Milling machine main shaft dynamic balance testing device

Abstract

The invention relates to a milling machine spindle dynamic balance testing device, which relates to the field of mechanical balance testing, and comprises a magneto-rheological damper array arranged around a spindle, a sensing assembly used for collecting multi-source vibration signals, a double-closed-loop control mechanism and a chuck assembly, the magneto-rheological damper array comprises a plurality of damping units which are evenly distributed in the circumferential direction of the main shaft, an acute included angle is formed between the force application direction of each damping unit and the axis of the main shaft, and the sensing assembly comprises an axial acceleration sensor located on the end face of the main shaft and a plurality of radial acceleration sensors distributed in the axis direction of the main shaft. The double-closed-loop control mechanism comprises an inner ring damping control unit and an outer ring counterweight decision-making unit, and the chuck assembly is matched with the main shaft positioning conical surface. The method and the device have the effects of realizing active suppression of high-frequency vibration and rapid identification of the unbalance amount.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of mechanical balance testing, in particular to a milling machine spindle dynamic balance testing device. BACKGROUND

[0002] At present, in the field of high-speed milling machines, spindle dynamic balance testing technology is crucial to ensure machining precision and efficiency. With the continuous development of industrial manufacturing, the precision and speed requirements of milling machines are becoming higher and higher, and the stable operation of the spindle at high speed has become a key factor. Good spindle dynamic balance can reduce vibration, reduce noise, prolong tool life, improve the quality of the machined surface, and thus improve the efficiency of the entire production process and the quality of the product.

[0003] In traditional high-speed milling machine spindle dynamic balance testing, a passive damping method is usually used to deal with vibration problems. One common method is to use a general damper, which absorbs and dissipates vibration energy through its physical properties, but the damping force is fixed and cannot be adjusted in real time according to the vibration situation. Another common method is to rely on workers' experience to manually add or remove weight blocks on the spindle to try to achieve balance, but this method is highly subjective and lacks precise quantitative basis. Another method is to use traditional sensors for vibration monitoring, which can only collect a single type of signal, and the information obtained is not comprehensive, making it difficult to accurately analyze complex vibration situations. Moreover, traditional testing methods often require multiple repeated tests and adjustments, resulting in a long testing period.

[0004] In view of the above related technologies, the traditional passive damping method has obvious defects. It is difficult to effectively suppress wideband vibration, and its suppression ability for high-frequency vibration is particularly limited, which cannot meet the vibration control requirements of high-speed milling machines in a wide frequency range. Moreover, the testing process relies on human experience, which not only has a long testing period and low efficiency, but also is prone to inaccurate test results due to human factors, and cannot achieve active suppression of high-frequency vibration and intelligent identification of unbalance. SUMMARY

[0005] In order to achieve active suppression of high-frequency vibration and rapid identification of unbalance, the present application provides a milling machine spindle dynamic balance testing device.

[0006] The present application provides a milling machine spindle dynamic balance testing device, which adopts the following technical solutions: The application discloses a milling machine spindle dynamic balance testing device, which comprises a magnetorheological damper array arranged around a spindle, a sensing assembly for collecting multi-source vibration signals, a double closed loop control mechanism and a chuck assembly, the magnetorheological damper array comprises a plurality of damping units arranged uniformly along the circumference of the spindle, the force applying direction of each damping unit forms an acute angle with the spindle axis, the sensing assembly comprises an axial acceleration sensor located on the end surface of the spindle and a plurality of radial acceleration sensors arranged along the direction of the spindle axis, the double closed loop control mechanism comprises an inner ring damping control unit and an outer ring counterweight decision unit, and the chuck assembly is matched with the positioning conical surface of the spindle.

