Pump shaft simulation load bounce detection system with state conversion

Abstract

The invention discloses a state transition pump shaft simulation load run-out detection system which comprises a pump, a dial indicator and a pull and push dynamometer. The pump shaft is provided with a driving disc and a stress disc, and the driving disc, the pump shaft and the stress disc are located on the same central axis. The dial indicator can be selectively configured in a radial run-out detection state by adjusting the position of the dial indicator and the direction of a measuring head, wherein the measuring head is perpendicular to the central axis and abuts against the outer circumferential surface of the pump shaft; in the axial run-out detection state, the measuring head is overlapped or parallel to the central axis and abuts against the axial end face of the pump shaft; the push-pull dynamometer can be selectively configured in a radial force application state by adjusting the position of the push-pull dynamometer and the direction of a force application end, wherein the force application end is perpendicular to the central axis and abuts against the outer circumferential surface of the stress disc, and a radial simulation load is applied; in the axial force application state, the force application end is parallel to the central axis and abuts against the disc end face of the stress disc, and an axial simulation load is applied. Through the state conversion of the same detection and force application device, the radial and axial runout integrated detection of the pump shaft under the simulated load is realized.

Description

Technical Field

[0001] The invention belongs to the technical field of pump shaft beat detection, and in particular relates to a state-transition pump shaft simulated load beat detection system. Background Art

[0002] Traditional methods for detecting pump shaft runout require separate radial and axial dial indicators, resulting in redundant equipment and cumbersome operation. Furthermore, existing technologies are unable to simulate actual operating conditions under dynamic loads: conventional methods estimate load effects after static testing, resulting in high data deviations. Furthermore, mechanically driven rotating mechanisms (such as gear motors) inevitably introduce vibration interference, obscuring the true runout value; and manually adjusting the test orientation introduces positioning errors, further reducing the reliability of the test results. Summary of the Invention

[0003] Purpose of the invention: In order to overcome the deficiencies in the prior art, the present invention provides a state-transition pump shaft simulated load runout detection system. By state transition of the same detection and force-applying device, integrated detection of radial and axial runout of the pump shaft under simulated load is achieved, thereby improving the comprehensiveness and accuracy of pump shaft runout detection.

[0004] Technical Solution: To achieve the above-mentioned purpose, the present invention provides a state-transition pump shaft simulated load runout detection system for detecting the runout of the pump shaft under simulated load, comprising:

[0005] A pump, wherein a driving disc and a force-bearing disc are fixedly arranged on the pump shaft in sequence along the axial direction, wherein the driving disc, the pump shaft and the force-bearing disc are on the same central axis;

[0006] A dial indicator that can be selectively configured to:

[0007] Radial runout detection state: the probe is perpendicular to the central axis and abuts against the outer circumferential surface of the pump shaft;

[0008] Axial runout detection state: the probe overlaps or is parallel to the central axis and abuts against the axial end face of the pump shaft;

[0009] and a push-pull force gauge, which can be selectively configured as follows by adjusting its position and direction of the force-applying end:

[0010] Radial force application state: the force application end is perpendicular to the central axis and abuts against the outer circumferential surface of the force-bearing disc to apply a radial simulated load;

[0011] Axial force application state: the force application end is parallel to the central axis and abuts against the end surface of the force-bearing disk to apply an axial simulated load.

[0012] Furthermore, the axial runout detection state includes an axial movement detection state and an end face runout detection state, wherein:

[0013] Axial movement detection state: the probe overlaps the central axis and abuts against the center of the axial end face of the pump shaft;

[0014] End face runout detection state: the probe is parallel to the central axis and rests against the edge of the axial end face of the pump shaft.

[0015] Furthermore, it includes a dial indicator feeding mechanism and a dial indicator position conversion adjustment mechanism, wherein the dial indicator is arranged on the dial indicator position conversion adjustment mechanism through the dial indicator feeding mechanism;

[0016] The dial indicator position conversion adjustment mechanism drives the dial indicator to move between the orientation of the probe perpendicular to the central axis and the orientation of the probe overlapping or parallel to the central axis to perform position conversion. The dial indicator feed mechanism drives the dial indicator to move toward the pump shaft so that the probe abuts the outer circumferential surface or axial end face of the pump shaft, thereby realizing the detection state switching between the radial runout detection state and the axial runout detection state.

