Quasi-zero stiffness active-passive vibration isolation platform based on force amplification mechanism

Abstract

The invention discloses a quasi-zero stiffness active-passive vibration isolation platform based on a force amplification mechanism. The quasi-zero stiffness active-passive vibration isolation platform is achieved through the synergistic effect of a negative stiffness mechanism, the force amplification mechanism and a frameless torque motor. The negative stiffness mechanism is of a nested double-ring structure, an outer ring stator is composed of arc-shaped permanent magnets magnetized in the radial direction, an inner ring rotor is composed of a fixing sleeve and arc-shaped permanent magnets with alternate magnetic poles, and the permanent magnets are arranged in a magnetic pole alternate mode in the circumferential direction of the inner side. Radial repulsive force is generated through homopolar opposite layout of the permanent magnets, and magnetic negative stiffness is formed. The rotor transmits rotation torque to the force amplification mechanism, the torque is converted into amplified axial force to be output through a geometrical relationship, traditional size limitation is broken through, and mechanical gain is achieved. The axial force and the acting force of the positive stiffness spring are reversely superposed, so that quasi-zero stiffness passive vibration isolation is realized; the tail end of the transmission shaft is connected with a frameless torque motor to form an active control unit, compensation torque is dynamically output through real-time vibration feedback, and finally wide-frequency-domain and high-precision vibration isolation is achieved.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of low-frequency vibration isolation technology, and particularly relates to a quasi-zero stiffness active-passive vibration isolation platform based on a force amplification mechanism. BACKGROUND

[0002] Vibration, as a ubiquitous physical phenomenon, often causes serious harm in industrial production and precision equipment fields - light causes equipment precision degradation, life attenuation, heavy causes structure resonance damage and even safety accidents. Under the trend of lightweight design of engineering equipment, the inherent frequency of the system continues to decrease, and the traditional linear vibration isolation technology faces a dilemma: low stiffness design can expand the vibration isolation frequency band, but it weakens the carrying capacity; high stiffness design can maintain the load performance, but it cannot achieve effective vibration isolation. This contradiction has given birth to quasi-zero stiffness vibration isolation technology, which connects in parallel through positive / negative stiffness mechanisms, maintains high static carrying capacity while achieving low dynamic stiffness, and thus meets the needs of carrying capacity and wide frequency vibration isolation.

[0003] However, the existing passive quasi-zero stiffness system relies on fixed parameter elements and cannot adapt to changes in dynamic characteristics under complex working conditions. For example, the dynamic weighing equipment causes the load to change over time due to random fluctuations in the carrying mass, and the inherent frequency of the system shifts during the machining process of precision instruments due to cutting force disturbances, which will cause the vibration isolation performance of the fixed stiffness system to deteriorate sharply. In addition, the traditional magnetic negative stiffness mechanism is limited by geometric size and magnetic energy utilization rate, and it is difficult to generate enough force in a small space, which restricts the compactness and high efficiency design of the system.

[0004] Therefore, the prior art still needs to be improved and improved. SUMMARY

[0005] In view of the above problems of the prior art, the present application aims to provide a quasi-zero stiffness active-passive vibration isolation platform based on a force amplification mechanism, which aims to solve the problems of the traditional linear vibration isolation system that cannot effectively suppress low-frequency vibration, the limited output of magnetic negative stiffness, and the weak adaptability of passive vibration isolation vibration sources.

[0006] In order to achieve the above purpose, the present application adopts the following technical scheme: In a first aspect, a quasi-zero stiffness active-passive vibration isolation platform based on a force amplification mechanism includes a housing, a load plate, a negative stiffness mechanism, a force amplification mechanism, a positive stiffness spring adjustment mechanism, and a frameless torque motor. The frameless torque motor and the negative stiffness mechanism are arranged on opposite side walls of the housing. One end of the force amplification mechanism is inserted into the housing and connected to the negative stiffness mechanism and the frameless torque motor, and the other end is connected to the load plate. One end of the positive stiffness spring adjustment mechanism is arranged in the housing, and the other end passes through the housing and is connected to the load plate.

