Electromechanical coupling type main shaft working condition dynamic characteristic simulation device and use method

Abstract

The invention discloses an electromechanical coupling type main shaft working condition dynamic characteristic simulation device and a using method, and relates to the technical field of numerical control machine tool performance tests.The electromechanical coupling type main shaft working condition dynamic characteristic simulation device comprises a supporting shell, a simulation cutter handle, a cooling device, a torque loading device, an axial force loading device and a radial force loading device, and the supporting shell comprises a box body and mounting shafts symmetrically distributed on the two sides of the box body; a plurality of groups of U-shaped mounting grooves are formed in the outer side of the box body. By integrating three sets of independent axial force, radial force and torque loading devices, the working conditions of force and torque borne by the main shaft in the cutting process can be simulated in the actual assembly state of the main shaft of the numerical control machine tool, so that the performance test result is closer to the actual machining state; and powerful theoretical and data support is provided for design verification and performance optimization of the main shaft and the whole machine.

Description

Technical Field

[0001] This invention relates to the field of CNC machine tool performance testing technology, specifically to an electromechanical coupled spindle dynamic characteristic simulation device and its usage method. Background Technology

[0002] The dynamic performance of a high-speed electric spindle is a key indicator of its modal characteristics, thermal accuracy, and vibration characteristics. Its dynamic performance directly determines the stability, machining quality, and reliability of the machine tool during high-speed rotation and high-precision machining.

[0003] Currently, most performance testing devices for functional components of high-end CNC machine tools are bench testing devices. These devices typically test individual functional components separately, detached from the integrated mechanical structure and overall working environment of the machine tool. Therefore, they cannot simulate the performance changes of functional components under the influence of multi-load coupling, multi-source vibration transmission, and multi-part thermal deformation. Thus, this paper proposes an electromechanical coupled spindle full-condition dynamic characteristic simulation device and its usage method. Summary of the Invention

[0004] To achieve the above objectives, the present invention provides the following technical solution: an electromechanical coupling type spindle working condition dynamic characteristic simulation device, including a support housing, a simulated tool holder, a cooling device, a torque loading device, an axial force loading device, and a radial force loading device. The support housing includes a box body and mounting shafts symmetrically distributed on both sides of the box body. Multiple sets of U-shaped mounting grooves are provided on the outer side of the box body. The torque loading device includes a planetary joint module installed inside the housing. The output end of the planetary joint module is connected to the bottom of the simulated tool holder via a coupling. The planetary joint module is electrically connected to an external controller. The cooling device includes a water-cooled jacket shell, a water-cooled jacket, and an end cap. The water-cooled jacket is press-fitted inside the water-cooled jacket shell. The simulated tool holder is connected from top to bottom to the bearing retainer ring, a deep groove ball bearing, and an axial lock nut. The central through hole of the water-cooled jacket is interference-fitted with the end cap and the outer ring of the deep groove ball bearing. The end cap rests against the bottom surface of the outer ring of the deep groove ball bearing. Both the axial force loading device and the radial force loading device are installed inside the housing, and are used to apply axial force and perpendicular force to the simulated tool holder, respectively.

[0005] Preferably, multiple guide pillars are fixedly installed inside the housing, and a lifting plate is slidably installed between the multiple guide pillars. The lifting plate is slidably connected to the guide pillars through linear bearings. The position of the lifting plate on the guide pillars is adjusted and locked by threaded fixing rings. The center of the lifting plate is fixedly connected to the water cooling jacket shell. The radial force loading device includes two opposing first cylinders, which are located on both sides of the simulated tool holder and fixedly connected to the housing. A first force sensor is provided at the output end of the first cylinder. One end of the first force sensor is connected to the output end of the first cylinder, and the other end of the first force sensor is fixedly connected to an axial baffle. The two axial baffles are located on both sides of the lifting plate. The first force sensor and the drive device of the first cylinder are electrically connected to an external controller.