[0017] Furthermore, the dial indicator position conversion adjustment mechanism includes a first circular arc guide rail and a linear guide rail, and the dial indicator feed mechanism is arranged on the first circular arc guide rail through the linear guide rail; the arc bending direction of the first circular arc guide rail is downward and toward the pump shaft, and the tangent line of the high point position at the end of the stroke is parallel to the central axis, and the tangent line of the low point position at the end of the stroke is perpendicular to the central axis, so as to provide a driving force for the dial indicator to move between the orientation of the probe perpendicular to the central axis and the orientation of the probe overlapping or parallel to the central axis for position conversion; the linear guide rail It is arranged along the tangential direction of the first circular arc guide rail, and provides a driving force for the dial indicator to move between the orientation of the overlapping central axis of the probe and the orientation of the parallel central axis of the probe to perform position conversion, thereby realizing the switching of the detection state between the axial movement detection state and the end face runout detection state in the axial runout detection state; the dial indicator feed mechanism and the dial indicator are both arranged along the radial direction of the first circular arc guide rail, and the dial indicator feed mechanism drives the dial indicator to move along the radial direction of the first circular arc guide rail, thereby realizing the abutment of the probe against the outer circumferential surface or axial end face of the pump shaft.

[0018] Furthermore, it includes a push-pull force gauge feeding mechanism and a push-pull force gauge position conversion adjustment mechanism, wherein the push-pull force gauge is arranged on the push-pull force gauge position conversion adjustment mechanism through the push-pull force gauge feeding mechanism;

[0019] The push-pull force gauge position conversion adjustment mechanism drives the push-pull force gauge to move between the orientation of the force-applying end perpendicular to the central axis and the orientation of the force-applying end parallel to the central axis for position conversion, and the push-pull force gauge feeding mechanism drives the push-pull force gauge to move toward the force disk so that the force-applying end rests against the outer circumferential surface or the end face of the force disk.

[0020] Furthermore, the push-pull force gauge position conversion adjustment mechanism includes a second circular arc guide rail, and the push-pull force gauge feed mechanism is arranged on the second circular arc guide rail; the arc bending direction of the second circular arc guide rail is upward and toward the pump shaft, and the tangent of the low point position at the end of the stroke is parallel to the central axis, and the tangent of the high point position at the end of the stroke is perpendicular to the central axis, so as to provide a driving force for the push-pull force gauge to move between the orientation of the force-applying end perpendicular to the central axis and the orientation of the force-applying end parallel to the central axis for position conversion; the push-pull force gauge feed mechanism and the push-pull force gauge are both arranged along the radial direction of the second circular arc guide rail, and the push-pull force gauge feed mechanism drives the push-pull force gauge to move along the radial direction of the second circular arc guide rail, so as to realize the abutment of the force-applying end against the outer circumferential surface or axial end face of the force-bearing disk to apply an axial simulated load or a radial simulated load.

[0021] Furthermore, the probe of the dial indicator is provided with a first ball head that is in rolling contact with the pump shaft; the force-applying end of the push-pull dynamometer is provided with a second ball head that is in rolling contact with the force-bearing disk.

[0022] Furthermore, the driving disk is an air-driven rotating disk with a hollow interior and an array of air holes evenly distributed on the outer circumference. The axis of the air holes and the tangent of the driving disk where the holes are located have an acute angle. The driving disk rotates by the reverse thrust generated by the jets ejected from the air holes, and the driving disk drives the pump shaft and the force-bearing disk to rotate synchronously.

[0023] Furthermore, the air inlet of the driving disk is located at the center of the disk, and the inner cavity disk surface of the driving disk facing the air inlet is a discharge cone surface that guides the input gas from the center to the surroundings to achieve force release.