[0007] Further, the shell is composed of a negative stiffness support frame, a motor support frame, two bearing support frames, a bottom plate, a front panel and a rear panel. The negative stiffness support frame and the motor support frame are arranged on the bottom plate and opposite to each other. The front panel and the rear panel are arranged on the bottom plate and opposite to each other. The negative stiffness support frame, the front panel, the motor support frame and the rear panel are sequentially connected to form a shell structure with an open upper end. The two bearing support frames are arranged on the bottom plate along the axial direction of the negative stiffness support frame and the motor support frame and located inside the shell.

[0008] Further, the force amplification mechanism includes a conversion mechanism, a T-shaped output shaft and a transmission shaft. The two ends of the transmission shaft are connected to the frameless torque motor and the negative stiffness mechanism. The conversion mechanism is sleeved on the transmission shaft and is rigidly connected to the transmission shaft through a flat key. A sliding groove is formed on the conversion mechanism. The head of the T-shaped output shaft is clamped in the sliding groove. The tail of the T-shaped output shaft is fixedly connected to the load-bearing plate through a fixing ring.

[0009] Further, the negative stiffness mechanism is composed of a rotor assembly and a stator assembly. The rotor assembly includes an inner ring fixed sleeve and an inner ring arc-shaped permanent magnet bonded to the outside of the inner ring fixed sleeve. The inner ring arc-shaped permanent magnet is fixed to the outside of the inner ring fixed sleeve in a magnetic pole alternating arrangement manner through industrial adhesive. The inner ring fixed sleeve is rigidly connected to the transmission shaft through a flat key. The two sides of the inner ring fixed sleeve in the axial direction are limited and fixed by a shaft sleeve and an axial end stop ring. The stator assembly is an outer ring arc-shaped permanent magnet and is fixed to the outer shell in a magnetic pole alternating arrangement manner through industrial adhesive.

[0010] Further, the rotor end of the frameless torque motor is fixed to the motor inner sleeve through industrial adhesive. The motor inner sleeve is connected to the transmission shaft through a flat key. The axial position of the motor inner sleeve is limited by the two side shaft sleeves and the axial end stop ring. The stator end of the frameless torque motor is interference fitted on the side wall of the shell.

[0011] Further, the positive stiffness spring adjusting mechanism includes a support plate, a spring cover and a positive stiffness spring. The support plate is arranged at the bottom of the shell. The spring cover is arranged at the upper end of the support plate. One end of the positive stiffness spring is connected to the spring cover. The other end of the positive stiffness spring is connected to the load-bearing plate through the spring cover.

[0012] Further, the positive stiffness spring adjusting mechanism further includes two inclined surface sliders. The support plate has a cross-shaped structure. The two inclined surface sliders are arranged at the bottom of the shell in a spaced manner and are connected to the front panel and the rear panel through adjusting bolts, respectively. The inclined surface of the inclined surface slider abuts against the support plate. The lower part of the bearing support frame is provided with a notch. One end of the support plate is clamped in the notch of the bearing support frame.

[0013] Further, the load-bearing plate is provided with a plurality of guide shafts at the lower end. A plurality of shaft holes are formed in the vertical direction on the negative stiffness support frame and the motor support frame. The guide shafts are connected to the shaft holes of the negative stiffness support frame and the motor support frame through oil-free bushings.

[0014] Further, the bearing support frame is provided with a bearing, and an inner ring of the bearing is in interference fit with the transmission shaft of the force amplification mechanism.

[0015] The technical scheme adopted by the present application has the following beneficial effects: The mover and the stator of the double-ring nested magnetic negative stiffness mechanism are coaxially nested, the radial magnetic repulsion force of the arc-shaped permanent magnet is coupled, high negative stiffness output is realized in limited space, and the space utilization and energy density of the system are significantly improved. Through the differential design of the guide rail radius of the conversion mechanism being smaller than the action radius of the negative stiffness mechanism, the magnetic repulsion torque is converted into amplified axial force by using the lever principle, which simplifies the mechanical complexity and improves the output efficiency of the negative stiffness, effectively breaking the bottleneck of insufficient output force of the traditional magnetic negative stiffness mechanism. The frameless torque motor is directly integrated with the transmission shaft, the control torque is actively input to compensate the load fluctuation and environmental disturbance in real time, the passive quasi-zero stiffness characteristic is combined to realize wide-frequency-domain adaptive vibration isolation, and the vibration isolation capacity is further enhanced. Meanwhile, the positive stiffness spring adjusting mechanism can make the vibration isolator adapt to heavy objects of different masses by adjusting the pre-compression amount of the spring, thereby increasing the application scenarios. The negative stiffness mechanism, the force amplification mechanism and the motor are arranged in layers along the transmission shaft, and the functional modules are bolted through the support frame and the bottom plate, which not only guarantees the rigidity of the system, but also facilitates disassembly and maintenance, and is suitable for precise equipment scenes with limited space. BRIEF DESCRIPTION OF DRAWINGS

