A pneumatic axial force loading device

Abstract

A pneumatic axial force loading device, which relates to an axial force loading device. The present invention aims to solve the problem that the existing axial force loading device needs to provide additional hydraulic components, which leads to a large volume and easy occurrence of eccentric loading. The present invention selects compressed air as the loading medium. Compared with hydraulic cylinder loading, compressed air is non-toxic, harmless, and has no pollution to the environment, and is energy-saving and environmentally friendly. Compared with hydraulic cylinder loading, the present invention only needs to adjust the pressure of the air supply line to complete the loading, and the loading efficiency is high; in hydraulic cylinder loading, the servo valve has high requirements on the accuracy of the oil. Before use, the entire loading oil circuit needs to be oiled, and then the oil needs to be tested for particle size. It can only be used after it passes the test; and the present invention has lower cost and is more convenient to operate; air loading only requires compressed air, while hydraulic cylinder loading requires hydraulic cylinders, hydraulic loading oil stations, lubricating oil stations, servo valves, filter elements, pipelines, etc. The present invention belongs to the technical field of axial loading of rotating parts.

Description

Technical Field

[0001] The present invention relates to an axial force loading device, in particular to a pneumatic axial force loading device, and belongs to the technical field of axial loading of rotating parts. Background Art

[0002] Many components in rotational testing equipment use pivot rolling bearings to withstand axial forces. These bearings are characterized by their ability to operate stably only under axial forces. For example, in an aircraft turbofan engine, the axial forces generated by the fan rotor's rotation are borne by its internal three-pivot ball bearings. However, during ground testing, additional equipment is required to provide axial forces to simulate the axial forces caused by fan rotation. Similarly, thrust bearing testers also require additional axial forces to assess the bearing's load-bearing capacity.

[0003] Among known axial force loading devices, loading is often achieved by combining a loading bearing seat with a hydraulic cylinder. For example, the patent with announcement number CN110836773B discloses a transmission test bench equivalent to simulate the central transmission main shaft bearing force loading device. The technical solution of this patent is to install a loading bearing seat on the transmission shaft. The rolling bearing in the bearing seat is a test bearing. The inner ring of the bearing is interference-connected with the transmission shaft and rotates together; the outer ring of the bearing is connected to the bearing seat and remains stationary. A hydraulic cylinder is set on the end face of the bearing seat, and an axial force is applied to the bearing seat through the hydraulic cylinder. The axial force is transmitted to the transmission shaft through the outer ring of the bearing, the rolling elements, and the inner ring of the bearing, and then the axial force is transmitted to the test bearing. The axial force of this loading method is limited by the performance of the test bearing in the bearing seat. The advantage is a compact structure, and the disadvantage is that it cannot withstand large axial forces. It is mainly used for axial force loading under high speed conditions.

[0004] Another example is patent publication number CN216846905U, which discloses a high-thrust, high-speed axial force loading device. This patent's technical solution utilizes a tilting-pad thrust sliding bearing as the loading bearing housing, with a loading plate mounted on the drive shaft. A hydraulic cylinder applies axial force, pushing the thrust sliding bearing against the loading plate on the drive shaft, transmitting the axial force. Compared to rolling bearings, sliding bearings can withstand much greater axial forces. However, they have the disadvantage of being relatively bulky, and high thrust forces can lead to significant power losses in the thrust sliding bearing, increasing the overall power consumption of the drive system by megawatts.

[0005] Both of the above-mentioned axial force loading devices require additional systems such as hydraulic oil stations, lubricating oil stations, hydraulic cylinders, force sensors, and servo valves. In the case of using sliding bearings as loading bearings, the required lubricating oil station is larger in size. In order to ensure the uniformity of the loading force, the oil inlets of the two loading hydraulic cylinders need to be connected in parallel. However, when a hydraulic cylinder gets stuck, the loading bearing seat will be overloaded.

[0006] In summary, how to propose an axial force loading device to address the above technical issues has become an urgent problem to be solved by those skilled in the art. Summary of the Invention

[0007] In view of the above-mentioned deficiencies in the prior art, the present invention provides a pneumatic axial force loading device.