[0024] Furthermore, the air inlet of the driving disk is connected to a rotary joint, a straight-through movable tube, an air supply flexible tube and an air supply source; a bracket is provided at the position of the straight-through movable tube, and a movable seat with an embedded guide tube is elastically suspended in the bracket by an elastic part, and the straight-through movable tube coaxially slides through the guide tube, so that the straight-through movable tube is in a suspended movable state connected between the air supply flexible tube and the rotary joint.

[0025] Beneficial effect: The present invention can realize integrated detection of radial and axial runout of the pump shaft under simulated load through the state conversion of the same detection and force-applying device, that is, the state switching of the dial indicator and the push-pull force gauge. The dial indicator digitally displays the runout value, and the push-pull force gauge applies the load to simulate the radial and axial runout detection of the pump shaft under multiple working conditions, thereby improving the comprehensiveness of pump shaft runout detection, reducing equipment switching, improving detection efficiency, and ensuring dynamic matching of load and detection state. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] Figure 1 It is a schematic diagram of the overall structure of the present invention,

[0027] Figure 2 It is an enlarged schematic diagram of the structures of the dial indicator feeding mechanism, the dial indicator position conversion adjustment mechanism, the push-pull force gauge feeding mechanism, and the push-pull force gauge position conversion adjustment mechanism;

[0028] Figure 3 It is a structural diagram of the radial runout detection state under radial force application state;

[0029] Figure 4 It is a structural diagram of an axial movement detection state belonging to an axial runout detection state under an axial force application state;

[0030] Figure 5 It is a structural schematic diagram of the end face runout detection state belonging to the axial runout detection state under the axial force application state;

[0031] Figure 6 A schematic diagram of the half-section structure of the drive disc Figure 1 ;

[0032] Figure 7 A schematic diagram of the half-section structure of the drive disc Figure 2 . DETAILED DESCRIPTION

[0033] The present invention will be further described below with reference to the accompanying drawings.

[0034] like Figure 1 As shown, a state-transition pump shaft simulated load jump detection system is used to detect the jump of the pump shaft 10 under a simulated load, including:

[0035] The pump 1 has a pump shaft 10 with a driving disc 2 and a force-bearing disc 3 fixedly arranged in sequence along the axial direction. The driving disc 2, the pump shaft 10 and the force-bearing disc 3 are located on the same central axis 11.

[0036] The dial indicator 4 can be selectively configured as follows by adjusting its position and probe direction:

[0037] Radial runout detection state: the probe is perpendicular to the central axis 11 and abuts against the outer circumferential surface of the pump shaft 10;

[0038] Axial runout detection state: the probe overlaps or is parallel to the central axis 11 and abuts against the axial end face of the pump shaft 10;

[0039] and a push-pull force gauge 5, which can be selectively configured as follows by adjusting its position and the direction of the force-applying end:

[0040] Radial force application state: the force application end is perpendicular to the central axis 11 and abuts against the outer circumferential surface of the force-bearing disc 3 to apply a radial simulated load;

[0041] Axial force application state: the force application end is parallel to the central axis 11 and rests against the end face of the force disc 3 to apply an axial simulated load. The present invention can realize the integrated detection of radial and axial runout of the pump shaft under simulated load through the state conversion of the same detection and force application device, that is, the state switching of the dial indicator 4 and the push-pull force gauge 5. The dial indicator 4 digitally displays the runout value, and the push-pull force gauge 5 applies the load to simulate the radial and axial runout detection of the pump shaft under multiple working conditions, thereby improving the comprehensiveness of the pump shaft runout detection. A single system can detect the full-dimensional radial and axial runout of the pump shaft 10 under simulated load, reducing equipment switching and improving detection efficiency. The push-pull force gauge 5 applies a controllable load to truly reflect the working state of the pump shaft and ensure dynamic matching of the load and detection state.

[0042] It is worth noting that the axial runout of the pump shaft 10 is further subdivided into axial runout and end face runout. In order to further ensure the comprehensiveness and efficiency of the pump shaft runout detection of the present invention, in the present invention, the axial runout detection state includes the axial runout detection state and the end face runout detection state, wherein:

[0043] Axial movement detection state: the probe overlaps with the central axis 11 and abuts against the center of the axial end face of the pump shaft 10. Affected by the structure of the shaft end face, the deviation in the center position is small and the detection is more accurate.