[0007] By adopting the technical scheme, the magnetorheological damper array is arranged around the spindle, the plurality of damping units arranged uniformly along the circumference of the spindle and having the force applying direction forming an acute angle with the spindle axis can apply damping force to the spindle from multiple angles, can effectively offset the vibration components of specific frequencies, can realize active vibration suppression in a wide frequency band, and can expand the testing rotating speed range. The sensing assembly can synchronously collect the acceleration signals of the spindle in the axial and radial directions, the inner ring damping control unit and the outer ring counterweight decision unit in the double closed loop control mechanism are combined, the energy distribution of the characteristic frequency band is extracted by adopting a wavelet packet transform algorithm through fusion analysis of the multi-source vibration signals, a mapping relationship database of the vibration mode and the unbalance amount is established, the unbalance amount can be quickly identified within 10 seconds, and the detection efficiency is improved. The chuck assembly is matched with the positioning conical surface of the spindle, adopts a standardized hydraulic quick-change chuck interface, can reduce the coaxiality error of the spindle with different diameters, and can reduce the spindle replacement time.

[0008] Optionally, the sensing assembly further comprises an optical encoder fixed on the end of the spindle and a rotating speed sensor arranged at the tail end of the spindle, and the signal output end of the optical encoder is connected with the double closed loop control mechanism.

[0009] By adopting the technical scheme, the optical encoder is arranged at the end of the spindle and the rotating speed sensor is arranged at the tail end of the spindle, and the signal output end of the optical encoder is connected with the double closed loop control mechanism, so that the double closed loop control mechanism can obtain more comprehensive multi-source vibration signals. The optical encoder can accurately capture the rotating position and angle information of the spindle, and the rotating speed sensor can measure the rotating speed of the spindle in real time, and the signals are transmitted to the double closed loop control mechanism. The double closed loop control mechanism can analyze and process the accurate information, can more accurately understand the running state of the spindle, can help improve the calculation accuracy of the mapping relationship between the vibration mode and the unbalance amount, and can realize more accurate damping force regulation and counterweight decision, thereby improving the identification and correction capability of the whole milling machine spindle dynamic balance testing device on the unbalance amount of the spindle, and guaranteeing the accuracy and efficiency of the spindle dynamic balance testing.

[0010] Optionally, the inner ring damping control unit comprises an adjusting module for feeding back the vibration acceleration signals in real time, and the outer ring counterweight decision unit comprises a data processing module for storing vibration mode parameters.

[0011] By adopting the technical scheme, the adjusting module of the inner ring damping control unit can feed back the vibration acceleration signal in real time, can dynamically adjust the damping force size and direction of each damping unit in the magnetorheological damper array in a timely manner according to the vibration condition, can counteract the vibration component of a specific frequency in a targeted manner, can realize active vibration suppression in a wide frequency band, and can expand the rotating speed range of the test.

[0012] Optionally, the adjusting module is electrically connected with a power supply circuit of the magnetorheological damper array, and the data processing module is connected with a counterweight execution mechanism through a communication interface.

[0013] By adopting the technical scheme, the adjusting module is electrically connected with the power supply circuit of the magnetorheological damper array, the power supply of the magnetorheological damper array can be adjusted in real time according to the vibration acceleration signal, the magnetic field strength generated by the magnetorheological damper is changed, the damping force size and direction are dynamically adjusted, the vibration component of a specific frequency is counteracted in a targeted manner, and active suppression of high-frequency vibration is realized; the data processing module is connected with the counterweight execution mechanism through the communication interface, the counterweight scheme can be automatically generated and output to the counterweight execution mechanism for correction based on the stored vibration modal parameters and the historical data matching model, intelligent rapid identification of unbalance is realized, and the dynamic balance test efficiency is effectively improved.

[0014] Optionally, the chuck assembly comprises a hydraulic chuck, a plurality of clamping jaws radially slidingly connected to the hydraulic chuck, a taper sleeve sleeved at one end of the clamping jaw away from the axis of the hydraulic chuck and forming an interference fit with the main shaft positioning taper surface, and a pressure monitoring element arranged at the root of the clamping jaw.

