A bearing measuring device and a bearing measuring method

Abstract

The application belongs to the field of bearing measurement, and particularly relates to a bearing measurement device and a bearing measurement method. In order to reduce the vibration of the bearing during measurement, the application provides a bearing measurement device, which comprises a main shaft, a bearing seat, a loading device and a fixedly arranged stopper, and the bearing seat is connected with a rotation-stopping piece; in the circumferential direction of the bearing seat, the stopper has a stop surface for stop cooperation with the rotation-stopping piece, the stop surface is located on both sides of the rotation-stopping piece, and the stop surfaces on both sides of the rotation-stopping piece are in time gap cooperation with the rotation-stopping piece in the non-rotation direction of the main shaft, so as to limit the rotation of the bearing seat by the stop surface and provide a clearance space for avoiding the axial movement path and the radial movement path of the rotation-stopping piece; the bearing seat is provided with a force sensor for measuring the friction force between the rotation-stopping piece and the stop surface. The application also provides a bearing measurement method using the above bearing measurement device. When the bearing seat vibrates, the two stop surfaces can limit the circumferential rotation or rotation tendency of the rotation-stopping piece, so as to reduce the vibration of the bearing seat.

Description

TECHNICAL FIELD

[0001] The present application belongs to the field of bearing measurement, and particularly relates to a bearing measurement device and a bearing measurement method. BACKGROUND

[0002] As shown in Figure 1 and Figure 2 , when measuring the bearing 3, it is often necessary to apply an axial load and / or a radial load to the bearing 3 by using a loading device, and to drive the bearing 3 to rotate by using the main shaft 1, so as to measure the parameters of the bearing 3 when rotating under load.

[0003] In the field, the commonly used structure for measurement is a simply supported beam structure or a cantilever beam structure, the bearing seat 2 (including a seat body and an end cover) is installed on the main shaft 1, and the bearing 3 is installed on the main shaft and the bearing seat 2, and the driving motor drives the main shaft 1 to rotate, so as to drive the bearing 3 to rotate.

[0004] When loading the bearing 3, since the bearing 3 is located in the bearing seat 2, it is necessary to apply a load to the bearing seat 2, so as to indirectly apply a load F to the bearing 3, and the load F can be a radial load Fr, an axial load Fa or a combined load of the radial load Fr and the axial load Fa. As shown in Figure 1 and Figure 2 , in order to ensure the accuracy of the application of the radial load Fr, the bearing seat 2 cannot be radially limited, so as to ensure that the radial load Fr is applied to the bearing 3; similarly, in order to ensure the accuracy of the application of the axial load Fa, the bearing seat 2 cannot be axially limited, so as to ensure that the axial load Fa is applied to the bearing 3.

[0005] When the main shaft 1 drives the bearing 3 to rotate, the bearing 3 will apply a circumferential rotating force to the bearing seat 2, so as to make the bearing seat 2 have a rotating tendency. In order to avoid the rotation of the bearing seat 2, the loading device will apply a friction force to the bearing seat 2, and since the normal pressure between the loading device and the bearing seat 2 is the radial load Fr or the axial load Fa applied by the loading device to the bearing seat 2, the maximum static friction force F between the loading device and the bearing seat 2 is μ·Fr or μ·Fa. Therefore, when the load applied by the loading device is large enough, the maximum static friction force F is large enough to overcome the circumferential rotating force applied by the bearing 3 to the bearing seat 2, so as to ensure that the bearing seat 2 does not rotate. However, when the load applied by the loading device is small, the maximum static friction force is small, and it is not enough to overcome the circumferential rotating force applied by the bearing 3 to the bearing seat 2, so the bearing seat 2 will rotate, which leads to the failure to continue the measurement.

[0006] In the field, the loading device is generally a cylinder or an oil cylinder, and the piston rod of the cylinder or the oil cylinder applies a load to the bearing seat 2. Since there is a gap between the piston rod and the corresponding cylinder body, when the bearing seat 2 shakes under the action of the bearing 3, the bearing seat 2 will drive the piston rod to shake under the action of static friction, and the shaking of the piston rod will further aggravate the shaking of the bearing seat 2, resulting in large vibration of the bearing and affecting the accuracy of the measured data. At the same time, affected by inertia, the vibration of the piston rod and the bearing seat 2 cannot always be consistent, so there will be a slip phenomenon between the piston rod and the bearing seat 2, thereby causing the vibration of the bearing seat 2 and the bearing to be more severe, affecting the accuracy of the measured data. SUMMARY

[0007] The purpose of the present application is to provide a bearing measuring device to solve the technical problem of inaccurate measurement data caused by large bearing vibration during measurement.

[0008] The purpose of the present application is also to provide a bearing measuring method to solve the same technical problem.