[0044] End face runout detection status: The probe is parallel to the central axis 11 and against the edge of the axial end face of the pump shaft 10. Since the axis of the pump shaft 10 has produced a non-collinear effect with the central axis 11 when end face runout occurs, when performing end face runout detection, the actual situation is that the end face runout amplitude at the center position of the pump shaft end face is too small, resulting in inaccuracy, while the end face runout amplitude at the edge position of the pump shaft end face is too large, which can more intuitively and accurately reflect the end face runout detection value. Splitting the axial runout into axial movement (probe against the axis center) and end face runout (probe against the edge) solves the differentiated detection needs of axial deformation and can accurately distinguish between the overall offset and local warping of the pump shaft end face.

[0045] like Figure 1 and Figure 2 As shown, the present invention includes a dial indicator feeding mechanism 6 and a dial indicator position conversion adjustment mechanism 7, wherein the dial indicator 4 is arranged on the dial indicator position conversion adjustment mechanism 7 through the dial indicator feeding mechanism 6; the dial indicator position conversion adjustment mechanism 7 drives the dial indicator 4 to move between the orientation of the probe perpendicular to the central axis 11 and the orientation of the probe overlapping or parallel to the central axis 11 to convert the position, and the dial indicator feeding mechanism 6 drives the dial indicator 4 to move toward the pump shaft 10 so that the probe abuts against the outer circumferential surface or axial end face of the pump shaft 10, thereby realizing the detection state switching between the radial runout detection state and the axial runout detection state. More specifically, as Figure 2 and Figure 3 As shown, the dial indicator position conversion adjustment mechanism 7 includes a first circular arc guide rail 71 and a linear guide rail 72, and the dial indicator feed mechanism 6 is set on the first circular arc guide rail 71 through the linear guide rail 72; the arc bending direction of the first circular arc guide rail 71 is downward and toward the pump shaft 10, and the tangent of the high point position at the end of the stroke is parallel to the central axis 11, and the tangent of the low point position at the end of the stroke is perpendicular to the central axis 11, so as to provide a driving force for the dial indicator 4 to move between the orientation of the probe perpendicular to the central axis 11 and the orientation of the probe overlapping or parallel to the central axis 11 for position conversion; the linear The linear guide rail 72 is arranged along the tangent direction of the first circular arc guide rail 71, and provides a driving force for the dial indicator 4 to move between the orientation of the probe overlapping the central axis and the orientation of the probe parallel to the central axis for position conversion, thereby realizing the detection state switching between the axial movement detection state and the end face runout detection state in the axial runout detection state; the dial indicator feed mechanism 6 and the dial indicator 4 are both arranged along the radial direction of the first circular arc guide rail 71, and the dial indicator feed mechanism 6 drives the dial indicator 4 to move along the radial direction of the first circular arc guide rail 71 to realize the contact of the probe with the outer circumferential surface or axial end face of the pump shaft 10. The guide rail track forcibly constrains the probe orientation, realizing mechanical automatic positioning, thereby avoiding manual adjustment errors; in addition, through the cooperation of the first circular arc guide rail 71 and the linear guide rail 72, it has a two-stage conversion capability, the first stage is: the first circular arc guide rail 71 switches between radial and axial detection modes, and the second stage is the linear guide rail 72 switches between axial movement and end face runout detection points.

