor 33 is mounted on the turbine shaft 32 and is driven by different drive components to achieve coaxial reverse rotation.

[0049] Specifically, such as Figures 2 to 5 As shown, the rear seat structure 10 includes a seat 100 and a support assembly 200. The seat 100 includes a main body 110. The main body 110 defines a first chamber 111, through which the rotor assembly 30 passes and is connected to the seat 100 via the support assembly 200. Specifically, the support assembly 200 includes a first bearing 210, a second bearing 220, and a third bearing 230. The first bearing 210 supports the rear end of the high-pressure rotor 33, and the second and third bearings 220 and 230 support the rear end of the low-pressure rotor 31. The front seat structure 20 also has three bearings to support the high-pressure rotor 33 and the low-pressure rotor 31 respectively.

[0050] It is important to note that due to the high speed of aero engines, the requirements for bearing heat dissipation and durability are extremely high. Therefore, lubrication is necessary for each bearing to facilitate heat dissipation and reduce friction. In existing technologies, each bearing has its own separate oil supply and return system, resulting in complex and space-consuming oil supply and return circuits for the entire dual-rotor system. This also significantly impacts the design layout of other structural components, making the entire system bulky. In this application, the first bearing 210, the second bearing 220, and the third bearing 230 are integrated into the first chamber 111 of the rear seat structure 10, and the bearings of the front seat structure 20 are integrated into the second chamber of the front seat structure 20. This allows for separate oil supply and return systems for the first and second chambers, and further facilitates the arrangement of lubrication channels for each bearing within the seat structure 100. This simplifies the oil supply and return circuits, optimizes the spatial layout, and improves the overall system compactness and operational efficiency.

[0051] To suppress vibration of the base 100 and extend its service life, this application optimizes the structure of the base 100. Specifically, the base 100 further includes a support 130, a spoke 140, and an annular portion 120. One end of the support 130 is used to connect to the slide rail assembly 50 of the dual-rotor experimental system, and the other end is used to connect to the annular portion 120, as shown below. Figure 1 and Figure 2 As shown, the slide rail assembly 50 includes two parallel tracks. A bracket 130 is connected to each side of the annular portion 120, so that both sides of the annular portion 120 are supported by the brackets 130, thus placing the annular portion 120 between the two tracks. The main body 110 passes through the annular portion 120 and is connected to the annular portion 120 via spokes 140. It is understood that the annular portion 120 and the main body 110 are connected by spokes 140, so that when the main body 110 vibrates, the spokes 140 can absorb some of the vibration to achieve buffering and vibration reduction, thereby extending the service life of the rear seat structure 10 and enabling it to be used in experimental conditions for a longer period.

[0052] In some embodiments, the main body 110 defines an oil supply line, and the support assembly 200 further includes a first resilient support 240, such as Figures 5 to 7 As shown, the rear end of the first elastic support 240 is fixedly connected to the base 100, and its front end extends between the first bearing 210 and the base 100. The first bearing 210 is disposed on the inner wall surface of the first elastic support 240 and is connected to the main body 110 through the first elastic support 240. The oil supply line includes a first oil passage 112, which connects to the outer wall surface of the first elastic support 240 to form a squeezed oil film between the first elastic support 240 and the base 100, effectively reducing operational vibration.

[0053] The first bearing 210 includes a first inner ring 211 and a first rolling element 212, the first rolling element 212 abutting against the inner wall surfaces of the first inner ring 211 and the first elastic support 240, respectively. It should be noted that, compared to the second bearing 220 and the third bearing 230, the first bearing 210 directly uses the first elastic support 240 as its outer ring structure, simplifying the design, reducing costs, and improving the overall compactness and integration of the structure.

[0054] In addition, the oil supply pipeline also includes a second oil line 113, such as Figure 7 As shown, the oil outlet of the second oil passage 113 is located on one side of the axial direction of the first bearing 210. The second oil passage 113 includes a first oil outlet hole 114, which extends axially and is disposed toward the first bearing 210 to spray lubricating oil toward the first bearing 210.