[0006] Preferably, the axial force loading device includes a second cylinder fixed to the bottom of the inner side of the housing. The output end of the second cylinder is connected to one end of a second force sensor, and the other end of the second force sensor is connected to a cylinder guide rod. The end of the cylinder guide rod away from the second force sensor is connected to a cylinder floating guide mechanism located at the bottom of the lifting plate. The cylinder floating guide mechanism includes a connecting seat and a connecting plate hinged together. The connecting seat is fixedly connected to the cylinder guide rod, and the connecting plate is fixedly connected to the bottom of the lifting plate. The second force sensor and the driving device of the second cylinder are electrically connected to an external controller.

[0007] Preferably, an axial mounting plate is fixedly provided between multiple guide pillars, and a zipper motor base is fixedly provided on the axial mounting plate. The planetary joint module is fixed on the zipper motor base, and the output end of the planetary joint module is connected to a flange shaft by bolts and positioning pins. The flange shaft is fixedly connected to the coupling.

[0008] Preferably, the planetary joint module includes a servo motor and a planetary reducer. The output end of the servo motor is connected to the input end of the planetary reducer. The output end of the planetary reducer is connected to the flange shaft by bolts and locating pins. A radial support shell is also fixedly installed on the outside of the planetary joint module. The radial support shell is connected and fixed to the housing.

[0009] The present invention also provides a method for using the electromechanical coupling type spindle operating condition dynamic characteristic simulation device, which, when applied to the device as described above, includes the following steps: Step 1: Investigate the parameters of the tested electric spindle under actual use conditions to provide a reference for parameter setting; Step 2: Based on the results of the survey in Step 1, determine the maximum test load, set the test environment conditions, and adjust the working parameters and loading speed of the device accordingly to ensure that they match the actual operating conditions and improve the authenticity of the test environment. Step 3: Start the machine tool under test, turn off the chip removal and cooling system, and run the spindle continuously at 80% of its maximum speed for 2 hours without installing the tool holder and under no load, so as to achieve the thermal equilibrium state of the machine tool. Then, install the simulated tool holder into the tapered hole of the spindle of the machine tool under test and tighten it. Then, use the U-shaped mounting groove on the housing or the mounting shafts on both sides of the housing to firmly install the device on the machine tool worktable or bed. Step 4: After setting the initial load parameters, start the spindle, torque loading device, radial force loading device and axial force loading device of the machine tool under test in sequence. Monitor the data of the first force sensor and the second force sensor and the spindle running status in real time through the external controller. Gradually increase the speed to 80% of the maximum speed of the spindle according to the set gradient, and at the same time gradually increase the radial force and axial force to the maximum test load determined in Step 2. Step 5: If there are no abnormalities during the operation of Step 4, stop the machine tool under test and this device, and use an external rotary accuracy measurement system, ball bar and temperature measuring instrument to determine the initial performance index of the spindle of the machine tool under test in the current state. Step 6: Restart the device and the machine tool under test, and enter the test environment conditions set in Step 2. The device can independently or synchronously control the first cylinder, the second cylinder and the planetary joint module, and simulate the multi-axis coupled load conditions in the real machining process by applying complex dynamic loads to the simulated tool holder.

[0010] The present invention has the following beneficial effects: This invention integrates three independent loading devices for axial force, radial force, and torque, which can simulate the force and torque conditions that the spindle bears during the cutting process under the actual assembly state of the CNC machine tool spindle. This makes the performance test results closer to the actual machining state and provides strong theoretical and data support for the design verification and performance optimization of the spindle and the whole machine.

[0011] This invention reduces the overall size through a modular and integrated support housing design, facilitating transportation and disassembly / installation. By incorporating a U-shaped mounting slot and mounting shaft on the housing, the device can be quickly adapted to machine tool worktables via the U-shaped mounting slot, and can also be installed even without a worktable, thus enabling universal on-machine testing of CNC machine tool spindles with various structures. Attached Figure Description

[0012] Figure 1 This is a schematic diagram of the overall structure of the present invention; Figure 2 This is a schematic diagram of the structure of the present invention after the box body has been removed; Figure 3 This is a schematic diagram of the structure of the housing and mounting shaft in this invention; Figure 4 This is a schematic diagram of the structure of the first cylinder, the first force sensor, and the axial baffle in this invention; Figure 5 This is a schematic diagram of the structure of the water cooling jacket, end cap, and axial locking nut in this invention; Figure 6 This is a schematic diagram of the structure of the second cylinder, the second force sensor, and the cylinder guide rod in this invention; Figure 7This is a schematic diagram of the planetary joint module, radial support housing, and coupling in this invention; Figure 8 This is a schematic diagram of the threaded retaining ring in this invention; Figure 9 This is a schematic diagram of the cylinder floating guide mechanism in this invention.