[0046] like Figure 1 and Figure 2 As shown, it includes a push-pull force gauge feeding mechanism 8 and a push-pull force gauge position conversion adjustment mechanism 9. The push-pull force gauge 5 is set on the push-pull force gauge position conversion adjustment mechanism 9 through the push-pull force gauge feeding mechanism 8; the push-pull force gauge position conversion adjustment mechanism 9 drives the push-pull force gauge 5 to move between the position where the force-applying end is perpendicular to the central axis 11 and the position where the force-applying end is parallel to the central axis 11 to convert the position. The push-pull force gauge feeding mechanism 8 drives the push-pull force gauge 5 to move toward the force-bearing disk 3 so that the force-applying end abuts against the outer circumferential surface or disk end surface of the force-bearing disk 3. More specifically, as Figure 2 and Figure 3As shown, the push-pull force gauge position conversion adjustment mechanism 9 includes a second circular arc guide rail 91, and the push-pull force gauge feeding mechanism 8 is arranged on the second circular arc guide rail 91; the arc bending direction of the second circular arc guide rail 91 is upward and toward the pump shaft 10, and the tangent of the low point position at the end of the stroke is parallel to the central axis 11, and the tangent of the high point position at the end of the stroke is perpendicular to the central axis 11, so as to provide a driving force for the push-pull force gauge 5 to move between the orientation of the force-applying end perpendicular to the central axis 11 and the orientation of the force-applying end parallel to the central axis 11 for position conversion; the push-pull force gauge feeding mechanism 8 and the push-pull force gauge 5 are both arranged along the radial direction of the second circular arc guide rail 91, and the push-pull force gauge feeding mechanism 8 drives the push-pull force gauge 5 to move along the radial direction of the second circular arc guide rail 91, so as to realize the abutment of the force-applying end against the outer circumferential surface or axial end face of the force-bearing disk 3, so as to apply an axial simulated load or a radial simulated load. The second arc-shaped guide rail 91 ensures the accuracy of the radial and axial force directions. The second arc-shaped guide rail 91 and the first arc-shaped guide rail 71 driving the dial indicator 4 are arranged in the opposite direction to avoid movement interference.

[0047] In the present invention, the entire system is set on the base 16, and the pump frame 17 and the guide rail frame 15 are installed on the base 16. The pump 1 is installed on the pump frame 17, and the first arc-shaped guide rail 71 and the second arc-shaped guide rail 91 are both installed on the guide rail frame 15. The dial indicator feed mechanism 6 is preferably a cylinder. The first arc-shaped guide rail 71, the linear guide rail 72, the push-pull force gauge feed mechanism 8 and the second arc-shaped guide rail 91 are all electric guide rails, and in order to ensure the accuracy of the force load, the push-pull force gauge feed mechanism 8 adopts a linear electric guide rail. Figure 2 and Figure 3 As shown, the probe of the dial indicator 4 is equipped with a first ball head 40 that rolls with the pump shaft 10; the force-applying end of the push-pull dynamometer 5 is equipped with a second ball head 50 that rolls with the force-bearing plate 3. The ball heads can reduce friction errors, and the rolling contact reduces the interference of sliding friction on the runout data. It also prevents the probe and the force-applying end from scratching the pump shaft 10 and the force-bearing plate 3.

[0048] In the present invention, Figures 3 and 4 to Figure 5 The three embodiments are briefly described in the order of the figures, and the working principles of the three embodiments are as follows:

[0049] Figure 3This is an embodiment of radial runout detection under radial force application: at this time, the dial indicator 4 is located at the highest point of the end of the stroke of the first arc-shaped guide rail 71, and the dial indicator feed mechanism 6 drives the dial indicator 4 to move toward the pump shaft 10, and the probe is fed downward perpendicular to the central axis 11 until the first ball head 40 contacts the outer circumferential surface of the pump shaft 10. At the same time, the push-pull dynamometer 5 is located at the lowest point of the end of the stroke of the second arc-shaped guide rail 91, and the push-pull dynamometer feed mechanism 8 drives the push-pull dynamometer 5 to move toward the pump shaft 10, and the force application end is fed upward perpendicular to the central axis 11 until the second ball head 50 contacts the outer circumferential surface of the force disk 3, applying a radial simulated load. Next, the size of the radial simulated load can be adjusted by the push-pull dynamometer 5 to realize the radial runout detection operation.