[0015] By adopting the technical scheme, the hydraulic chuck and the clamping jaws radially slidingly connected thereto can effectively clamp the main shaft; the taper sleeve sleeved at one end of the clamping jaw away from the axis of the hydraulic chuck and forming an interference fit with the main shaft positioning taper surface can further enhance the positioning and clamping effect of the main shaft, and ensure the stability of the main shaft installation; the pressure monitoring element arranged at the root of the clamping jaw can monitor the clamping force of the clamping jaw on the main shaft in real time, and the main shaft positioning taper self-calibration function integrated with the standardized hydraulic quick-change chuck interface is adopted.

[0016] Optionally, a signal output end of the pressure monitoring element is connected to a double-closed-loop control mechanism, and a through-type wire channel is arranged in a wiring groove of the chuck assembly.

[0017] By adopting the technical scheme, the signal output end of the pressure monitoring element is connected to the double closed-loop control mechanism, the pressure signal of the jaw root can be fed back to the double closed-loop control mechanism in real time, the double closed-loop control mechanism can accurately regulate the test process according to the pressure condition, and reliable clamping of the main shaft is ensured; and the through lead channel arranged in the wiring groove of the chuck assembly can make the line layout more regular and orderly, avoid faults caused by disordered lines, facilitate maintenance and repair of the lines, and improve the stability and reliability of the entire test device.

[0018] Optionally, it further comprises a ring-shaped mounting bracket surrounding the magneto-rheological damper array, and the ring-shaped mounting bracket is provided with a rigid connection structure matched with the base of the damping unit.

[0019] By adopting the technical scheme, the ring-shaped mounting bracket surrounding the magneto-rheological damper array is arranged, and the ring-shaped mounting bracket is provided with a rigid connection structure matched with the base of the damping unit, which can provide a stable and reliable support and mounting base for the magneto-rheological damper array, ensure the stability of the damping unit installation, enhance the stability of the overall structure of the device, avoid the position deviation or loosening of the damping unit caused by vibration or external factors, and thus ensure the stable play of the vibration suppression effect of the magneto-rheological damper array on the main shaft, which is conducive to effectively suppressing the active vibration of the main shaft in a wide frequency band.

[0020] Optionally, the rigid connection structure comprises a mounting base and a plurality of self-locking bolts, the self-locking bolts are threadedly connected with the ring-shaped mounting bracket through the mounting base, and the mounting base is adjustably connected with the ring-shaped mounting bracket.

[0021] By adopting the technical scheme, the mounting base and the ring-shaped mounting bracket in the rigid connection structure are adjustably connected, so that the position and angle between the magneto-rheological damper array and the ring-shaped mounting bracket can be flexibly adjusted according to actual needs, the adaptability and flexibility of the device installation are enhanced, and the device can better adapt to main shafts and test environments of different specifications; meanwhile, the self-locking bolts are threadedly connected with the ring-shaped mounting bracket through the mounting base, this connection mode has good fastening and stability, can ensure that the magneto-rheological damper array is stably mounted on the ring-shaped mounting bracket, effectively prevents the loosening from affecting the test results during the test process, and thus ensures the reliable operation of the entire milling machine main shaft dynamic balance test device, and provides a stable hardware foundation for high-precision dynamic balance test.

[0022] Optionally, the mounting base comprises a base plate and an angle encoder, the base plate is provided with a plurality of waist-shaped holes corresponding to the self-locking bolts one by one, the self-locking bolts are threadedly connected with the ring-shaped mounting bracket through the corresponding waist-shaped holes, and the angle encoder is embedded at one end of the base plate close to the damping unit.