[0013] In the diagram: 1, simulated tool holder; 2, cylinder nut; 3, planetary joint module; 4, radial support housing; 5, flange shaft; 6, coupling; 7, housing; 8, mounting shaft; 9, first cylinder; 10, first force sensor; 11, axial baffle; 12, zipper motor base; 13, lifting plate; 14, guide post; 15, linear bearing; 16, threaded retaining ring; 17, axial mounting plate; 18, water-cooled jacket housing; 19, water-cooled jacket; 20, end cap; 21, deep groove ball bearing; 22, bearing retaining ring; 23, axial locking nut; 24, second cylinder; 25, second force sensor; 26, cylinder floating guide mechanism; 27, cylinder guide rod. Detailed Implementation

[0014] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0015] The present invention will now be described in further detail with reference to the accompanying drawings and embodiments.

[0016] Embodiments of the present invention: refer to Figures 1 to 7 An electromechanical coupling type spindle working condition dynamic characteristic simulation device includes a support housing, a simulated tool holder 1, a cooling device, a torque loading device, an axial force loading device and a radial force loading device; The supporting housing includes a box body 7 and mounting shafts 8 symmetrically distributed on both sides of the box body 7. The bottom and both end faces of the box body 7 are machined with multiple arrays of U-shaped mounting grooves, which enables the device to achieve quick and rigid connection with various machine tool worktables through standard fixtures, and can also achieve cantilever clamping installation using the mounting shafts 8 on both sides when there is no worktable, thereby enhancing the installation adaptability of the device and improving its versatility and flexibility.

[0017] refer to Figures 1 to 4 as well as Figure 7The housing 7 has four guide pillars 14 fixedly installed inside, and an axial mounting plate 17 is fixedly installed between the four guide pillars 14. The torque loading device includes a zipper motor seat 12 fixedly installed on the axial mounting plate 17. A planetary joint module 3 is fixedly installed on the zipper motor seat 12. The planetary joint module 3 is an integrated electromechanical drive module, which integrates a servo motor and a planetary reducer. The output end of the servo motor is connected to the input end of the planetary reducer. The output end of the planetary reducer (i.e., the output end of the planetary joint module 3) is connected to a flange shaft 5 by bolts and positioning pins. The flange shaft 5 is fixedly connected to a coupling 6. The planetary joint module 3 is connected to the bottom of the simulated tool holder 1 through the coupling 6. When the planetary joint module 3 is working, the servo motor generates torque, which is amplified by the planetary reducer and then applied to the simulated tool holder 1 through the flange shaft 5 and the coupling 6 in sequence. A radial support shell 4 is also fixedly installed outside the planetary joint module 3. The radial support shell 4 is connected and fixedly installed to the housing 7.

[0018] refer to Figures 1 to 5 as well as Figure 8 The cooling device includes a water-cooled jacket shell 18, a water-cooled jacket 19, and an end cap 20. The water-cooled jacket 19 is press-fitted inside the water-cooled jacket shell 18. From top to bottom, the outer side of the simulated tool holder 1 is connected to a bearing retainer ring 22, a deep groove ball bearing 21, and an axial locking nut 23. The central through hole of the water-cooled jacket 19 is interference-fitted with the end cap 20 and the outer ring of the deep groove ball bearing 21. The end cap 20 abuts against the bottom surface of the outer ring of the deep groove ball bearing 21. The simulated tool holder 1 is located inside the water-cooled jacket 19. The upper end of the simulated tool holder 1 is a standard machine tool tool holder interface, used to insert into the tapered hole of the spindle under test. When it rotates at high speed with the spindle, coolant is introduced into the water-cooled jacket 19 to simulate real cutting cooling conditions. The water-cooled jacket 19 is a stationary, layered annular component. It consists of an inner wall and an outer wall forming a closed annular cavity, which is the space for coolant circulation.