[0009] To achieve the above-mentioned purpose, the technical scheme of the bearing measuring device provided by the present application is:

[0010] A bearing measuring device, comprising a main shaft for driving the bearing to rotate, a bearing seat mounted on the main shaft, and a loading device for applying a radial load and / or an axial load to the bearing seat, further comprising a stopper arranged fixedly when the bearing rotates, and a rotation-stopping piece connected with the bearing seat and moving synchronously with the bearing seat on the outer surface of the bearing seat;

[0011] In the circumferential direction of the bearing seat, the stopper has a stop surface for stop cooperation with the rotation-stopping piece, the stop surface is located on both sides of the rotation-stopping piece, and the stop surfaces on both sides of the rotation-stopping piece are in clearance fit with the rotation-stopping piece when the main shaft does not rotate, so as to limit the circumferential rotation and circumferential rotation trend of the bearing seat through the stop surface, and provide a clearance space for avoiding the axial movement path and the radial movement path of the rotation-stopping piece;

[0012] The bearing seat is provided with a force sensor for measuring the friction force between the rotation-stopping piece and the stop surface.

[0013] Further, the friction coefficient μ between the rotation-stopping piece and the stop surface is less than 0.1.

[0014] Further, the stopper comprises a stopper body and an elastic buffer layer arranged close to one side of the rotation-stopping piece when the stopper body is used, and the surface of the elastic buffer layer for contacting the rotation-stopping piece constitutes the stop surface, so as to reduce the vibration of the rotation-stopping piece and the bearing seat.

[0015] Further, the bearing measuring device comprises two stoppers arranged on the circumference of the bearing seat and on both sides of the rotation-stopping piece, the surfaces of the two stoppers arranged opposite to each other form the stop face, and the space between the two stoppers forms the avoiding space.

[0016] Further, the bearing measuring device comprises a mounting base below the main shaft, the mounting base is provided with a sliding groove, the extension direction of the sliding groove is perpendicular to the axial direction of the main shaft, the sliding groove comprises a stopper sliding groove and a bolt sliding groove; the stopper sliding groove is in guided sliding cooperation with the stopper; the stopper is provided with a bolt, the bolt sliding groove comprises a bolt head sliding groove and a communication hole above the bolt head sliding groove and connected with the stopper sliding groove, the cross-sectional area of the communication hole is smaller than that of the bolt head of the bolt, the bolt head is in guided sliding cooperation with the bolt head sliding groove, and the bolt is connected with a nut after penetrating through the stopper, so that the stopper is fixed on the mounting base by the bolt and the nut after the stopper is slid into place.

[0017] Further, the stopper is provided with an insertion slot for the insertion of the rotation-stopping piece, the two slot side walls arranged opposite to each other on the circumference of the bearing seat form the stop face, and the internal space of the insertion slot forms the avoiding space.

[0018] Further, the rotation-stopping piece is in a "T" shape, the rotation-stopping piece comprises a horizontal plate and a vertical plate perpendicular to the horizontal plate, the vertical plate is connected to the horizontal plate, the horizontal plate is connected to the bearing seat, and the vertical plate is inserted between the two stop faces for the circumferential stop cooperation with the stop faces.

[0019] Further, the rotation-stopping piece is connected to the outer circumferential surface of the bearing seat, and the force sensor is arranged between the rotation-stopping piece and the bearing seat.

[0020] Further, the bearing measuring device further comprises a PLC automatic control module, the PLC automatic control module is used for collecting the data measured by the force sensor in real time, and is used for increasing the load output by the loading device on the basis of the initial value by the value of the data measured by the force sensor.

[0021] The bearing measuring device has the advantages that: the bearing measuring device is an improved invention, and the core difference between the bearing measuring device and the prior art is that: in the prior art, the rotation of the bearing seat is limited by the friction force between the loading device and the bearing seat, when the load applied by the loading device is small, the maximum static friction force is small, which is not enough to overcome the circumferential rotation force applied by the bearing on the bearing seat, and the bearing seat will rotate; in the bearing measuring device, the rotation of the stop rotating piece is limited by the stop surface on the basis of the friction force between the loading device and the bearing seat, thereby limiting the rotation of the bearing seat, and therefore, even if the load applied by the loading device is small, the stop surface can limit the rotation of the bearing seat, thereby measuring the parameters of the bearing under a small load. Meanwhile, in the bearing measuring device, the stop surface is located on both sides of the stop rotating piece, and the stop surface on both sides of the stop rotating piece is in clearance fit with the stop rotating piece, and when the bearing seat vibrates, the high-frequency vibration caused by the circumferential rotation trend of the bearing seat can be limited, thereby reducing the vibration of the bearing seat.

[0022] When the loading device applies a radial load and / or an axial load to the bearing seat during measurement, the bearing seat will be slightly displaced in the radial direction and / or the axial direction, and since the avoidance space exists, the stop piece will not limit the bearing seat in the radial direction and / or the axial direction, thereby ensuring that the load is applied to the bearing through the bearing seat.

[0023] It should be noted that after the main shaft drives the bearing to rotate, the stop piece is in stop contact with the stop surface, and therefore, the friction force exists between the stop piece and the stop surface, and the friction force can be monitored by the force sensor.