[0016] Figure 1 A structure schematic view of a quasi-zero stiffness active-passive vibration isolation platform based on a force amplification mechanism is provided. Figure 2 An internal structure schematic view of a quasi-zero stiffness active-passive vibration isolation platform based on a force amplification mechanism is provided. Figure 3 A negative stiffness principle schematic view of a quasi-zero stiffness active-passive vibration isolation platform based on a force amplification mechanism is provided. Figure 4 A negative stiffness mechanism structure schematic view of a quasi-zero stiffness active-passive vibration isolation platform based on a force amplification mechanism is provided. Figure 5 A force amplification mechanism structure schematic view of a quasi-zero stiffness active-passive vibration isolation platform based on a force amplification mechanism is provided. Figure 6 A positive stiffness spring adjusting mechanism structure schematic view of a quasi-zero stiffness active-passive vibration isolation platform based on a force amplification mechanism is provided.

[0017] Figure 1 - fixed ring, 2 - bearing plate, 3 - guide shaft, 4 - oil-free bushing, 5 - motor support frame, 6 - bearing support frame, 7 - frameless torque motor, 8 - shaft end retainer, 9 - motor inner sleeve, 10 - conversion mechanism, 11 - bearing, 12 - support plate, 13 - spring cover, 14 - bottom plate, 15 - positive stiffness spring adjustment mechanism, 16 - inclined surface slider, 17 - positive stiffness spring, 18 - negative stiffness support frame, 19 - outer ring arc-shaped permanent magnet, 20 - inner ring arc-shaped permanent magnet, 21 - inner ring fixed sleeve, 22 - transmission shaft, 23 - shaft sleeve, 24 - negative stiffness mechanism, 25 - force amplification mechanism, 26 - T-shaped output shaft, 27 - rear panel, 28 - front panel, 29 - flat key, 30 - adjusting bolt. DETAILED DESCRIPTION

[0018] To make the purpose, technical scheme and effect of the present application more clear and explicit, the present application is further described in detail below with reference to the drawings and examples. It should be understood that the specific examples described herein are only used to explain the present application and do not limit the present application.

[0019] The present application is described in detail below with reference to the drawings: According to Figures 1-6 , the shell system of the quasi-zero stiffness primary and passive vibration isolation platform based on the force amplification mechanism is composed of multiple component modules: the motor support frame 5, the negative stiffness support frame 18, the bottom plate 14, the front panel 28 and the rear panel 27 are assembled into an overall shell structure by bolt connection, and two bearing support frames 18 are fixed inside the motor support frame 5 and the negative stiffness support frame 18. The square shell design has both aesthetic and practical functions, and the compact size layout can adapt to complex working conditions with limited space.

[0020] As shown in Figure 2 , the core execution mechanism of the vibration isolation platform is composed of four parts in cooperation: the negative stiffness structure 24, the force amplification mechanism 25, the positive stiffness spring adjustment mechanism 15 and the frameless torque motor 7. Among them, the negative stiffness mechanism is shown in Figure 3 , which adopts a dynamic and stator double-component design. The dynamic component adopts a composite structure of inner ring fixed sleeve 21 and inner ring arc-shaped permanent magnet 20, and the inner ring fixed sleeve 21 is provided with a flat key installation groove; the stator component is a circumferentially arranged outer ring arc-shaped permanent magnet 19. The inner and outer ring permanent magnets 19, 20 are radially magnetized, and the same magnetic poles are opposite to each other to generate repulsive force as shown in Figure 4 the schematic magnetic field distribution.