[0055] In some embodiments, the oil supply line further includes a third oil passage 116, such as Figures 8 to 11As shown, the oil outlet of the third oil passage 116 is located on one side of the axial direction of the second bearing 220. The support assembly 200 also includes a first oil slinger ring 260, which is set corresponding to the oil outlet of the third oil passage 116. The first oil slinger ring 260 defines a first oil passage groove 261 and a second oil passage groove 262. The first oil passage groove 261 is set through the first oil slinger ring 260, and the second oil passage groove 262 is set on the inner wall surface of the first oil slinger ring 260 and is arranged around it circumferentially. The first oil passage groove 261 and the second oil passage groove 262 are connected, so that the lubricating oil sprayed from the third oil passage 116 passes through the first oil passage groove 261 and the second oil passage groove 262 and is guided to the second bearing 220 to achieve lubrication of the second bearing 220.

[0056] It is understood that the second bearing 220 includes a second inner ring 221 and a second rolling element 222. The inner wall of the second inner ring 221 is provided with a third oil passage 2112 that communicates with the second oil passage 262. The second inner ring 221 is also provided with a first oil guide hole 2111 that penetrates the second inner ring 221, so that the lubricating oil can be guided to the contact surface of the second rolling element 222 through the oil outlet of the third oil passage 116, the first oil passage 261, the second oil passage 262, the third oil passage 2112, and the first oil guide hole 2111, thereby reducing the rolling friction of the second rolling element 222.

[0057] Furthermore, such as Figure 9 and Figure 10 As shown, the extension direction of the first oil passage groove 261 is inclined relative to the radial direction of the first oil slinger ring 260. Along the rotation direction of the first oil slinger ring 260, the distance from the groove wall of the first oil passage groove 261 to the central axis of the first oil slinger ring 260 gradually increases. It can be understood that the first oil passage groove 261 is inclined along the rotation direction, which is conducive to the entry of lubricating oil during rotation, thereby guiding the lubricating oil to the second oil passage groove 262 inside the first oil slinger ring 260.

[0058] like Figure 11 As shown, the outer wall surface of the first oil slinger ring 260 also includes a first flange 263 and a second flange 264 arranged at intervals and side by side, defining a first oil storage space between the first flange 263 and the second flange 264. The support assembly 200 also includes a second elastic support 250, as shown. Figure 6 As shown, the second bearing 220 and the third bearing 230 are respectively disposed at both ends of the axial direction of the second elastic support 250. Furthermore, both the second bearing 220 and the third bearing 230 are connected to the inner wall surface of the second elastic support 250. The first flange 263 of the first oil slinger ring 260 is spaced apart from the inner wall surface of the second elastic support 250 to form an oil passage for lubricating oil to pass through and enter the second bearing 220.

[0059] It should be noted that the third bearing 230 is also equipped with a second oil slinger ring 270. The structure of the second oil slinger ring 270 is similar to that of the first oil slinger ring 260, and the oil circuit design between the second oil slinger ring 270 and the third bearing 230 is also similar to that between the first oil slinger ring 260 and the second bearing 220. It will not be described in detail here.

[0060] In such Figure 4 and Figure 5 In the rear seat structure 10 shown, the seat 100 defines a first opening 150 and a second opening 160 communicating with the first chamber 111, and the rotor assembly 30 passes through the first opening 150 and the second opening 160. The seat 100 also includes a first sealing member 300 and a second sealing member 350. The first sealing member 300 is disposed in the first opening 150 and connected to the high-pressure rotor 33, and the second sealing member 350 is disposed in the second opening 160 and connected to the low-pressure rotor 31. Both the first sealing member 300 and the second sealing member 350 are graphite sealing structures. It should be noted that the graphite sealing structure, formed by the continuous friction between a stationary graphite component and the rotating component, has good high-temperature resistance and wear resistance, effectively preventing oil and gas leakage and improving the sealing performance and reliability of the system.