[0024] To achieve the above-mentioned purposes, the technical scheme of the bearing measuring method provided by the application is:

[0025] A bearing measuring method is measured by using a bearing measuring device, the bearing measuring device comprises a main shaft for driving the bearing to rotate, a bearing seat mounted on the main shaft, and a loading device for applying a radial load and / or an axial load to the bearing seat, and further comprises a stop piece arranged fixedly when the bearing rotates, and the outer surface of the bearing seat is connected with a stop rotating piece that moves synchronously with the bearing seat;

[0026] In the circumferential direction of the bearing seat, the stop piece has a stop surface for stop fit with the stop rotating piece, the stop surface is located on both sides of the stop rotating piece, and the stop surface on both sides of the stop rotating piece is in clearance fit with the stop rotating piece when the main shaft does not rotate, so as to limit the circumferential rotation and circumferential rotation trend of the bearing seat by the stop surface, and provide an avoidance space for avoiding the axial movement path and the radial movement path of the stop rotating piece;

[0027] The bearing seat is provided with a force sensor for measuring the friction force between the stop rotating piece and the stop surface;

[0028] The main shaft drives the bearing installed in the bearing seat to rotate, and the loading device applies an initial load F0 to the bearing seat to indirectly apply an axial load and / or a radial load to the bearing. When the main shaft drives the bearing to rotate, the rotation-stopping piece is in abutting engagement with the limiting surface in the circumferential direction of the bearing seat to limit the circumferential rotation and the circumferential rotation tendency of the bearing seat by limiting the rotation-stopping piece, thereby reducing the high-frequency vibration caused by the circumferential rotation tendency of the bearing seat. The force sensor is used to measure the friction force f between the rotation-stopping piece and the limiting surface, and the load applied by the loading device is adjusted in real time to F0+f, or the compensation constant f0 is determined according to the fluctuation curve of the friction force f, and the load applied by the loading device is fixed to F0+f0.

[0029] Further, the friction coefficient μ between the rotation-stopping piece and the limiting surface is less than 0.1.

[0030] Further, the limiting piece includes a limiting piece body and an elastic buffer layer arranged on the side close to the rotation-stopping piece when the limiting piece body is used, and the surface of the elastic buffer layer used to contact the rotation-stopping piece constitutes the limiting surface, so as to reduce the vibration of the rotation-stopping piece and the bearing seat.

[0031] Further, in the circumferential direction of the bearing seat, the limiting piece has two limiting pieces arranged on the two sides of the rotation-stopping piece, and the surfaces of the two limiting pieces arranged opposite constitute the limiting surface, and the space between the two limiting pieces constitutes the avoiding space.

[0032] Further, the bearing measuring device includes a mounting seat below the main shaft, and the mounting seat is provided with a sliding groove, the extension direction of the sliding groove is perpendicular to the axial direction of the main shaft, and the sliding groove includes a limiting piece sliding groove and a bolt sliding groove; the limiting piece sliding groove is in guiding sliding cooperation with the limiting piece; a bolt is arranged through the limiting piece, the bolt sliding groove includes a bolt head sliding groove and a communication hole arranged above the bolt head sliding groove and communicating the bolt head sliding groove and the limiting piece sliding groove, the cross-sectional area of the communication hole is smaller than the cross-sectional area of the bolt head of the bolt, the bolt head is in guiding sliding cooperation with the bolt head sliding groove, and a nut is connected to the bolt after the bolt passes through the limiting piece, so as to fix the limiting piece on the mounting seat by the bolt and the nut after the limiting piece is slid into place.

[0033] Further, the limiting piece is provided with a slot for inserting the rotation-stopping piece, and in the circumferential direction of the bearing seat, the two groove side walls arranged opposite constitute the limiting surface, and the internal space of the slot constitutes the avoiding space.

[0034] Further, the rotation-stopping piece is in a "T" structure, and the rotation-stopping piece includes a horizontal plate and a vertical plate perpendicular to the horizontal plate, the vertical plate is connected to the horizontal plate, the horizontal plate is connected to the bearing seat, and the vertical plate is inserted between the two limiting surfaces to be in circumferential abutting cooperation with the limiting surfaces.

[0035] Further, the rotation-stopping piece is connected to the outer circumferential surface of the bearing seat, and the force sensor is arranged between the rotation-stopping piece and the bearing seat.

[0036] The bearing measurement method provided by the application has the beneficial effect that the application is an improved invention. Compared with the prior art, the application introduces a stop surface to limit the circumferential movement of the rotation-stopping piece, so as to avoid the rotation of the bearing seat. The stop surface on the two sides of the rotation-stopping piece is in clearance fit with the rotation-stopping piece. When the bearing seat vibrates, the high-frequency vibration caused by the circumferential rotation trend of the bearing seat can be limited, so as to reduce the vibration of the bearing seat.

[0037] In use, the rotation-stopping piece is in circumferential stop fit with the stop surface to provide the normal pressure required by the friction force. The loading device applies an initial load F0 (axial load and / or radial load) to the bearing seat, and the bearing seat and the rotation-stopping piece will have corresponding axial displacement and / or radial displacement (or have a movement trend with axial displacement and / or radial displacement), so that the friction force f is generated between the rotation-stopping piece and the stop surface. The direction of the friction force f is opposite to the direction of the initial load F0, and the friction force f offsets part of the initial load. Therefore, the load applied by the loading device needs to be adjusted to F0+f or F0+f0, so as to measure the parameters of the bearing under the initial load F0. BRIEF DESCRIPTION OF DRAWINGS

[0038] Figure 1 It is a structural schematic diagram of a simply supported beam structure.