[0008] The technical solution of the present invention is: a pneumatic axial force loading device, comprising a loading plate, a barrel-shaped cover, a support seat, a plurality of auxiliary support legs and a plurality of sensor supports.

[0009] The support base is installed on the foundation through anchor bolts. Several auxiliary support legs and several sensor supports are installed on the support base in a circular array. A force sensor is installed on the sensor support, and the force sensor is offset from the barrel cover.

[0010] An annular end cover is installed at the open end of the barrel-shaped cover shell, two air supply seats are installed on the barrel-shaped cover shell, and the barrel-shaped cover shell is slidably connected with the auxiliary supporting legs.

[0011] The loading plate is coaxially fixed to the transmission shaft to be tested, and is coaxially arranged in the barrel-shaped cover. The loading plate can move along the axial direction of the barrel-shaped cover. The loading plate divides the inner cavity of the barrel-shaped cover into a first air cavity and a second air cavity, and the first air cavity is connected to the air supply seat.

[0012] Compared with the prior art, the present invention has the following effects:

[0013] 1. The present invention selects compressed air as the loading medium. Compared with hydraulic cylinder loading, compressed air is non-toxic, harmless, has no pollution to the environment, and is energy-saving and environmentally friendly.

[0014] 2. Compared with hydraulic cylinder loading, the present invention only needs to adjust the pressure of the air supply line to complete loading, and the loading efficiency is high. During hydraulic cylinder loading, the servo valve has high requirements on the oil quality. Before use, the entire loading oil circuit needs to be oiled, and then the oil needs to be tested for particle size. It can only be used after passing the test.

[0015] 3. Compared with hydraulic cylinder loading, the present invention has lower cost and is more convenient to operate; air loading only requires compressed air, while hydraulic cylinder loading requires hydraulic cylinders, hydraulic loading oil stations, lubricating oil stations, servo valves, filter elements, pipelines, etc.

[0016] 4. Compared with hydraulic cylinder loading, the present invention has no failure risk; since hydraulic loading involves multiple devices such as hydraulic cylinders and servo valves, there are risks such as failure of hydraulic cylinders and servo valves, which may cause the loaded bearing seat to suffer from overload failure.

[0017] 5. Compared with the rolling bearing loading bearing seat, the present invention selects a loading plate 2 that uses air pressure to achieve loading. The loading plate 2 is coaxially fixed with the tested transmission shaft 1 and rotates coaxially with the tested transmission shaft 1. There is no need for an additional test bearing as in the prior art, which avoids the axial force loading being restricted by the rotational speed of the test bearing.

[0018] 6. Compared with the bearing seat loaded by sliding bearings, the compressed air of the present invention has low viscosity, and the power loss under large load is much smaller than that of sliding bearings. The use of air loading can reduce the energy consumption of the entire drag system. Therefore, the advantage of using compressed air loading under the working condition of large axial force loading is very obvious. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 is an axonometric drawing of the present invention;

[0020] Figure 2 is a cross-sectional view of the present invention;

[0021] Figure 3 is a first cross-sectional view of the loading tray 2 of the present invention;

[0022] Figure 4 This is a first cross-sectional view of the loading plate 2, annular end cover 3, barrel-shaped housing 4 and air supply seat 9 of the present invention. The hollow arrows in the figure indicate the direction of compressed air flow, and the solid arrows indicate the direction of axial force and support reaction force;

[0023] Figure 5 is a second cross-sectional view of the loading tray 2 of the present invention;

[0024] Figure 6 This is a second cross-sectional view of the loading plate 2, annular end cover 3, barrel-shaped housing 4 and air supply seat 9 of the present invention. The hollow arrows in the figure indicate the direction of compressed air flow, and the solid arrows indicate the direction of axial force and support reaction force;

[0025] Figure 7 is an axonometric view of the auxiliary support leg 5 of the present invention;

[0026] Figure 8 Schematic diagram of the connection between the auxiliary support leg 5 and the support base 8 of the present invention;

[0027] Figure 9 It is a first axonometric view of the barrel-shaped housing 4 of the present invention;

[0028] Figure 10 is a second axonometric view of the barrel-shaped housing 4 of the present invention;

[0029] Figure 11 It is an axonometric view of the support seat 8 of the present invention.