[0061] A second aspect of this application provides a dual-rotor experimental system, which includes a rotor assembly 30 and a base assembly 100. The base assembly 100 includes a first base structure and a second base structure respectively disposed at both ends of the rotor assembly 30 and serving a supporting function. The first base structure is a front base structure 20, and the second base structure is the rear base structure 10 mentioned in any of the above embodiments. It should be noted that since the dual-rotor experimental system in this embodiment includes the rear base structure 10 from the above embodiments, it inherits the advantages of the aforementioned design, such as compact structure and excellent sealing performance, which will not be elaborated further here.

[0062] In addition, such as Figure 1As shown, the first base structure includes a first base and a first driving member 21 and a second driving member 22 connected to the first base. The first driving member 21 is used to drive the low-pressure rotor 31 to rotate. Specifically, the first driving member 21 includes a motor body and a first transmission shaft extending from the motor body. The first transmission shaft and the low-pressure rotor 31 are coaxially arranged. The first transmission shaft extends along the axial direction of the rotor assembly 30 and is connected to the low-pressure rotor 31 through a coupling or other structure, thereby realizing the driving of the low-pressure rotor 31. The second driving member 22 is used to drive the high-pressure rotor 33. It includes a motor body and a second transmission shaft extending out. Since the high-pressure rotor 33 and the low-pressure rotor 31 are coaxially arranged, and the first driving member 21 is already provided at one axial end of the low-pressure rotor 31, the second driving member 22 is provided on the side of the rotor assembly 30 to avoid the first driving member 21 and realize the driving of the high-pressure rotor 33. Figure 1 As shown, the second drive unit 22 is installed above the first base, and the second drive shaft extends into the cavity of the first base and is connected to the high-pressure rotor 33. The axis of the second drive shaft intersects with the axis of the high-pressure rotor 33.

[0063] To achieve the transmission connection between the second drive member 22 and the high-pressure rotor 33, a first bevel gear is provided at the end of the second drive shaft, and a second bevel gear is provided at the front end of the high-pressure rotor 33. The first bevel gear and the second bevel gear mesh so that the second drive member 22 can drive the high-pressure rotor 33 to rotate.

[0064] Furthermore, since the second drive component 22 is in a cantilever state, it needs to be fixed to provide support and reduce shaking during operation. Therefore, the dual-rotor experimental system of this application also includes a slide rail assembly 50 and a third seat structure 40. The first and second seat structures are slidably connected to the slide rail assembly 50 and can be locked on the slide rail assembly 50 to achieve stepless adjustment between the seat structures, thereby adapting to experiments with rotor assemblies 30 of different sizes. The third seat structure 40 is disposed between the first and second seat structures and connected to the second drive component 22 to support it. Figure 1 As shown, the third base structure 40 includes two support arms located on both sides of the second drive member 22, and the two support arms form a triangular support structure to provide a stable support effect for the second drive member 22.

[0065] It should be noted that, as Figure 4As shown, the high-pressure rotor 33 of this application includes multiple discs 35. To achieve stable connection and transmission between the discs 35, adjacent discs 35 are connected by end teeth. Furthermore, the high-pressure rotor 33 also includes a tie rod 34. Each disc 35 is sequentially sleeved onto the tie rod 34 along the axial direction. The two ends of the tie rod 34 are fixed to lock each disc 35 onto the tie rod 34, thereby achieving the overall connection of the entire high-pressure rotor 33.

[0066] The embodiments of the present invention have been described in detail above with reference to the accompanying drawings. However, the present invention is not limited to the above embodiments. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of the present invention. Furthermore, the embodiments of the present invention and the features thereof can be combined with each other unless otherwise specified.