[0039] Figure 2 It is a structural schematic diagram of a cantilever beam structure.

[0040] Figure 3 It is a structural schematic diagram of a bearing measurement device.

[0041] Figure 4 It is a structural schematic diagram of a bearing measurement device. Figure 3 It is an enlarged view of the structure at A in FIG. 1.

[0042] Figure 5 It is a partial structural schematic diagram of a bearing measurement device.

[0043] Figure 6 It is an enlarged view of the structure at B in FIG. 1. Figure 5 It is an enlarged view of the structure at B in FIG. 1.

[0044] Figure 7 It is a front view of a partial structure of a bearing measurement device.

[0045] Figure 8 It is an enlarged view of the structure at C in FIG. 1. Figure 7 It is an enlarged view of the structure at C in FIG. 1.

[0046] Figure 9 It is a side view of a partial structure of a bearing measurement device.

[0047] Figure 10 It is an enlarged view of the structure at D in FIG. 1. Figure 9

[0048] It is an enlarged view of the structure at D in FIG. 1.Figure 11 Structure diagram of relative arrangement position of two stoppers in bearing measuring device;

[0049] Figure 12 Structure diagram of rotation-stopping piece in bearing measuring device;

[0050] Figure 13 Vibration-speed diagram of bearing when test is carried out by using existing bearing measuring device;

[0051] Figure 14 Vibration-speed diagram of bearing when test is carried out by using bearing measuring device of the present application.

[0052] Explanation of reference numerals:

[0053] 1, main shaft; 2, bearing seat; 3, bearing; 4, loading device; 5, force sensor; 6, rotation-stopping piece; 6-1, horizontal plate; 6-2, vertical plate; 7, stopper; 7-1, stop face; 7-2, bolt through hole; 8, mounting seat; 8-1, stopper sliding groove; 8-2, bolt sliding groove; 9, bolt assembly; 9-1, bolt; 9-2, nut; 10, avoiding space. DETAILED DESCRIPTION

[0054] In order to solve the problems in the background art, the core inventive concept of the present application is that, on the basis of not affecting axial movement and radial movement of the bearing seat and keeping friction between the loading device and the bearing seat, the bearing seat is circumferentially limited by the fixed stopper, so as to limit rotation of the bearing seat and reduce vibration of the bearing seat.

[0055] The present application will be further described in detail in combination with the embodiments.

[0056] The embodiments of the bearing measuring device provided by the present application are as follows:

[0057] As Figures 3-12As shown, the bearing measuring device comprises a motor for driving the main shaft 1 to rotate, the main shaft 1 for driving the bearing 3 to rotate, the bearing seat 2 mounted on the main shaft 1, the loading device 4 for applying a load to the bearing seat 2, and the stopper 7 arranged fixedly when the bearing 3 rotates. The outer surface of the bearing seat 2 is connected with the rotation-stopping member 6 which moves synchronously with the bearing seat 2. The loading device 4 comprises a radial loading device for applying a radial load to the bearing seat 2 and an axial loading device for applying an axial load to the bearing seat 2, so as to indirectly apply a radial load and / or an axial load to the bearing 3 through the bearing seat 2. In the circumferential direction of the bearing seat 2, the stopper 7 has a stop surface 7-1 for stop cooperation with the rotation-stopping member 6. The stop surface 7-1 is located on both sides of the rotation-stopping member 6. The stop surface 7-1 on both sides of the rotation-stopping member 6 is in small gap cooperation with the rotation-stopping member 6 when the main shaft 1 does not rotate, so as to limit the rotation of the bearing seat 2 through the rotation-stopping surface and provide a clearance space 10 for avoiding the axial movement path and the radial movement path of the rotation-stopping member 6. When the main shaft 1 rotates at high speed, the small gap between the two stop surfaces 7-1 and the rotation-stopping member 6 can prevent the circumferential rotation of the bearing seat 2 and limit the high-frequency vibration caused by the circumferential rotation tendency of the bearing seat 2, thereby reducing the vibration of the bearing seat 2. Meanwhile, the bearing seat 2 is provided with the force sensor 5 for measuring the friction force between the rotation-stopping member 6 and the stop surface 7-1. The force sensor 5 is a force sensor 5 for measuring friction force in the prior art, and the setting position is in a conventional manner in the art, for example, it can be arranged between the rotation-stopping member 6 and the bearing seat 2. The stopper 7 and the rotation-stopping member 6 can be block-shaped, plate-shaped or other shapes.

[0058] It should be particularly pointed out that, in the art, according to different needs, only the axial loading device or the radial loading device can be arranged. Figure 3 In the bearing measuring device (simply supported beam structure) shown, Figure 3 except for A in the prior art (i.e. Figure 4 ), the remaining parts are all prior art. The present application is equivalent to adding the force sensor 5, the rotation-stopping member 6 and the stopper 7 on the basis of the prior art bearing measuring device. Therefore, except for the parts related to the force sensor 5, the rotation-stopping member 6 and the stopper 7, the remaining parts are all prior art, which will not be described here.