[0019] A lifting plate 13 is slidably arranged among the four guide pillars 14. The lifting plate 13 is slidably connected to the guide pillars 14 via linear bearings 15 and is fixedly connected to the lifting plate 13. The position of the lifting plate 13 on the guide pillars 14 is adjusted and locked by a threaded retaining ring 16. The center of the lifting plate 13 is fixedly connected to the water-cooling jacket shell 18. The threaded retaining ring 16 is similar to a clamp and is used to support the linear bearings 15 and the lifting plate 13. The position of the lifting plate 13 is adjusted by changing the height of the threaded retaining ring 16.

[0020] The radial force loading device is used to apply a force perpendicular to the axial direction to the simulated tool holder 1. It includes two opposing first cylinders 9, which are located on both sides of the simulated tool holder 1. The first cylinders 9 are fixedly installed on the top inner side of the housing 7. A first force sensor 10 is provided at the output end (piston rod) of the first cylinder 9. One end (detection end) of the first force sensor 10 is connected to the output end of the first cylinder 9, and the other end of the first force sensor 10 is fixedly connected to an axial baffle 11. The two axial baffles 11 are located on both sides of the lifting plate 13. When the first cylinder 9 is activated, the thrust generated is measured by the first force sensor 10 and transmitted to the water-cooled jacket housing 18 through the axial baffles 11 and the lifting plate 13, thereby applying a radial load to the simulated tool holder 1.

[0021] refer to Figures 1 to 6 as well as Figure 9 The axial force loading device is used to apply an axial force to the simulated tool holder 1. It includes two second cylinders 24 fixed to the bottom inner side of the housing 7. Each second cylinder 24 has a second force sensor 25 at its output end. One end (detection end) of the second force sensor 25 is connected to the output end of the second cylinder 24, and the other end of each second force sensor 25 is fixedly connected to a cylinder guide rod 27. The end of the cylinder guide rod 27 away from the second force sensor 25 is connected to a cylinder floating guide mechanism 26 located at the bottom of the lifting plate 13. The cylinder floating guide mechanism 26 includes a connecting seat and a connecting plate hinged together. The connecting seat is fixedly connected to the cylinder guide rod 27 via the cylinder nut 2, and the connecting plate is fixedly connected to the bottom of the lifting plate 13 to ensure that the loading force is transmitted axially. When the second cylinder 24 is activated, the thrust is measured by the second force sensor 25 and then acts on the cylinder floating guide mechanism 26 through the cylinder guide rod 27. The cylinder floating guide mechanism 26 acts on the lifting plate 13, which in turn acts on the water cooling jacket shell 18, the water cooling jacket 19, and the end cap 20. The end cap 20 then acts on the deep groove ball bearing 21, which in turn acts on the simulated tool holder 1, thus subjecting the simulated tool holder 1 to a reaction force in the same direction, achieving axial loading. The first force sensor 10, the second force sensor 25, the planetary joint module 3, and the drive devices of the first cylinder 9 and the second cylinder 24 are all electrically connected to an external controller. The first force sensor 10, the second force sensor 25, the first cylinder 9, the second cylinder 24, and the controller are all existing known technologies and will not be described in detail here.