[0023] By adopting the technical scheme, the mounting base comprises a base plate with a waist-shaped hole and an angle encoder, and a self-locking bolt is screwed with the annular mounting frame through the waist-shaped hole, so that the mounting base and the annular mounting frame can be connected in an adjustable manner, the installation position and angle can be flexibly adjusted according to actual conditions, and the installation requirements of the magnetorheological damper array can be better adapted. Meanwhile, the angle encoder embedded in the base plate near one end of the damping unit can accurately measure the installation angle of the damping unit, provide reliable angle data support for accurate vibration suppression of the equipment, and be beneficial to more accurately exert the vibration reduction effect of the magnetorheological damper array and improve the stability and test precision of the whole milling machine spindle dynamic balance testing device.

[0024] In summary, the present application has at least one of the following beneficial technical effects: 1. The magnetorheological damper array arranged around the main shaft, each damping unit of which can change the magnetic field strength through real-time current adjustment, dynamically adjust the damping force size and direction, and counteract the vibration components of specific frequencies, so as to realize wide-band active vibration suppression and expand the test speed range; 2. The sensing assembly synchronously collects the main shaft axial and radial acceleration signals, the speed pulse signal and the phase reference signal, the multi-source vibration signals are intelligently processed through the double closed-loop control mechanism, the wavelet packet transform algorithm is used to extract the energy distribution of the characteristic frequency band and establish the mapping relationship database of the vibration mode and the unbalance, so as to realize rapid identification of the unbalance in a short time and improve the efficiency compared with the traditional method; 3. The chuck assembly adopts a standardized hydraulic quick-change chuck interface and integrates a main shaft positioning taper self-calibration function, the uniformity of the clamping force is monitored through a pressure sensor, the coaxiality error of the main shafts with different diameters is reduced, and the main shaft replacement time is reduced. BRIEF DESCRIPTION OF DRAWINGS

[0025] Figure 1 Fig. 1 is a schematic diagram of the overall structure of the milling machine spindle dynamic balance testing device.

[0026] Figure 2 Fig. 2 is an enlarged schematic diagram of part A in Fig. 1. Figure 1

[0027] Figure 3 Fig. 3 is a structural schematic diagram of the main shaft and the sensing assembly.

[0028] Figure 4 Fig. 4 is a structural schematic diagram of the chuck assembly.

[0029] ​The reference signs are explained as follows: 100, main shaft; 1, damping unit; 2, sensing assembly; 21, axial acceleration sensor; 22, radial acceleration sensor; 23, photoelectric encoder; 24, rotating speed sensor; 3, annular mounting bracket; 4, chuck assembly; 41, hydraulic chuck; 42, chuck jaw; 43, taper sleeve; 44, pressure monitoring element; 5, rigid connection structure; 51, mounting base; 511, base plate; 512, angle encoder; 513, waist-shaped hole; 52, self-locking bolt; 6, double closed-loop control mechanism. DETAILED DESCRIPTION

[0030] The application will be further described in detail below with reference to all the drawings.

[0031] The application discloses a milling machine main shaft dynamic balance testing device.

[0032] Reference Figure 1 A milling machine main shaft dynamic balance testing device comprises a magneto-rheological damper array arranged around a main shaft 100, a sensing assembly 2 for collecting multi-source vibration signals, a double closed-loop control mechanism 6, and a chuck assembly 4. The magneto-rheological damper array is arranged around the main shaft 100 and can actively suppress vibration of the main shaft 100. The sensing assembly 2 is responsible for collecting various vibration signals of the main shaft 100 and provides data support for subsequent analysis. The double closed-loop control mechanism 6 calculates and makes decisions based on the data collected by the sensing assembly 2, thereby achieving precise control of vibration. The chuck assembly 4 is used to quickly and accurately install the main shaft 100, thereby ensuring the coaxiality of the main shaft 100. Such a combination achieves the effect of efficiently and accurately testing the dynamic balance of the milling machine main shaft 100. Through the wideband active vibration suppression of the magneto-rheological damper, the intelligent signal processing system, and the standardized interface, the shortcomings of the traditional testing method are overcome, the testing efficiency and accuracy are improved, and the device is suitable for mass production line detection scenarios.