[0059] In the test, first, the bearing 3 is mounted on the main shaft 1 and the bearing seat 2; then, the main shaft 1 drives the bearing 3 to rotate, and the loading device 4 applies a load F to the bearing 3. In this process, on the one hand, the rotation-stopping member 6 is in stop cooperation with the stop surface 7-1, so as to limit the circumferential rotation of the rotation-stopping member 6 and thereby limit the circumferential rotation of the bearing seat 2. On the other hand, the rotation-stopping member 6 moves (or has a tendency to move) in the direction of the load F (radial and / or axial), and generates a friction force f between the rotation-stopping member 6 and the stop surface 7-1. The force sensor 5 can detect the size of the friction force f. Finally, the parameters of the bearing 3 can be measured, and the specific measurement process is the same as that of the prior art, which will not be described here.

[0060] In the measurement, since the friction force f is opposite to the direction of the initial load F0 applied by the loading device 4, the load applied by the loading device 4 is offset to some extent, so that the actual load borne by the bearing 3 is less than the initial load F0. Therefore, one of the following three methods can be used by those skilled in the art to deal with it:

[0061] (1) The ratio of the friction force f to the initial load F0 is calculated. If the ratio of the friction force f to the initial load F0 is less than the allowable value, the initial load F0 does not need to be compensated, and the error measured is within the allowable measurement error range. The allowable value is generally 1% or 5% or the like. The smaller the allowable value, the higher the required accuracy. The allowable value cannot exceed 10%. If the ratio of the friction force f to the initial load F0 exceeds 10%, one of the following two methods must be used for compensation.

[0062] (2) Due to the influence of the vibration of the bearing seat 2, the friction force f fluctuates within a certain range. Those skilled in the art can observe the fluctuation curve of the friction force f on the industrial computer and select a representative constant value as the compensation constant value f0 (the friction force f fluctuates around the compensation constant value f0). The load applied by the loading device 4 is adjusted to F0+f0. Of course, the compensation constant value f0 can also be calculated by the PLC automatic control module (including an industrial computer with calculation function), and the load applied by the loading device 4 is adjusted to F0+f0 by the PLC automatic control module.

[0063] In this way, the compensation constant value f0 is used instead of the fluctuating friction force f, which is convenient to calculate and can quickly determine the fluctuation value f0 according to the fluctuation curve of the friction force f without the help of an industrial computer. At the same time, the force applied by the loading device 4 (generally a pneumatic cylinder or an oil cylinder) is constant and does not need to be adjusted back and forth.

[0064] (3) The PLC automatic control module collects the friction force f measured by the force sensor 5 in real time, and adjusts the load applied by the loading device 4 in real time to F0+f. In this way, the load borne by the bearing 3 is closest to the initial value F0, and the measurement accuracy is the highest.

[0065] It should be particularly noted that even if the ratio of the friction force f to the initial load F0 is less than 1%, the above-mentioned method (2) or method (3) can be used for compensation.

[0066] In order to verify the actual use effect of the device, a vibration sensor is additionally arranged at the outer diameter of the bearing 3 in the existing bearing measurement device and the bearing measurement device in the application to monitor the vibration value of the bearing 3 in real time. In the application, two groups of experiments are conducted for the existing bearing measurement device and the bearing measurement device in the application, respectively, correspondingFigure 13 and Figure 14 . Take Figure 13 for example, the reading method of Figure 13 and Figure 14 is introduced, Figure 13 The blue rotating speed waveform curve and the red vibration waveform curve are included, in the time period from 0 to t, as shown in the rotating speed waveform curve, the rotating speed of the bearing 3 is 3000 r / min, as shown in the vibration waveform curve, the vibration of the bearing 3 is about 4 m / s 2 , in the time period from t to T, the rotating speed of the main shaft 1 is continuously increased, the rotating speed of the bearing 3 is continuously increased, in the time period from T to 17 s, as shown in the rotating speed waveform curve, the rotating speed of the bearing 3 is 24000 r / min, as shown in the vibration waveform curve, the vibration of the bearing 3 is about 100 m / s 2 , wherein t is 8.5 s, T is 10.83 s. Figure 14 The reading method is the same, Figure 14 The blue rotating speed waveform curve and the red vibration waveform curve are included, in the time period from 0 to t, as shown in the rotating speed waveform curve, the rotating speed of the bearing 3 is 3000 r / min, as shown in the vibration waveform curve, the vibration of the bearing 3 is about 3 m / s 2 , in the time period from t to T, the rotating speed of the main shaft 1 is continuously increased, the rotating speed of the bearing 3 is continuously increased, in the time period from T to 17 s, as shown in the rotating speed waveform curve, the rotating speed of the bearing 3 is 24000 r / min, as shown in the vibration waveform curve, the vibration of the bearing 3 is about 45 m / s 2 , wherein t is 8.5 s, T is 10.83 s. In the control test (1): in the time period from 0 to t, the rotating speed of the bearing 3 is 3000 r / min, as shown in the vibration waveform curve in Figure 13 , when the existing bearing measuring device is used, the vibration of the bearing 3 is about 4 m / s 2 , as shown in the vibration waveform curve in Figure 14 , when the bearing measuring device in the application is used, the vibration of the bearing 3 is about 3 m / s 2 , the vibration is reduced by 25%; in the control test (2): in the time period from T to 17 s, the rotating speed of the bearing 3 is 24000 r / min, as shown in the vibration waveform curve in Figure 13 , when the existing bearing measuring device is used, the vibration of the bearing 3 is about 100 m / s 2 , as shown in the vibration waveform curve in Figure 14 , when the bearing measuring device in the application is used, the vibration of the bearing 3 is about 45 m / s 2 , the vibration is reduced by more than 50%.