Claims

1. A rear seat structure for supporting a rotor assembly, the rotor assembly including a high-pressure rotor and a low-pressure rotor, the low-pressure rotor including a turbine shaft, the high-pressure rotor being sleeved on the turbine shaft, characterized in that, include: A base, the base including a main body defining a first chamber, the rotor assembly passing through the first chamber; The support assembly includes a first bearing disposed in the first chamber and connected to the high-pressure rotor, a second bearing disposed in the first chamber and rotatably connected to the low-pressure rotor, and a third bearing. The seat body further includes a bracket, spokes, and an annular portion. One end of the bracket is connected to the slide rail assembly, and the other end is connected to the annular portion to support the annular portion between the slide rail assemblies. The main body passes through the annular portion and is connected to the annular portion through the spokes.

2. The rear seat structure according to claim 1, characterized in that, The main body defines an oil supply line, and the support assembly further includes a first elastic support. The first bearing is disposed on the inner wall surface of the first elastic support and is connected to the main body through the first elastic support. The oil supply pipeline includes a first oil passage, which is connected to the outer wall surface of the first elastic support.

3. The rear seat structure according to claim 1, characterized in that, The main body defines an oil supply line, which includes a third oil passage. The oil outlet of the third oil passage is located on one side of the axial direction of the second bearing. Corresponding to the oil outlet of the third oil passage, the support assembly also includes a first oil slinger ring. The first oil slinger ring defines a first oil passage groove that extends through the first oil slinger ring and a second oil passage groove disposed on the inner wall surface of the first oil slinger ring and communicating with the first oil passage groove. The second oil passage groove is used to guide lubricating oil to the second bearing.

4. The rear seat structure according to claim 3, characterized in that, The extension direction of the first oil passage groove is inclined relative to the radial direction of the first oil slinger ring. Along the rotation direction of the first oil slinger ring, the distance from the groove wall of the first oil passage groove to the central axis of the first oil slinger ring gradually increases.

5. The rear seat structure according to claim 3, characterized in that, The outer wall of the first oil slinger ring also includes a first flange and a second flange arranged at intervals and side by side, defining a first oil storage space between the first flange and the second flange. The support assembly also includes a second elastic support, and the second bearing is connected to the inner wall of the second elastic support. The first flange and the inner wall of the second elastic support are spaced apart to form an oil passage for lubricating oil to pass through.

6. The rear seat structure according to claim 1, characterized in that, The base body defines a first opening and a second opening communicating with the first chamber, and the rotor assembly passes through the first opening and the second opening; The base body further includes a first sealing member disposed at the first opening and a second sealing member disposed at the second opening. The first sealing member is connected to the high-pressure rotor, and the second sealing member is connected to the low-pressure rotor. Both the first sealing member and the second sealing member are graphite sealing structures.

7. A dual-rotor experimental system, characterized in that, include: Rotor assembly; A base assembly, the base assembly comprising a first base structure and a second base structure respectively located at both ends of the rotor assembly and serving as supports, the second base structure being a rear base structure as described in any one of claims 1 to 6.

8. The dual-rotor experimental system according to claim 7, characterized in that, The first base structure includes a first base and a first driving member and a second driving member connected to the first base. The first driving member is driven by the low-pressure rotor, and the second driving member is driven by the high-pressure rotor. The drive shaft of the first driving member is coaxial with the axis of the low-pressure rotor, and the drive shaft of the second driving member is inclined relative to the axis of the high-pressure rotor.

9. The dual-rotor experimental system according to claim 8, characterized in that, The dual-rotor experimental system further includes a slide rail assembly and a third seat structure. The first seat structure and the second seat structure are slidably connected to the slide rail assembly, respectively. The third seat structure is disposed between the first seat structure and the second seat structure and is connected to the second driving member to support the second driving member.

10. The dual-rotor experimental system according to claim 7, characterized in that, The high-pressure rotor includes a tie rod and multiple discs. Each disc is sequentially sleeved on the tie rod along the axial direction. Adjacent discs are connected by end teeth. The two ends of the tie rod are fixed to lock each disc onto the tie rod.

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