[0033] Reference Figure 1 and Figure 2 The magneto-rheological damper array comprises a plurality of damping units 1 arranged uniformly in the circumferential direction of the main shaft 100. The force application direction of each damping unit 1 forms an acute angle with the axis of the main shaft 100. Taking six groups of independently controlled damping units 1 arranged around the main shaft 100 as an example, the damping units 1 can use magneto-rheological fluid as the working medium. Magneto-rheological fluid is an intelligent material, and its rheological properties can be quickly and reversibly controlled by an external magnetic field. For example, when an electric current passes through the coil of the damping unit 1, a magnetic field is generated, which changes the viscosity of the magneto-rheological fluid and thus changes the size and direction of the damping force. The damping units 1 here can also be replaced by a new type of controllable fluid damper, such as an electro-rheological fluid damper, which can also control the damping force through an electric field.

[0034] Reference Figure 2The damping unit 1 is characterized by a coil winding inside for generating a magnetic field and a shell outside for protection. The installation method is fixed through the annular mounting bracket 3, which is provided with a rigid connection structure 5 matched with the base of the damping unit 1. The rigid connection structure 5 includes a mounting base 51 and a plurality of self-locking bolts 52, which are threadedly connected with the annular mounting bracket 3 through the mounting base 51, and the mounting base 51 is adjustably connected with the annular mounting bracket 3. The mounting base 51 includes a base plate 511 and an angle encoder 512, the base plate 511 is provided with a plurality of waist-shaped holes 513 corresponding to the self-locking bolts 52, the self-locking bolts 52 are threadedly connected with the annular mounting bracket through the corresponding waist-shaped holes 513, and the angle encoder 512 is embedded in one end of the base plate 511 close to the damping unit 1. This installation method makes the damping unit 1 convenient to adjust the position and angle to adapt to different test requirements. The angle encoder 512 functions to monitor the angle position of the damping unit 1 in real time and provide feedback for accurate control. Specifically, the operator can first loosen the self-locking bolts 52, so that the mounting base 51 has a certain freedom on the annular mounting bracket 3, then adjusts the damping unit 1 to the appropriate position and angle according to the actual test requirements, and then tightens the self-locking bolts 52 to fix the damping unit 1. The angle encoder 512 will record the angle information of the damping unit 1 in real time and feed back the information to the control system, so that the control system can accurately control according to the actual angle of the damping unit 1.

[0035] Referring to Figure 1 The plurality of damping units 1 are uniformly arranged along the circumference of the main shaft 100, which can suppress the vibration of the main shaft 100 from multiple directions. They work together to adjust the damping force according to different vibration frequencies and directions, thereby effectively canceling the vibration components of specific frequencies. This combination logic enables the magneto-rheological damper array to achieve wide-band active vibration suppression, expanding the test speed range to 300-18000 rpm.

[0036] Referring to Figure 1 and Figure 3, The main shaft 100 in the application has a conical frustum at one end, and the sensing assembly 2 includes an axial acceleration sensor 21 located on the end face of the conical frustum of the main shaft 100 and a plurality of radial acceleration sensors 22 arranged along the axial direction of the main shaft 100. The axial acceleration sensor 21 is fixed in a central groove on the end face of the main shaft 100, and the axial acceleration sensor 21 is threadedly connected with the main shaft 100. The axial acceleration sensor 21 is used to collect the axial vibration acceleration signal of the main shaft 100. The radial acceleration sensors 22 are fixedly connected to the annular mounting bracket 3, and the radial acceleration sensors 22 collect the radial vibration acceleration signal of the main shaft 100. The axial acceleration sensor 21 is generally a piezoelectric accelerometer, which has the advantages of high sensitivity and fast response speed. In some special cases, a strain accelerometer can also be used. The radial acceleration sensors 22 are arranged along the axial direction of the main shaft 100, so that the radial vibration signals of the main shaft 100 can be collected from different positions, improving the comprehensiveness of signal collection.