[0067] In the present application, even if the compensation is made in the above-mentioned manner (3) and the force sensor 5 measurement time delay, signal transmission time and PLC automatic control module calculation time are all regarded as 0, the load F adjustment is also affected by the loading device 4 load adjustment speed (cylinder and air cylinder output load adjustment speed) and needs a certain time. At the same time, the main shaft 1 and bearing 3 rotate at a very high speed, so the bearing 3 vibration frequency is very high, and the bearing seat 2 vibration frequency is also very high, which causes the friction force f between the stopper 7 and the stop surface 7-1 to change very quickly, so even if the real-time adjustment is used, there will be a certain delay.

[0068] Preferably, in the present application, since the normal pressure between the rotation stopper 6 and the stopper 7 is uncontrollable, in order to reduce the ratio of the friction force f to the initial load F0, the rotation stopper 6 and the stop surface 7-1 can be made smoother, so that the friction coefficient μ between the rotation stopper 6 and the stop surface 7-1 is less than 0.1, thereby minimizing the influence of the friction force f on the load of the bearing 3 and ensuring that the measurement result meets the expectation.

[0069] Of course, the friction coefficient μ can also be 0.15, 0.2, 0.25, 0.3, 0.4, etc. It needs to be emphasized that in the present application, the friction coefficient μ should be as small as possible, so even if the compensation is made in the above-mentioned manner (2) or manner (3), it is not recommended to increase the friction coefficient μ to more than 0.3.

[0070] In order to further reduce the vibration of the bearing 3, in a preferred embodiment, the stopper 7 comprises a stopper body (not shown in the figure) and an elastic buffer layer (not shown in the figure) arranged on the side of the stopper body close to the rotation stopper 6 during use, and the surface of the elastic buffer layer used to contact the rotation stopper 6 constitutes the stop surface 7-1, so as to reduce the vibration of the rotation stopper 6 and the bearing seat 2. The stopper body can be made of metal material, and the elastic buffer layer can be made of smooth-surfaced rubber or silicone, so as to reduce the friction coefficient of the stop surface 7-1.

[0071] In other embodiments, the stopper 7 and the rotation stopper 6 can be made of smooth-surfaced metal material to reduce the friction coefficient.

[0072] The arrangement of the stopper 7 and the rotation stopper 6 will be described in detail below.

[0073] For ease of understanding, in this article, the main shaft 1 extends horizontally, and the axial direction of the main shaft 1 is defined as the left-right direction, but in the actual working condition, according to the different directions of the observer, the axial direction of the main shaft 1 can also be the front-back direction, at this time, the "front-back direction" in the actual working condition constitutes the "left-right direction" in this article.

[0074] In one embodiment, as shown in Figures 3-11As shown in the drawings, the bearing seat 2 is provided with two stoppers 7 arranged on the circumference of the bearing seat 2 and on the two sides of the rotation-stopping piece 6, the surfaces of the two stoppers 7 arranged opposite to each other form the stop surfaces 7-1, and the space between the two stoppers 7 forms the avoiding space 10, which is simple in structure.

[0075] The stopper 7 can be welded to the mounting seat 8 below the main shaft 1, as shown in the drawings. Figure 3 As shown in the drawings, the rotation-stopping piece 6 is fixedly connected to the bearing seat 2 by welding or the like, and when the bearing seat 2 needs to be repaired, the bearing seat 2 needs to be moved leftward and rightward to separate the rotation-stopping piece 6 from the stopper 7 in the front-rear direction; or the rotation-stopping piece 6 is flange-connected to the bearing seat 2, and in this case, the length of the rotation-stopping piece 6 in the up-down direction can be lengthened to reserve space for the dismounting bolts, thereby facilitating the dismounting of the rotation-stopping piece 6 from the bearing seat 2.