[0030] In the figure: 1. Tested transmission shaft; 2. Loading disk; 201. First sleeve; 202. Disk body; 203. Second sleeve; 3. Annular end cover; 4. Barrel-shaped cover; 5. Auxiliary support leg; 501. First support plate; 502. Second support plate; 6. Force sensor; 7. Sensor support; 8. Support seat; 803. Load-bearing plate; 801. Base; 802. Rectangular frame; 9. Air supply seat; 11. Slider; 13. Sliding column; 14. Connecting beam; 15. Limiting plug. DETAILED DESCRIPTION

[0031] In order to make the purpose, features and advantages of the present invention more obvious and easy to understand, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention.

[0032] Specific implementation method 1: Combination Figures 1 to 11 This embodiment will be described. A pneumatic axial force loading device of this embodiment includes a loading plate 2 , a barrel-shaped cover 4 , a support seat 8 , a plurality of auxiliary support legs 5 and a plurality of sensor supports 7 .

[0033] The support base 8 is installed on the foundation through anchor bolts. Several auxiliary support legs 5 and several sensor supports 7 are installed on the support base 8 in a circular array. A force sensor 6 is installed on the sensor support 7, and the force sensor 6 is against the barrel cover 4.

[0034] An annular end cap 3 is mounted on the open end of the barrel-shaped casing 4. Preferably, the annular end cap 3 is bolted to the end surface of the barrel-shaped casing 4. Two air supply seats 9 are mounted on the barrel-shaped casing 4. Preferably, the air supply seats 9 are flange-jointed with the barrel-shaped casing 4 and bolted to the outer circumference of the barrel-shaped casing 4. The barrel-shaped casing 4 is slidably connected to the auxiliary support legs 5.

[0035] The loading disc 2 is coaxially fixed to the transmission shaft 1 to be tested, and the loading disc 2 is coaxially arranged in the barrel-shaped cover 4. The loading disc 2 can move along the axial direction of the barrel-shaped cover 4. The loading disc 2 divides the inner cavity of the barrel-shaped cover 4 into a first air cavity and a second air cavity. The first air cavity is connected to the air supply seat 9.

[0036] Specific implementation method 2: Combination Figure 1 、 Figure 3 and Figure 4 To describe this embodiment, the loading disk 2 includes a first sleeve 201 , a disk body 202 , and a second sleeve 203 that are integrally arranged in sequence.

[0037] Comb-teeth sealing rings 204 are installed on the outer circumferential surfaces of the first sleeve 201 and the disc body 202 . The first sleeve 201 is rotatably connected to the barrel bottom of the barrel-shaped cover shell 4 .

[0038] The barrel bottom of the barrel-shaped cover 4, the barrel body of the barrel-shaped cover 4 and the disc body 202 form a first air cavity, and the annular end cover 3, the barrel body of the barrel-shaped cover 4 and the disc body 202 form a second air cavity.

[0039] The annular end cap 3 is provided with a plurality of vent holes in a circumferential array. The inner diameter of the annular end cap 3 is larger than the outer diameter of the second sleeve 203. The second air cavity is connected to the atmosphere. This arrangement is for the following purposes:

[0040] Typically, the maximum pressure of an industrial air compressor is between 0.6 and 1.3 MPa. Therefore, when the bearing on the tested transmission shaft 1 bears a large axial load, compressed air between 0.6 and 1.3 MPa needs to be introduced into the first air cavity.

[0041] When the present invention is working, compressed air enters the first air chamber through the air supply seat 9.

[0042] Since the first sleeve 201 and the disc body 202 are equipped with a comb-tooth sealing ring 204, the compressed air forms a certain air pressure in the first air chamber; and because the barrel-shaped cover 4 is slidingly connected to the auxiliary support legs 5, and the loading disc 2 can move along the axial direction of the barrel-shaped cover 4, the air pressure pushes the loading disc 2 and the barrel-shaped cover 4 to move in two opposite directions respectively.