[0037] With reference to Figure 3 , The sensing assembly 2 further includes an optical encoder 23 fixed to the end of the main shaft 100 and a rotational speed sensor 24 arranged at the tail end of the main shaft 100. The signal output end of the optical encoder 23 is connected with the double-closed-loop control mechanism 6. The optical encoder 23 is fixedly connected to the conical frustum end face of the main shaft 100, and the optical encoder 23 can accurately measure the rotational speed and phase of the main shaft 100. The rotational speed sensor 24 monitors the rotational speed of the main shaft 100 in real time. Together with the acceleration sensors, they synchronously collect the axial / radial acceleration signals, rotational speed pulse signals and phase reference signals of the main shaft 100. For example, during the rotation of the main shaft 100, the axial acceleration sensor 21 collects the axial vibration acceleration of the main shaft 100 in real time, the radial acceleration sensors 22 collect the radial vibration acceleration at different positions of the main shaft 100, the optical encoder 23 accurately measures the rotational speed and phase of the main shaft 100 by reading the code disc signal at the end of the main shaft 100, and the rotational speed sensor 24 obtains the rotational speed of the main shaft 100 in real time by sensing the rotating part at the tail end of the main shaft 100. These signals are synchronously transmitted to the double-closed-loop control mechanism 6, providing comprehensive data support for subsequent analysis. The magnetic attraction seat of the rotational speed sensor 24 is fixed to the eccentric position of the end face of the main shaft 100 away from the conical frustum, which facilitates the installation and removal of the sensor and ensures the stability of the sensor.

[0038] The multi-source vibration signals collected by the sensors are transmitted to the double-closed-loop control mechanism 6, the wavelet packet transform algorithm is used to extract the energy distribution of the characteristic frequency band, and the mapping relationship database of the vibration mode and the unbalance amount is established. In this way, the vibration of the main shaft 100 can be more comprehensively and accurately analyzed, providing a basis for subsequent control.

[0039] With reference to Figure 1The double closed-loop control module is fixed in the control box on the outer wall of the annular mounting frame, and the double closed-loop control mechanism 6 includes an inner ring damping control unit and an outer ring counterweight decision unit. The inner ring damping control unit includes an adjustment module that feeds back the vibration acceleration signal in real time, and the adjustment module is electrically connected with the power supply circuit of the magnetorheological damper array. When the vibration acceleration signal collected by the sensing assembly 2 is fed back to the adjustment module, the adjustment module calculates the required damping force according to the preset algorithm, and adjusts the damping force of the magnetorheological damper in real time by adjusting the current of the power supply circuit, so as to realize real-time regulation and control of vibration. For example, when the vibration acceleration signal shows that the vibration of the main shaft 100 is large, the adjustment module will increase the current of the power supply circuit, so that the damping force of the magnetorheological damper is increased, thereby inhibiting the vibration of the main shaft 100; on the contrary, when the vibration is small, the adjustment module will reduce the current to reduce the damping force.

[0040] The outer ring counterweight decision unit includes a data processing module for storing vibration modal parameters fixed on the inner wall of the control box, and the data processing module is connected with the counterweight execution mechanism through a communication interface. The data processing module automatically generates a counterweight scheme based on a historical data matching model and outputs the counterweight scheme to the numerical control counterweight mechanical arm for correction. For example, when the data processing module analyzes that the main shaft 100 has an unbalance amount, it will calculate the position and weight of the counterweight block to be added or reduced according to the mapping relationship in the database, and then send the counterweight scheme to the numerical control counterweight mechanical arm. The mechanical arm operates according to the scheme to correct the unbalance amount of the main shaft 100. Specifically, the data processing module compares the collected vibration signal with the vibration modal in the database to find the most matched vibration modal, and then calculates the required counterweight block position and weight according to the unbalance amount information corresponding to the modal. Then, the counterweight scheme is sent to the numerical control counterweight mechanical arm through the communication interface. After receiving the scheme, the mechanical arm will automatically move to the specified position and install or remove the corresponding counterweight block. This double closed-loop control architecture enables the system to accurately control vibration and quickly correct unbalance amount. The intelligent signal processing system can quickly identify the unbalance amount within 10 seconds, which is 60% more efficient than traditional methods.