[0076] Preferably, as shown in the drawings, Figures 3-11 The mounting seat 8 is provided with a sliding groove extending in the front-rear direction, which includes a stopper sliding groove 8-1 and a bolt sliding groove 8-2; the stopper sliding groove 8-1 is in guided sliding cooperation with the stopper 7; the stopper 7 is provided with a bolt 9-1 penetrating therethrough; the bolt sliding groove 8-2 includes a bolt head sliding groove and a communication hole located above the bolt head sliding groove and communicating the bolt head sliding groove with the stopper sliding groove 8-1, the cross-sectional area of the communication hole is smaller than that of the bolt head of the bolt 9-1, the bolt head is in guided sliding cooperation with the bolt head sliding groove, and the bolt 9-1 is connected with a nut 9-2 after penetrating through the stopper 7, so as to fix the stopper 7 to the mounting seat 8 by using the bolt assembly 9 (including the bolt 9-1 and the nut 9-2) after the stopper 7 is slid into position. Figure 11 As shown in the drawings, the stopper 7 is in “L” shape, so as to thin the thickness at the bolt through hole 7-2, thereby facilitating the penetration of the bolt 9-1 through the bolt through hole 7-2 of the stopper 7.

[0077] When repair is needed, the nut 9-2 is loosened, and the stopper 7 is moved in the front-rear direction, thereby facilitating the repair. Meanwhile, the above connection mode can steplessly adjust the distance between the two stop surfaces 7-1, thereby conveniently adjusting the gap between the rotation-stopping piece 6 and the stop surface 7-1, and facilitating the adjustment.

[0078] In another embodiment, as shown in the drawings, Figures 3-11 The stopper 7 can also be only one, and the stopper 7 includes a bottom plate and two vertical plates arranged on the upper surface of the bottom plate, the two vertical plates form a slot for inserting the rotation-stopping piece 6, the two slot side walls (i.e. the two plate surfaces of the two vertical plates arranged opposite to each other) arranged opposite to each other in the circumference of the bearing seat 2 form the stop surfaces 7-1, and the internal space of the slot (i.e. the space between the two vertical plates) forms the avoiding space 10.

[0079] Of course, the stopper 7 can also be directly formed by digging a groove on the cuboid base, and the groove forms a slot with four side walls. During installation, the rotation stopper 6 is inserted into the slot, and then the rotation stopper 6 is connected with the bearing seat 2.

[0080] In an embodiment, as shown in Figures 3-10 and Figure 12 , the rotation stopper 6 is in a “T-shaped” structure, and the rotation stopper 6 includes a horizontal plate 6-1 and a vertical plate 6-2 which is perpendicular to the horizontal plate 6-1 and is connected to the horizontal plate 6-1. The horizontal plate 6-1 is connected to the bearing seat 2, and the vertical plate 6-2 is inserted between the two stopper surfaces 7-1 for circumferential stoppage with the stopper surfaces 7-1. The horizontal plate 6-1 is essentially a flange plate, so that the rotation stopper 6 is flange-connected with the bearing seat 2, which is simple in structure and convenient to install.

[0081] In other embodiments, the rotation stopper 6 can also be a cuboid cantilever, and the rotation stopper 6 and the bearing seat 2 can be fixedly connected by welding or the like, or the rotation stopper 6 can be integrally formed with the seat body of the bearing seat 2.

[0082] In Figures 3-12 the embodiment, the radial loading device is arranged above the bearing seat 2, the rotation stopper 6 is arranged at the bottom of the outer circumferential surface of the bearing seat 2, and therefore the stopper 7 is arranged below the bearing seat 2. In other embodiments, the rotation stopper 6 can also be arranged at the front end or the rear end of the bearing seat 2, and the rotation stopper 6 is arranged horizontally along the front-rear direction, and the stopper 7 is correspondingly arranged in front of or behind the bearing seat 2. Alternatively, the radial loading device is arranged below the bearing seat 2, the rotation stopper 6 is arranged at the top of the bearing seat 2, and the stopper 7 is arranged above the bearing seat 2. Of course, the stopper 7 can also be connected to the left and right sides of the bearing seat 2 (and can be connected to the end cover of the bearing seat 2), and the stopper 7 is correspondingly arranged on the left and right sides of the bearing seat 2.

[0083] Preferably, the radial loading device and the rotation stopper 6 are symmetrically arranged in the up-down direction or the front-rear direction, so that the force on the bearing seat 2 is more uniform.

[0084] The embodiment of the bearing measurement method provided by the application is as follows:

[0085] The bearing measuring method provided by the application is: any one of the bearing measuring device embodiments of the application is used for measurement, in the measurement, the bearing 3 installed in the bearing seat 2 is driven to rotate by the main shaft 1, and the initial load F0 is applied to the bearing seat 2 by the loading device 4, so as to indirectly apply the axial load and / or radial load to the bearing 3, when the bearing 3 is driven to rotate by the main shaft 1, the rotation of the bearing seat 2 is limited by the limiting stop cooperation between the rotation stopping piece 6 and the limiting surface 7-1, so as to limit the rotation of the bearing seat 2 by limiting the rotation stopping piece 6; the friction force f between the rotation stopping piece 6 and the stop surface 7-1 is measured by the force sensor 5, and the load applied by the loading device 4 is adjusted to F0+f in real time. At this time, the bearing measuring method corresponds to the third compensation method in the above, which will not be repeated here.

[0086] Of course, during the measurement, the compensation constant f0 can also be determined according to the fluctuation curve of the friction force f, and the load applied by the loading device 4 is fixed to F0+f0. At this time, the bearing measuring method corresponds to the second compensation method in the above, which will not be repeated here.