[0022] When using this device to test the dynamic performance of the spindle, first insert the simulated tool holder 1 into the tapered hole of the spindle of the machine tool under test and tighten it. Fix the entire device to the machine tool table or bed through the U-shaped mounting groove on the housing 7. Roughly adjust the position of the coupling 6 so that the coupling 6 is roughly aligned with the bottom of the tool holder. Fix one end of the coupling 6 to the flange shaft 5 first without locking it. Adjust the position of the machine tool spindle and the height of the lifting plate 13 so that the radially loaded axial baffle 11 is aligned with the lifting plate 13 and the torque-loaded coupling 6 is precisely aligned with the simulated tool holder 1. Lock the coupling 6 and fix the coupling 6 and the simulated tool holder 1 together. After locking the device, perform a final inspection and then start the test. During testing, the spindle drives the simulated tool holder 1 to rotate at high speed. The first cylinder 9 of the radial force loading device is activated, applying radial force to the lifting plate 13 and the water-cooled jacket housing 18 fixed thereto through the first force sensor 10 and the axial baffle 11. This force is ultimately transmitted to the spindle through the simulated tool holder 1. Simultaneously, the second cylinder 24 of the axial force loading device is activated, applying axial force to the lower end of the lifting plate 13 through the second force sensor 25, the cylinder guide rod 27 and the cylinder floating guide mechanism 26. The force is then transmitted to the water-cooled jacket housing 18, the water-cooled jacket 19 and the end cover 20 through the lifting plate 13. The axial force is then transmitted to the deep groove ball bearing 21 and the simulated tool holder 1 through the end cover 20, ultimately causing the spindle to generate an axial reaction force in the same direction. The servo motor in the planetary joint module 3 of the torque loading device is activated, outputting dynamic torque to the simulated tool holder 1 through the flange shaft 5 and the coupling 6. This device can independently or synchronously control the servo motors in the first cylinder 9, the second cylinder 24, and the planetary joint module 3, thereby simulating the complex working load in real machining conditions on the simulated tool holder 1.

[0023] This embodiment also provides a method for using the electromechanical coupling type spindle dynamic characteristic simulation device. Using the device described above, taking a certain model of HSK toolholder as an example, the spindle dynamic performance test includes the following steps: Step 1: Investigate the parameters of the tested electric spindle under actual use conditions, such as maximum speed, power, bearing type, voltage and current, to provide a reference for subsequent parameter setting. Step 2: Based on the results of the survey in Step 1, set the test environment conditions with reference to relevant test standards, and adjust the working parameters and loading speed of the device accordingly to ensure that they match the actual operating conditions, thereby improving the authenticity of the test environment, and determine the maximum test load based on the results of the survey in Step 1. Step 3: Start the machine tool under test, turn off the chip removal and cooling system, and run the spindle continuously at 80% of the maximum speed for 2 hours without installing the tool holder and under no load, so as to achieve the thermal balance of the machine tool. Then, insert the simulated tool holder 1 into the tapered hole of the spindle of the machine tool under test and tighten it. Then, use the U-shaped mounting groove on the housing 7 or the mounting shafts 8 on both sides of the housing 7 to firmly install the device on the machine tool table or bed. Step 4: Set the initial load parameters: axial force 50N, radial force 50N, torque 20N·m, and speed 350r / min. Then, start the spindle, torque loading device, radial force loading device, and axial force loading device of the machine tool under test in sequence. Monitor the data of the first force sensor 10 and the second force sensor 25 and the spindle running status in real time through the external controller. Gradually increase the speed to 80% of the maximum spindle speed according to the set gradient, increasing by 250r / min each time. At the same time, gradually increase the radial force and axial force to the maximum test load determined in Step 2, increasing by 50N each time. Step 5: If there are no abnormalities during Step 4, stop the machine tool under test and this device, and use an external rotational accuracy measurement system, ballbar, and temperature measuring instrument to determine the initial performance indicators of the machine tool spindle under the current state. After the spindle reaches thermal equilibrium, measure its initial performance indicators to provide a comparison benchmark for the dynamic characteristic changes under subsequent loading conditions, thereby accurately assessing the impact of load on spindle performance. If the measured rotational accuracy or ballbar trajectory is abnormal at this time (for example, a spindle that is normally very accurate shows severe eccentricity when measured under no-load conditions), it indicates that the testing device (such as a simulated tool holder or coupling) is faulty or that the testing device itself (such as a bearing) is malfunctioning. Step 6: Restart the device and the machine tool under test, and enter the test environment conditions (simulated working conditions) set in Step 2. The device can independently or synchronously control the first cylinder 9, the second cylinder 24 and the planetary joint module 3, and apply complex dynamic loads by simulating the tool holder 1 to simulate the multi-axis coupled load conditions in the real machining process.