[0041] Referring to Figure 1 and Figure 4, the chuck assembly 4 is provided with a clamping mechanism matched with the positioning taper surface of the main shaft 100. The clamping mechanism includes a hydraulic chuck 41, a plurality of clamping jaws 42 radially slidingly connected with the hydraulic chuck 41, a taper sleeve 43 sleeved at one end of the clamping jaw 42 away from the axis of the hydraulic chuck 41, and a pressure monitoring element 44 arranged at the root of the clamping jaw 42, and the taper surface of the taper sleeve 43 is in interference fit with the positioning taper surface of the main shaft 100. Taking the example of four clamping jaws 42 evenly distributed on the hydraulic chuck 41, the hydraulic chuck 41 is powered by a hydraulic system, so that the clamping jaw 42 can quickly and firmly clamp the main shaft 100. The clamping jaw 42 can slide along the radial direction of the hydraulic chuck 41 to adapt to different diameters of the main shaft 100. When the main shaft 100 needs to be installed, the hydraulic system pushes the clamping jaw 42 to slide outward, so that the clamping jaw 42 is opened, and after the main shaft 100 is put in, the hydraulic system reversely pushes the clamping jaw 42 to slide inward, and the clamping jaw 42 gradually clamps the main shaft 100. At the same time, the taper surface of the taper sleeve 43 closely matches the positioning taper surface of the main shaft 100, and since the two are in interference fit, the installation gap can be eliminated, further ensuring the coaxiality of the main shaft 100 installation.

[0042] The pressure monitoring element 44 can adopt a pressure sensor for monitoring the uniformity of the clamping force of the clamping jaw 42. The signal output end of the pressure monitoring element 44 is connected to a double closed loop control mechanism 6, which can issue instructions for adjustment when the clamping force is found to be uneven. For example, if the pressure detected by the pressure sensor of a certain clamping jaw 42 differs greatly from that of other clamping jaws 42, it indicates that the clamping force of the clamping jaw 42 is uneven, and the double closed loop control mechanism 6 will adjust the pressure of the hydraulic system according to the signal to make the clamping force of each clamping jaw 42 tend to be uniform. The through-type wire channel is arranged in the wiring groove of the clamping mechanism for arranging the sensor and control circuit, so that the wiring of the entire device is more orderly and reasonable. For example, the signal line of the pressure sensor and the control line for controlling the action of the clamping jaw 42 can be arranged through the through-type wire channel to avoid disorderly wiring and reduce interference. The use of standardized hydraulic quick-change chuck interface and integrated main shaft 100 positioning taper self-calibration function, combined with the monitoring of the pressure sensor, ensures that the coaxiality error of the main shaft 100 installation of different diameters is ≤0.005mm, and the main shaft 100 replacement time is controlled within 3 minutes, which is also applicable to mass production line detection scenarios.

[0043] The implementation principle of the embodiment is that the milling machine spindle 100 dynamic balance testing device overcomes the defects of the traditional testing method through the cooperative work of each component. The magnetorheological damper array utilizes the characteristics of magnetorheological fluid to achieve wideband active suppression of the spindle 100 vibration, and expands the test speed range. The sensor assembly 2 collects multi-source vibration signals to provide comprehensive data support for the double closed loop control mechanism 6. The double closed loop control mechanism 6 realizes real-time regulation and control of vibration and rapid correction of unbalance through accurate calculation and decision making. The chuck assembly 4 ensures the rapidity and accuracy of the spindle 100 installation. Overall, it improves the testing efficiency and accuracy, and is suitable for mass production line detection, which greatly improves and contributes to the existing technology.