[0087] Finally, it should be pointed out that the above-mentioned is only the preferred embodiment of the application, and is not used to limit the application, although the application has been described in detail with reference to the foregoing embodiments, for those skilled in the art, the technical solutions recorded in the foregoing embodiments can be modified without creative labor, or some technical features can be replaced, or different embodiments can be combined organically, so as to combine the embodiments given in the drawings, of course, those skilled in the art can also combine the embodiments not given in the drawings of the remaining specification. Any modification, equivalent replacement, improvement, etc. within the spirit and principles of the application shall be included in the protection scope of the application.

Claims

1. A bearing measuring device, comprising a PLC automatic control module, a spindle for driving the bearing to rotate, a bearing housing mounted on the spindle for mounting the bearing to be measured, and a loading device for applying radial and / or axial loads to the bearing housing, characterized in that, It also includes a stop for fixing the bearing in place when it rotates, and an anti-rotation element that moves synchronously with the bearing housing is connected to the outer surface of the bearing housing. In the circumferential direction of the bearing housing, the stop member has a stop surface, which is located on both sides of the anti-rotation member. The anti-rotation member is inserted between the two stop surfaces to stop and engage with the stop surfaces circumferentially. There are two stop members, which are respectively arranged on both sides of the anti-rotation member. The surfaces of the two stop members arranged facing each other constitute the stop surface. Alternatively, the stop member is provided with a slot for the anti-rotation member to be inserted. The slot and the two groove sidewalls of the circumferential stop of the anti-rotation member constitute the stop surface. The stop surfaces on both sides of the anti-rotation component are in clearance fit with the anti-rotation component when the spindle is not rotating. This is used to limit the circumferential rotation and circumferential rotation tendency of the bearing housing through the anti-rotation surface, and to provide clearance space for avoiding the axial and radial movement paths of the anti-rotation component. The bearing housing is equipped with a force sensor for measuring the friction between the anti-rotation component and the stop surface. The PLC automatic control module is used to collect the data measured by the force sensor in real time and compensate the load output by the loading device based on the value of the data measured by the force sensor.

2. The bearing measuring device as described in claim 1, characterized in that, The coefficient of friction μ between the anti-rotation component and the stop surface is less than 0.

1.

3. The bearing measuring device as described in claim 1 or 2, characterized in that, The stop includes a stop body and an elastic buffer layer disposed on the side of the stop body near the anti-rotation component when in use. The surface of the elastic buffer layer that contacts the anti-rotation component forms the stop surface to reduce the vibration between the anti-rotation component and the bearing housing.

4. The bearing measuring device as described in claim 1, characterized in that, The bearing measuring device includes a mounting base located below the spindle. The mounting base has a sliding groove, the extension direction of which is perpendicular to the axial direction of the spindle. The sliding groove includes a stop groove and a bolt groove. The stop groove slides in a guide-sliding fit with the stop. A bolt passes through the stop. The bolt groove includes a bolt head groove and a connecting hole located above the bolt head groove and connecting the bolt head groove and the stop groove. The cross-sectional area of ​​the connecting hole is smaller than the cross-sectional area of ​​the bolt head. The bolt head slides in a guide-sliding fit with the bolt head groove. After the bolt passes through the stop, a nut is connected to it so that the stop is fixed to the mounting base by the bolt and nut after the stop slides into place.

5. The bearing measuring device as described in claim 1 or 2, characterized in that, The anti-rotation component has a "T-shaped" structure, which includes a horizontal plate and a vertical plate perpendicular to the horizontal plate. The vertical plate is connected to the horizontal plate, and the horizontal plate is connected to the bearing seat. The vertical plate is inserted between the two stop surfaces for circumferential stop engagement with the stop surfaces.

6. The bearing measuring device as described in claim 1 or 2, characterized in that, The anti-rotation component is connected to the outer circumferential surface of the bearing housing, and the force sensor is located between the anti-rotation component and the bearing housing.

7. The bearing measuring device as described in claim 1 or 2, characterized in that, The PLC automatic control module is used to increase the load output by the loading device by the value measured by the force sensor, based on the initial value.

8. A bearing measurement method, comprising measuring using a bearing measuring device, rotating the bearing to be measured mounted in a bearing housing using a spindle, and applying an initial load F0 to the bearing housing using a loading device to indirectly apply axial and / or radial loads to the bearing, characterized in that, The bearing measuring device is any one of claims 1 to 6. When the spindle drives the bearing to rotate, the anti-rotation component engages with the stop surface in the circumferential direction of the bearing housing. This restricts the circumferential rotation and circumferential rotation tendency of the bearing housing by limiting the anti-rotation component, thereby reducing the high-frequency vibration caused by the circumferential rotation tendency of the bearing housing. The frictional force f between the anti-rotation component and the stop surface is measured by a force sensor, and the load applied by the loading device is adjusted to F0+f in real time. Alternatively, a compensation setpoint f0 is determined based on the fluctuation curve of the frictional force f, and the load applied by the loading device is fixed to F0+f0.

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