[0024] In summary, this device features a compact structure, comprehensive loading conditions, and high testing efficiency. It monitors the applied radial force, axial force, and torque in real time using built-in force sensors. Simultaneously, it can be connected to external devices such as a rotational accuracy measurement system, accelerometer, and temperature measuring instrument. During spindle rotation and dynamic load application, it synchronously collects performance data such as vibration response, thermal deformation, and rotational error. By comparing and analyzing the measured data under loading conditions with the unloaded thermal benchmark, dynamic performance indicators such as modal characteristics, thermal accuracy, and stiffness changes are extracted. This allows for a quantitative evaluation of the spindle's stability, accuracy retention, and deformation resistance under simulated real cutting conditions. It enables the rapid acquisition of dynamic performance change data for different types of machine tool spindles under simulated real-world conditions. This device can be installed on the machine tool worktable, rotary table, or bed, etc., and can apply dynamic radial force, axial force and torque to the machine tool spindle without breaking the overall structure of the machine tool. It simulates the complex actual working conditions of high-speed, high-torque electric spindles commonly used in high-end CNC machine tools, and can realize comprehensive testing and evaluation of spindle dynamic performance. It provides reliable experimental data and theoretical support for the optimization design and improvement of electric spindles.

[0025] This invention reduces the overall size through a modular and integrated support housing design, facilitating transportation and disassembly / installation. By incorporating a U-shaped mounting slot and mounting shaft on the housing, the device can be quickly adapted to machine tool worktables via the U-shaped mounting slot, and can also be installed even without a worktable, thus enabling universal on-machine testing of CNC machine tool spindles with various structures.

[0026] This invention integrates three independent loading devices for axial force, radial force, and torque, which can simulate the force and torque conditions that the spindle bears during the cutting process under the actual assembly state of the CNC machine tool spindle. This makes the performance test results closer to the actual machining state and provides strong theoretical and data support for the design verification and performance optimization of the spindle and the whole machine.

[0027] Although embodiments of the invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the appended claims and their equivalents.

Claims

1. An electromechanical coupling type spindle operating condition dynamic characteristic simulation device, characterized in that, It includes a support housing, a simulated tool holder (1), a cooling device, a torque loading device, an axial force loading device and a radial force loading device. The support housing includes a box (7) and mounting shafts (8) symmetrically distributed on both sides of the box (7). Multiple sets of U-shaped mounting grooves are provided on the outside of the box (7). The torque loading device includes a planetary joint module (3) installed in the housing (7). The output end of the planetary joint module (3) is connected to the bottom of the simulated tool holder (1) through a coupling (6). The planetary joint module (3) is electrically connected to an external controller. The cooling device includes a water-cooled jacket shell (18), a water-cooled jacket (19), and an end cap (20). The water-cooled jacket (19) is press-fitted inside the water-cooled jacket shell (18). The simulated tool holder (1) is connected from top to bottom to the outer side of the shell. The bearing retainer (22), the deep groove ball bearing (21), and the axial locking nut (23) are connected sequentially. The central through hole of the water-cooled jacket (19) is interference-fitted with the end cap (20) and the outer ring of the deep groove ball bearing (21). The end cap (20) abuts against the bottom surface of the outer ring of the deep groove ball bearing (21). The axial force loading device and the radial force loading device are both installed inside the housing (7), and are used to apply axial force and perpendicular force to the simulated tool holder (1), respectively.

2. The electromechanical coupling type spindle working condition dynamic characteristic simulation device according to claim 1, characterized in that, Multiple guide pillars (14) are fixedly installed inside the housing (7). A lifting plate (13) is slidably installed between the multiple guide pillars (14). The lifting plate (13) is slidably connected to the guide pillars (14) through a linear bearing (15). The position of the lifting plate (13) on the guide pillars (14) is adjusted and locked by a threaded fixing ring (16). The center of the lifting plate (13) is fixedly connected to the water cooling jacket shell (18). The radial force loading device includes two opposing first cylinders (9), which are located on both sides of the simulated tool holder (1) and fixedly connected to the housing (7). The output end of the first cylinder (9) is provided with a first force sensor (10), one end of which is connected to the output end of the first cylinder (9), and the other end of which is fixedly connected to an axial baffle (11). The two axial baffles (11) are located on both sides of the lifting plate (13). The driving device of the first force sensor (10) and the first cylinder (9) is electrically connected to an external controller.