[0043] The force exerted by air pressure on the loading plate 2 is the axial force, which is applied to the bearing on the transmission shaft 1 under test through the loading plate 2. The force exerted by air pressure on the barrel-shaped cover 4 is the support reaction force. Since the force sensor 6 and the barrel-shaped cover 4 are offset, the support reaction force is measured by the force sensor 6. The support reaction force is equal in magnitude and opposite in direction to the axial force, so the magnitude of the applied axial force can be indirectly judged by measuring the support reaction force.

[0044] The compressed air slowly leaks into the atmosphere and the second air cavity through the two grate sealing rings 204. After the second air cavity is connected to the atmosphere, the internal air pressure is equal to that of the atmosphere, and the axial force is fully applied to the measured transmission shaft 1, preventing the stored air pressure in the second air cavity from hindering the movement of the loading disk 2, thereby causing the resultant axial force to become smaller.

[0045] Other components and connection relationships are the same as those in the first embodiment.

[0046] Specific implementation method three: Combination Figure 5 and Figure 6 To describe this embodiment, the loading disk 2 includes a first sleeve 201 , a disk body 202 , and a second sleeve 203 that are integrally arranged in sequence.

[0047] Comb-teeth sealing rings 204 are installed on the outer circumferential surfaces of the first sleeve 201 , the disc body 202 and the second sleeve 203 . The first sleeve 201 is rotatably connected to the barrel bottom of the barrel-shaped cover 4 , and the second sleeve 203 is rotatably connected to the annular end cover 3 .

[0048] The bottom of the barrel-shaped cover 4, the barrel body of the barrel-shaped cover 4 and the disc 202 form a first air cavity, and the annular end cover 3, the barrel body of the barrel-shaped cover 4 and the disc 202 form a second air cavity. The purpose of such arrangement is:

[0049] When the bearing on the tested transmission shaft 1 is under a relatively small axial load, compressed air with a pressure of less than 0.6 MPa needs to be introduced into the first air cavity. The compressed air enters the first air cavity through the air supply seat 9 and forms a certain air pressure in the first air cavity. The force exerted by the air pressure on the loading disk 2 is the axial force.

[0050] The compressed air slowly leaks to the atmosphere and the second air cavity through the first sleeve 201 and the grate sealing ring 204 on the disc body 202, and then the air pressure in the second air cavity slowly releases to the atmosphere from the grate sealing ring 204 on the second sleeve 203, thereby causing a pressure difference between the first air cavity and the second air cavity. Therefore, a reverse axial force is generated in the second air cavity to hinder the movement of the loading disc 2, thereby achieving the goal that the axial force cannot be fully applied to the measuring transmission shaft 1, so as to facilitate accurate control of the load acting on the measured transmission shaft 1, avoid the need to manufacture devices of different sizes under different working loads, and achieve the above functions by re-equipping the loading disc 2 and the annular end cover 3, thereby saving costs.

[0051] Other components and connection relationships are the same as those in the first or second embodiment.

[0052] Specific implementation method four: Combination Figure 3 and Figure 5 In this embodiment, the longitudinal cross-section of the plate body 202 is trapezoidal. This design is based on the theory of equal strength. Since the loading plate 2 is a load-bearing component during operation, the base of the plate body 202 experiences the greatest bending moment when subjected to axial force. Therefore, the longitudinal cross-section of the plate body 202 is designed to be trapezoidal according to the theory of equal strength to ensure the service life of the loading plate 2. The remaining components and connections are the same as those of the first, second, or third embodiments.

[0053] Specific implementation method five: Combination Figure 1 、 Figure 7 and Figure 8 To illustrate this embodiment, the auxiliary support leg 5 in this embodiment is a special-shaped member, and the support leg 5 includes a first support plate 501 , a second support plate 502 , a sliding column 13 and a connecting beam 14 .