[0050] Figure 4 This is an embodiment of the axial movement detection state belonging to the axial runout detection state under the axial force application state: at this time, the dial indicator 4 is driven by the first arc-shaped guide rail 71 to move from the high point position at the end of the stroke to the low point position at the end of the stroke, and the dial indicator feed mechanism 6 drives the dial indicator 4 to move toward the pump shaft 10, and the probe is fed along a path overlapping with the center axis 11 until the first ball head 40 contacts the center of the axial end face of the pump shaft 10. At the same time, the push-pull dynamometer 5 is driven by the second arc-shaped guide rail 91 to move from the low point position at the end of the stroke to the high point position at the end of the stroke, and the push-pull dynamometer feed mechanism 8 drives the push-pull dynamometer 5 to move toward the pump shaft 10, and the force application end is fed along a path parallel to the center axis 11 until the second ball head 50 contacts the disk end face of the force disk 3 to apply an axial simulated load. Next, the size of the radial simulated load can be adjusted by the push-pull dynamometer 5 to perform the axial movement detection operation.

[0051] Figure 5 This is an embodiment of the end face runout detection state belonging to the axial runout detection state under the axial force application state: at this time, the dial indicator 4 is driven by the linear guide rail 72 and moves vertically upward, thereby adjusting from the center position of the pump shaft 10 to the edge position. When it reaches the edge position of the pump shaft 10, the dial indicator feed mechanism 6 drives the dial indicator 4 to move toward the pump shaft 10, so that the probe is fed along a path parallel to the central axis 11 until the first ball head 40 contacts the edge of the axial end face of the pump shaft 10, applying an axial simulated load. Next, the size of the radial simulated load can be adjusted by the push-pull dynamometer 5 to perform the end face runout detection operation.

[0052] It should be noted that in the prior art, when a mechanically driven rotating mechanism (such as a gear motor drive) is used to drive the pump shaft 10 to rotate for runout detection, vibration interference is inevitably introduced, which masks the true runout value and causes a large error in the runout detection result. Figure 1 and Figure 6As shown, the driving disk 2 is an air-driven rotating disk with a hollow interior and air holes 20 evenly distributed in an array on the outer circumference. The axis of the air holes 20 and the tangent of the driving disk 2 where the holes are located have an acute angle of 30 to 60 degrees. The driving disk 2 rotates due to the reverse thrust generated by the jets from the air holes 20, and the driving disk 2 drives the pump shaft 10 and the force disk 3 to rotate synchronously. The air-driven rotation replaces the motor-driven rotation. The pneumatic drive can completely eliminate the interference of the motor vibration on the runout detection, thereby reducing the runout detection error. At the same time, as Figure 7 As shown, the air inlet 21 of the driving disc 2 is located at the center of the disc. In order to reduce the axial vibration caused by the impact of the air flow, the inner disc surface of the driving disc 2 facing the air inlet 21 is a discharge cone surface 22 that guides the input gas from the center to the surrounding areas to achieve force release, thereby reducing the interference of the air drive itself in the axial direction on the runout detection.

[0053] The air inlet 21 of the driving disk 2 is connected to a rotary joint 23, a straight-through movable tube 24, an air supply flexible tube 25 and an air supply source 26; a bracket 27 is provided at the position of the straight-through movable tube 24, and a movable seat 30 with an embedded guide cylinder 29 is elastically suspended by an elastic part 28 in the bracket 27. The straight-through movable tube 24 coaxially slides through the guide cylinder 29, so that the straight-through movable tube 24 is in a suspended movable state connected between the air supply flexible tube 25 and the rotary joint 23, thereby compensating for the slight deflection of the rotary joint 23, avoiding excessive distortion of the air supply flexible tube 25, and ensuring the stability of air supply and air drive.

[0054] The advantages of the present invention are as follows:

[0055] 1) A single system covers three runout detection indicators: radial runout, axial runout, and end face runout, and supports dynamic loading of axial and radial loads;

[0056] 2) The guide rail mechanism realizes automatic switching and precise positioning between detection and force application states, reducing manual intervention errors;

[0057] 3) The ball head contact combined with the air drive vibration-free design improves the accuracy of capturing the beating signal;

[0058] 4) Push-pull force gauges apply force in multiple directions to simulate real loads, and the air-driven rotation restores the interference-free operation state;

[0059] 5) The relief cone stabilizes the airflow and the floating air supply pipe resists deflection, ensuring long-term detection stability.

[0060] The present invention integrates the traditional independent axial and radial runout detection and load testing processes into one that can realize integrated radial and axial runout detection of the pump shaft under simulated load, thereby improving detection efficiency, accuracy and working condition coverage, and is particularly suitable for quality inspection and fault analysis scenarios of high-precision pump shafts.