[0044] The above are preferred embodiments of the present application, but do not limit the protection scope of the present application, therefore: any equivalent changes made according to the structure, shape, principle of the present application should be covered within the protection scope of the present application.

Claims

1. A dynamic balancing testing device for a milling machine spindle, characterized in that: The system includes a magnetorheological damper array arranged around the main shaft (100), a sensing component (2) for collecting multi-source vibration signals, a dual closed-loop control mechanism (6), and a chuck assembly (4). The magnetorheological damper array includes several damping units (1) evenly arranged around the main shaft (100). The force direction of each damping unit (1) forms an acute angle with the axis of the main shaft (100). The sensing component (2) includes an axial acceleration sensor (21) located on the end face of the main shaft (100) and several radial acceleration sensors (22) arranged along the axis of the main shaft (100). The dual closed-loop control mechanism (6) includes an inner ring damping control unit and an outer ring counterweight decision unit. The chuck assembly (4) is engaged with the positioning cone surface of the main shaft (100).

2. The milling machine spindle dynamic balancing test device according to claim 1, characterized in that: The sensing component (2) also includes a photoelectric encoder (23) fixed at the end of the spindle (100) and a speed sensor (24) set at the tail end of the spindle (100). The signal output end of the photoelectric encoder (23) is connected to the dual closed-loop control mechanism (6).

3. The milling machine spindle dynamic balancing test device according to claim 1, characterized in that: The inner ring damping control unit includes an adjustment module that provides real-time feedback of vibration acceleration signals, and the outer ring counterweight decision unit includes a data processing module that stores vibration modal parameters.

4. The milling machine spindle dynamic balancing test device according to claim 3, characterized in that: The adjustment module is electrically connected to the power supply circuit of the magnetorheological damper array, and the data processing module is connected to the counterweight actuator through a communication interface.

5. The milling machine spindle dynamic balancing test device according to claim 1, characterized in that: The chuck assembly (4) includes a hydraulic chuck (41), a plurality of jaws (42) that are slidably connected to the chuck along the radial direction of the hydraulic chuck (41), a tapered sleeve (43) sleeved on one end of the jaw (42) away from the axis of the hydraulic chuck (41), and a pressure monitoring element (44) disposed at the root of the jaw (42). The tapered surface of the tapered sleeve (43) forms an interference fit with the positioning tapered surface of the spindle (100).

6. The milling machine spindle dynamic balancing test device according to claim 5, characterized in that: The signal output terminal of the pressure monitoring element (44) is connected to the dual closed-loop control mechanism (6), and the cable tray assembly (4) has a through-type wire channel in its wiring groove.

7. The milling machine spindle dynamic balancing test device according to claim 1, characterized in that: It also includes an annular mounting bracket (3) surrounding the magnetorheological damper array, the annular mounting bracket (3) having a rigid connection structure (5) that matches the base of the damping unit (1).

8. The milling machine spindle dynamic balancing test device according to claim 7, characterized in that: The rigid connection structure (5) includes a mounting base (51) and several self-locking bolts (52). The self-locking bolts (52) pass through the mounting base (51) and are threadedly connected to the annular mounting bracket (3). The mounting base (51) and the annular mounting bracket (3) are adjustablely connected.

9. The milling machine spindle dynamic balancing test device according to claim 8, characterized in that: The mounting base (51) includes a base plate (511) and an angle encoder (512). The base plate (511) has several waist-shaped holes (513) that correspond one-to-one with the self-locking bolts (52). The self-locking bolts (52) pass through the corresponding waist-shaped holes (513) and are threadedly connected to the annular mounting bracket. The angle encoder (512) is embedded in one end of the base plate (511) near the damping unit (1).

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