[0054] The first support plate 501 and the second support plate 502 are fixed to two ends of the connecting beam 14 , respectively, and the second support plate 502 is fixed to the support base 8 .

[0055] Both ends of the sliding column 13 are respectively inserted into the first support plate 501 and the second support plate 502 , and the first support plate 501 and the second support plate 502 are both installed with a limit blocking cover 15 , which abuts against the end surface of the sliding column 13 .

[0056] Other components and connection relationships are the same as those in the first, second, third or fourth embodiment.

[0057] Specific implementation method six: combination Figure 1 and Figure 9 To describe this embodiment, in this embodiment, a number of sliding ear plates are fixedly connected to the outer circumferential surface of the barrel-shaped cover shell 4 in a circumferential array. The barrel-shaped cover shell 4 is slidably connected to the auxiliary support leg 5 through the sliding ear plates. Preferably, a notch with a C-shaped cross-section is opened on the sliding ear plate, and the notch slides with the sliding column 13. With this arrangement, the sliding ear plate has a strong bearing capacity and can realize the sliding of the barrel-shaped cover shell 4 along the length direction of the sliding column 13, which is conducive to ensuring that the barrel-shaped cover shell 4 slides freely on the auxiliary support leg 5.

[0058] Other components and connection relationships are the same as those in the first, second, third, fourth or fifth embodiment.

[0059] Specific implementation method seven: combination Figure 1 、 Figure 8 and Figure 10 To illustrate this embodiment, in this embodiment, a plurality of sliding ear plates are fixedly connected to the outer circumferential surface of the barrel-shaped cover 4 in a circumferential array. The sliding ear plates are provided with through holes, and a slider 11 is installed in the through holes. The slider 11 is slidably connected to the slide post 13.

[0060] Furthermore, the slider 11 can be a ball slider or a graphite copper sleeve. Preferably, when the barrel-shaped housing 4 is small and lightweight, a ball slider with low friction is selected. When the barrel-shaped housing 4 is large and heavy, a graphite copper sleeve with high load-bearing capacity and self-lubricating properties is selected.

[0061] Furthermore, the slider 11 is axially limited in the through hole by an elastic retaining ring; with this arrangement, the slider 11 and the slide column 13 form a linear bearing structure, which reduces the friction between the barrel-shaped cover 4 and the auxiliary support leg 5, avoiding the influence of friction on the magnitude of the axial force.

[0062] Other components and connection relationships are the same as those in the first, second, third, fourth, fifth or sixth embodiment.

[0063] Specific implementation method eight: combination Figure 4 and Figure 6 To describe this embodiment, an annular groove is opened on the inner circumference of the barrel-shaped cover shell 4 in this embodiment, and a wear-resistant layer is provided in the annular groove by centrifugal casting or spraying. Preferably, the wear-resistant layer is made of a soft alloy material or polyphenylene ester material.

[0064] Other components and connection relationships are the same as those in the first, second, third, fourth, fifth, sixth or seventh embodiment.

[0065] Specific implementation method nine: combination Figure 1 and Figure 11 To describe this embodiment, the support base 8 includes a base 801 and a rectangular frame 802 .

[0066] The base 801 is installed on the foundation through anchor bolts, and the rectangular frame 802 is vertically fixed to the base 801. A load-bearing plate 803 is fixed to the rectangular frame 802. The auxiliary support legs 5 and the sensor holder 7 are both fixed to the load-bearing plate 803.

[0067] Furthermore, in order to improve the positioning accuracy of the auxiliary support leg 5 on the support seat 8, a boss is integrally provided on the end face of the second support plate 502, and the boss is coaxially arranged with the sliding column 13. A positioning hole is opened on the load-bearing plate 803, and the boss is inserted into the positioning hole, and the second support plate 502 and the load-bearing plate 803 are connected by bolts.

[0068] Furthermore, a rib plate is fixedly connected to the support seat 8, and the rib plate and the auxiliary support legs 5 are respectively arranged on two side surfaces of the load-bearing plate 803. The rib plate provides support for the load-bearing plate 803 to withstand the support reaction force generated by the cover shell.