[0061] The above is only a preferred embodiment of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the principles of the present invention. These improvements and modifications should also be regarded as the scope of protection of the present invention.

Claims

1. A state-transition pump shaft simulated load beating detection system for detecting the beating of a pump shaft (10) under a simulated load, characterized in that: include: A pump (1) having a pump shaft (10) fixedly provided with a driving disc (2) and a force-bearing disc (3) in sequence along an axial direction, wherein the driving disc (2), the pump shaft (10) and the force-bearing disc (3) are located on the same central axis (11); A dial indicator (4) which can be selectively configured to: Radial runout detection state: the probe is perpendicular to the central axis (11) and abuts against the outer circumferential surface of the pump shaft (10); Axial runout detection state: the probe overlaps or is parallel to the central axis (11) and abuts against the axial end face of the pump shaft (10); and a push-pull force gauge (5), which can be selectively configured as follows by adjusting its position and the direction of the force-applying end: Radial force application state: the force application end is perpendicular to the central axis (11) and abuts against the outer circumferential surface of the force-bearing disc (3) to apply a radial simulated load; Axial force application state: the force application end is parallel to the central axis (11) and abuts against the disk end surface of the force-bearing disk (3) to apply an axial simulated load.

2. The pump shaft simulated load jump detection system of state transition according to claim 1, characterized in that: The axial runout detection state includes an axial movement detection state and an end face runout detection state, wherein: Axial movement detection state: the probe overlaps the central axis (11) and abuts against the center of the axial end face of the pump shaft (10); End face runout detection state: the probe is parallel to the central axis (11) and abuts against the edge of the axial end face of the pump shaft (10).

3. The pump shaft simulated load jump detection system with state transition according to claim 2, characterized in that: It comprises a dial gauge feeding mechanism (6) and a dial gauge position conversion adjustment mechanism (7), wherein the dial gauge (4) is arranged on the dial gauge position conversion adjustment mechanism (7) via the dial gauge feeding mechanism (6); The dial indicator position conversion adjustment mechanism (7) drives the dial indicator (4) to move between an orientation in which the probe is perpendicular to the central axis (11) and an orientation in which the probe overlaps or is parallel to the central axis (11) to perform position conversion. The dial indicator feed mechanism (6) drives the dial indicator (4) to move toward the pump shaft (10) so that the probe abuts against the outer circumferential surface or the axial end face of the pump shaft (10), thereby realizing detection state switching between a radial runout detection state and an axial runout detection state.

4. The pump shaft simulated load jump detection system with state transition according to claim 3, characterized in that: The dial indicator position conversion adjustment mechanism (7) comprises a first circular arc guide rail (71) and a linear guide rail (72), and the dial indicator feeding mechanism (6) is arranged on the first circular arc guide rail (71) through the linear guide rail (72); the arc bending direction of the first circular arc guide rail (71) is downward and toward the pump shaft (10), and the tangent line of the high point position at the end of the stroke is parallel to the central axis (11), and the tangent line of the low point position at the end of the stroke is perpendicular to the central axis (11), so as to provide a driving force for the dial indicator (4) to move between the orientation of the measuring head perpendicular to the central axis (11) and the orientation of the measuring head overlapping or parallel to the central axis (11) for position conversion; the linear guide rail (72) is arranged on the first circular arc guide rail (71); the arc bending direction of the first circular arc guide rail (71) is downward and toward the pump shaft (10), and the tangent line of the first circular arc guide rail (71) is parallel to the central axis (11) and the tangent line of the first circular arc guide rail (71) is parallel to the central axis (11). The linear guide rail (72) is arranged along the tangent direction of the first circular arc guide rail (71), and provides a driving force for the dial indicator (4) to move between the orientation of the overlapping central axis of the probe and the orientation of the parallel central axis of the probe to perform position conversion, thereby realizing the detection state switching between the axial movement detection state and the end face runout detection state in the axial runout detection state; the dial indicator feed mechanism (6) and the dial indicator (4) are both arranged along the radial direction of the first circular arc guide rail (71), and the dial indicator feed mechanism (6) drives the dial indicator (4) to move along the radial direction of the first circular arc guide rail (71), thereby realizing the probe abutting against the outer circumferential surface or the axial end face of the pump shaft (10).