3. The electromechanical coupling type spindle working condition dynamic characteristic simulation device according to claim 2, characterized in that, The axial force loading device includes a second cylinder (24) fixed to the bottom of the inner side of the housing (7). The output end of the second cylinder (24) is connected to one end of the second force sensor (25). The other end of the second force sensor (25) is connected to a cylinder guide rod (27). The end of the cylinder guide rod (27) away from the second force sensor (25) is connected to a cylinder floating guide mechanism (26) located at the bottom of the lifting plate (13). The cylinder floating guide mechanism (26) includes a connecting seat and a connecting plate hinged together. The connecting seat is fixedly connected to the cylinder guide rod (27), and the connecting plate is fixedly connected to the bottom of the lifting plate (13). The driving device of the second force sensor (25) and the second cylinder (24) is electrically connected to an external controller.

4. The electromechanical coupling type spindle working condition dynamic characteristic simulation device according to claim 3, characterized in that, An axial mounting plate (17) is fixedly installed between multiple guide pillars (14). A zipper motor seat (12) is fixedly installed on the axial mounting plate (17). The planetary joint module (3) is fixed on the zipper motor seat (12). The output end of the planetary joint module (3) is connected to a flange shaft (5) by bolts and positioning pins. The flange shaft (5) is fixedly connected to the coupling (6).

5. The electromechanical coupling type spindle working condition dynamic characteristic simulation device according to claim 4, characterized in that, The planetary joint module (3) includes a servo motor and a planetary reducer. The output end of the servo motor is connected to the input end of the planetary reducer. The output end of the planetary reducer is connected to the flange shaft (5) by bolts and positioning pins. A radial support shell (4) is also fixedly installed on the outside of the planetary joint module (3). The radial support shell (4) is connected and fixed to the housing (7).

6. A method for using the electromechanical coupling type spindle operating condition dynamic characteristic simulation device, employing the device as described in claim 5, characterized in that, Includes the following steps: Step 1: Investigate the parameters of the tested electric spindle under actual use conditions to provide a reference for parameter setting; Step 2: Based on the results of the survey in Step 1, determine the maximum test load, set the test environment conditions, and adjust the working parameters and loading speed of the device accordingly to ensure that they match the actual operating conditions and improve the authenticity of the test environment. Step 3: Start the machine tool under test, turn off the chip removal and cooling system, and run the spindle continuously at 80% of the maximum speed for 2 hours without installing the tool holder and under no load, so as to achieve the thermal balance of the machine tool. Then, install the simulated tool holder (1) into the tapered hole of the spindle of the machine tool under test and tighten it. Then, use the U-shaped mounting groove on the housing (7) or the mounting shafts (8) on both sides of the housing (7) to firmly install the device on the machine tool worktable or bed. Step 4: After setting the initial load parameters, start the spindle, torque loading device, radial force loading device and axial force loading device of the machine tool under test in sequence. Monitor the data of the first force sensor (10) and the second force sensor (25) and the spindle running status in real time through the external controller. Gradually increase the speed to 80% of the maximum speed of the spindle according to the set gradient, and at the same time gradually increase the radial force and axial force to the maximum test load determined in step 2. Step 5: If there are no abnormalities during the operation of Step 4, stop the machine tool under test and this device, and use an external rotary accuracy measurement system, ball bar and temperature measuring instrument to determine the initial performance index of the spindle of the machine tool under test in the current state. Step 6: Restart the device and the machine tool under test, and enter the test environment conditions set in Step 2. The device can independently or synchronously control the first cylinder (9), the second cylinder (24) and the planetary joint module (3), and apply complex dynamic loads by simulating the tool holder (1) to simulate the multi-axis coupled load conditions in the real machining process.

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