[0069] Other components and connection relationships are the same as those in the first, second, third, fourth, fifth, sixth, seventh or eighth embodiments.

[0070] How it works

[0071] Combine Figures 1 to 11 The working principle of the present invention is described:

[0072] The present invention is used in conjunction with an air compressor. When the present invention is working, the loading disc 2 is coaxially fixed to the transmission shaft 1 to be measured and coaxially rotates with the transmission shaft 1 to be measured.

[0073] The loading tray 2 is coaxially arranged in the barrel-shaped housing 4 , and the loading tray 2 divides the inner cavity of the barrel-shaped housing 4 into a first air cavity and a second air cavity.

[0074] When the bearing on the tested transmission shaft 1 bears a large axial load, compressed air with a pressure of 0.6 to 1.3 MPa needs to be introduced into the first air cavity. The compressed air enters the first air cavity through the air supply seat 9 .

[0075] Since the first sleeve 201 and the disc body 202 are equipped with a comb-tooth sealing ring 204, the compressed air forms a certain air pressure in the first air chamber; and because the barrel-shaped cover 4 is slidingly connected to the auxiliary support legs 5, and the loading disc 2 can move along the axial direction of the barrel-shaped cover 4, the air pressure pushes the loading disc 2 and the barrel-shaped cover 4 to move in two opposite directions respectively.

[0076] The force exerted by air pressure on the loading plate 2 is the axial force, which is applied to the bearing on the transmission shaft 1 under test through the loading plate 2. The force exerted by air pressure on the barrel-shaped cover 4 is the support reaction force. Since the force sensor 6 and the barrel-shaped cover 4 are offset, the support reaction force is measured by the force sensor 6. The support reaction force is equal in magnitude and opposite in direction to the axial force, so the magnitude of the applied axial force can be indirectly judged by measuring the support reaction force.

[0077] The compressed air slowly leaks into the atmosphere and the second air cavity through the two grate sealing rings 204. After the second air cavity is connected to the atmosphere, the internal air pressure is equal to that of the atmosphere, and the axial force is fully applied to the measured transmission shaft 1, preventing the stored air pressure in the second air cavity from hindering the movement of the loading disk 2, thereby causing the resultant axial force to become smaller.

[0078] When the bearing on the tested transmission shaft 1 is under a relatively small axial load, compressed air with a pressure of less than 0.6 MPa needs to be introduced into the first air cavity. The compressed air enters the first air cavity through the air supply seat 9 and forms a certain air pressure in the first air cavity. The force exerted by the air pressure on the loading disk 2 is the axial force.

[0079] The compressed air slowly leaks to the atmosphere and the second air cavity through the first sleeve 201 and the grate sealing ring 204 on the disc body 202, and then the air pressure in the second air cavity slowly releases to the atmosphere from the grate sealing ring 204 on the second sleeve 203, thereby causing a pressure difference between the first air cavity and the second air cavity. Therefore, a reverse axial force is generated in the second air cavity to hinder the movement of the loading disc 2, thereby achieving the goal that the axial force cannot be fully applied to the measured transmission shaft 1, so as to facilitate accurate control of the load acting on the measured transmission shaft 1, avoid the need to manufacture devices of different sizes under different working loads, and achieve the above-mentioned function by re-equipping the loading disc 2 and the annular end cover 3, thereby saving costs.

[0080] The present invention has been disclosed as above in terms of preferred embodiments, but this is not intended to limit the present invention. Any simple modifications, equivalent changes, and modifications made to the above implementation cases by any person skilled in the art without departing from the content of the technical solution of the present invention based on the technical essence of the present invention are still within the scope of the technical solution of the present invention.