5. The state-transition pump shaft simulated load jump detection system according to claim 1, characterized in that: It comprises a push-pull force gauge feeding mechanism (8) and a push-pull force gauge position conversion adjustment mechanism (9), wherein the push-pull force gauge (5) is arranged on the push-pull force gauge position conversion adjustment mechanism (9) via the push-pull force gauge feeding mechanism (8); The push-pull force gauge position conversion adjustment mechanism (9) drives the push-pull force gauge (5) to move between an orientation in which the force-applying end is perpendicular to the central axis (11) and an orientation in which the force-applying end is parallel to the central axis (11) to perform position conversion, and the push-pull force gauge feeding mechanism (8) drives the push-pull force gauge (5) to move toward the force-applying disk (3) so that the force-applying end abuts against the outer circumferential surface or disk end surface of the force-applying disk (3).

6. The state-transition pump shaft simulated load jump detection system according to claim 5, characterized in that: The push-pull force gauge position conversion adjustment mechanism (9) includes a second circular arc guide rail (91), and the push-pull force gauge feeding mechanism (8) is arranged on the second circular arc guide rail (91); the arc bending direction of the second circular arc guide rail (91) is upward and toward the pump shaft (10), and the tangent line of the position of the lowest point at the end of the stroke is parallel to the central axis (11), and the tangent line of the position of the highest point at the end of the stroke is perpendicular to the central axis (11), so as to provide the push-pull force gauge (5) with a vertical position at the force application end of the central axis (11). ) and the direction of the force-applying end parallel to the central axis (11) for position conversion; the push-pull force gauge feeding mechanism (8) and the push-pull force gauge (5) are both arranged along the radial direction of the second circular arc guide rail (91), and the push-pull force gauge feeding mechanism (8) drives the push-pull force gauge (5) to move along the radial direction of the second circular arc guide rail (91), so as to achieve the abutment of the force-applying end against the outer circumferential surface or the axial end face of the force-bearing disk (3) to apply an axial simulated load or a radial simulated load.

7. The pump shaft simulated load jump detection system with state transition according to claim 1, characterized in that: The probe of the dial indicator (4) is provided with a first ball head (40) that is in rolling contact with the pump shaft (10); the force-applying end of the push-pull dynamometer (5) is provided with a second ball head (50) that is in rolling contact with the force-bearing disk (3).

8. The pump shaft simulated load jump detection system with state transition according to claim 1, characterized in that: The driving disk (2) is an air-driven rotating disk with a hollow interior and air holes (20) uniformly distributed in an array on its outer circumference. The axes of the air holes (20) and the tangent of the driving disk (2) where the holes are located have an acute angle. The driving disk (2) rotates due to the reverse thrust generated by the jets ejected from the air holes (20), and the driving disk (2) drives the pump shaft (10) and the force-bearing disk (3) to rotate synchronously.

9. The state-transition pump shaft simulated load jump detection system according to claim 8, characterized in that: The air inlet (21) of the driving disc (2) is located at the disc center, and the inner disc surface of the driving disc (2) facing the air inlet (21) is a force relief cone surface (22) for guiding the input gas from the center to the surrounding areas to achieve force relief.

10. The state-transition pump shaft simulated load jump detection system according to claim 9, characterized in that: The air inlet (21) of the driving disk (2) is connected to a rotary joint (23), a straight-through movable tube (24), an air supply flexible tube (25) and an air supply source (26); a bracket (27) is provided at the position where the straight-through movable tube (24) is located, and a movable seat (30) with an embedded guide cylinder (29) is elastically suspended and supported in the bracket (27) by an elastic portion (28). The straight-through movable tube (24) is coaxially slidably arranged to pass through the guide cylinder (29), so that the straight-through movable tube (24) is in a suspended movable state connected between the air supply flexible tube (25) and the rotary joint (23).

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