Claims

1. A pneumatic axial force loading device, characterized in that: It comprises a loading plate (2), a barrel-shaped cover (4), a support base (8), a plurality of auxiliary support legs (5) and a plurality of sensor supports (7); The support base (8) is mounted on the foundation through anchor bolts, and a plurality of auxiliary support legs (5) and a plurality of sensor supports (7) are mounted on the support base (8) in a circular array. A force sensor (6) is mounted on the sensor support (7), and the force sensor (6) is abutted against the barrel-shaped cover (4); An annular end cover (3) is installed at the open end of the barrel-shaped cover (4), two air supply seats (9) are installed on the barrel-shaped cover (4), and the barrel-shaped cover (4) is slidably connected to the auxiliary support legs (5); A plurality of sliding lugs are fixedly connected to the outer circumferential surface of the barrel-shaped cover shell (4) in a circumferential array, and the barrel-shaped cover shell (4) is slidably connected to the auxiliary support legs (5) via the sliding lugs; The loading disc (2) is coaxially fixed to the transmission shaft (1) to be tested, the loading disc (2) is coaxially arranged in the barrel-shaped cover (4), and the loading disc (2) is movable along the axis direction of the barrel-shaped cover (4), and the loading disc (2) divides the inner cavity of the barrel-shaped cover (4) into a first air cavity and a second air cavity, and the first air cavity is communicated with the air supply seat (9); The loading disc (2) comprises a first sleeve (201), a disc body (202), and a second sleeve (203) which are integrally arranged in sequence; The longitudinal section of the disc body (202) is trapezoidal, and the outer circumferential surfaces of the first sleeve (201) and the disc body (202) are both provided with a grate seal ring (204), and the first sleeve (201) is rotatably connected to the barrel bottom of the barrel-shaped cover shell (4); The barrel bottom of the barrel-shaped cover (4), the barrel body of the barrel-shaped cover (4) and the disc body (202) form a first air cavity, and the annular end cover (3), the barrel body of the barrel-shaped cover (4) and the disc body (202) form a second air cavity; A plurality of vent holes are formed on the annular end cover (3) in a circumferential array, and the inner diameter of the annular end cover (3) is larger than the outer diameter of the second sleeve (203); The auxiliary support leg (5) comprises a first support plate (501), a second support plate (502), a sliding column (13) and a connecting beam (14); The first support plate (501) and the second support plate (502) are respectively fixed to two ends of the connecting beam (14), and the second support plate (502) is fixed to the support seat (8); The two ends of the sliding column (13) are respectively inserted into the first support plate (501) and the second support plate (502), and the first support plate (501) and the second support plate (502) are both installed with a limit blocking cover (15), and the limit blocking cover (15) is against the end surface of the sliding column (13).

2. The pneumatic axial force loading device according to claim 1, characterized in that: The loading disc (2) comprises a first sleeve (201), a disc body (202), and a second sleeve (203) which are integrally arranged in sequence; Grate seal rings (204) are installed on the outer circumferential surfaces of the first sleeve (201), the disc body (202), and the second sleeve (203); the first sleeve (201) is rotatably connected to the barrel bottom of the barrel-shaped cover (4); and the second sleeve (203) is rotatably connected to the annular end cover (3); The barrel bottom of the barrel-shaped cover (4), the barrel body of the barrel-shaped cover (4), and the disc body (202) form a first air cavity, and the annular end cover (3), the barrel body of the barrel-shaped cover (4), and the disc body (202) form a second air cavity.

3. The pneumatic axial force loading device according to claim 1, characterized in that: A plurality of sliding ear plates are fixedly connected to the outer circumferential surface of the barrel-shaped cover shell (4) in a circumferential array. The sliding ear plates are provided with through holes, and a sliding block (11) is installed in the through holes. The sliding block (11) is slidably connected to the sliding column (13).

4. The pneumatic axial force loading device according to claim 1, characterized in that: An annular groove is formed on the inner circumferential surface of the barrel-shaped cover shell (4), and a wear-resistant layer is provided in the annular groove by centrifugal casting or spraying.

5. The pneumatic axial force loading device according to claim 1, characterized in that: The support base (8) comprises a base (801) and a rectangular frame (802); The base (801) is installed on the foundation through anchor bolts, the rectangular frame (802) is vertically fixed to the base (801), a load-bearing plate (803) is fixed to the rectangular frame (802), and the auxiliary support legs (5) and the sensor support (7) are both fixed to the load-bearing plate (803).

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