[0021] The construction process of the mover assembly is as follows: a plurality of inner ring arc-shaped permanent magnets 20 are arranged circumferentially along the outer peripheral surface of the inner ring fixing sleeve 21 by using industrial-grade adhesive, the magnetic polarities of adjacent magnets are alternately distributed, and a regular magnetic pole array is formed; the inner ring fixing sleeve 21 is rigidly connected with the transmission shaft 22 through a flat key, so as to ensure effective transmission of the negative stiffness torque, and the axial freedom degree is mechanically constrained by the shaft sleeves 23 arranged on both sides and the shaft end retainer 8. Correspondingly, the arc-shaped permanent magnets 24 in the stator assembly are fixed on the inner surface of the circular hole of the negative stiffness support frame 18 by the adhesive process according to the same polarity alternation principle, to form a static fixed assembly. During the operation of the platform, the mover assembly and the stator assembly rotate relative to each other, at this time, the repulsion force field between the inner and outer ring permanent magnets forms a nonlinearly changed torque output, and the negative stiffness characteristic is mechanically transmitted to the force amplification mechanism 25 through the transmission shaft 22.

[0022] The force amplification mechanism 25 is composed of the conversion mechanism 10 and the T-shaped output shaft 26, as shown in Figure 5 The force amplification mechanism 25 includes the conversion mechanism 10, the T-shaped output shaft 26 and the transmission shaft 22, both ends of the transmission shaft 22 are connected to the frameless torque motor 7 and the negative stiffness mechanism 24, the conversion mechanism 10 is sleeved on the transmission shaft 22 and is rigidly connected with the transmission shaft 22 through a flat key 29, a sliding groove is also formed on the conversion mechanism 10, the head of the T-shaped output shaft 26 is clamped in the sliding groove, and the tail of the T-shaped output shaft 26 is fixedly connected with the bearing plate 2 through the fixing ring 1. The specific principle is as follows: the conversion mechanism 10 is rigidly connected with the transmission shaft 22 through a flat key to realize the transmission of the torque. The conversion mechanism 10 is processed with a guide sliding groove, and the T-shaped output shaft 26 and the sliding groove form a low-friction sliding pair, so that the rotary motion of the transmission shaft 22 is converted into the linear motion of the T-shaped output shaft.

[0023] In the realization principle of the quasi-zero stiffness system, the negative stiffness mechanism 24 first transmits the negative stiffness torque to the transmission shaft 22, and the transmission shaft 22 further transmits the torque to the conversion mechanism 10 through the flat key 29. Under the constraint of the guide sliding groove of the conversion mechanism 10, the T-shaped output shaft 26 is limited to move only in the axial direction, so as to transmit the negative stiffness effect to the bearing plate 2. At the same time, the bearing plate 2 is connected with the positive stiffness spring 17 on both sides, for providing the positive stiffness output. By coupling the positive stiffness and the negative stiffness in parallel, the system finally realizes the quasi-zero stiffness characteristic. The guide of the positive stiffness spring 17 and the T-shaped output shaft 26 in the structure is realized by the sliding pair composed of the guide shafts 3 installed on the four corners of the bearing plate 2 and the oil-free bushings 4 installed on the negative stiffness support frame 18 and the motor support frame 5.

[0024] The mechanism realizes force amplification function through kinematic parameter optimization: the design value of the rotation radius of the sliding groove of the conversion mechanism 10 is less than the action radius of the negative stiffness mechanism 24, and the rotation torque input by the transmission shaft 22 is converted into amplified axial output force by using the difference between the movement radii. This mechanical gain effect enables the system to significantly improve the dynamic response performance of the negative stiffness output while maintaining the compactness of the structure.

[0025] The positive stiffness spring adjusting mechanism 15 mainly comprises the inclined sliding blocks 16, the support plate 12, the adjusting bolt 30, the bottom plate 14 and the sliding grooves on the bearing support frame 6, as shown in Figure 6 The support plate 12 is arranged at the bottom in the housing, the spring cover 13 is arranged at the upper end of the support plate 12, one end of the positive stiffness spring 17 is connected to the spring cover 13, and the other end is connected to the load-bearing plate 2 through the spring cover 13, the support plate 12 has a cross-shaped structure, the two inclined sliding blocks 16 are arranged at intervals at the bottom in the housing and are connected to the front panel 28 and the rear panel 27 respectively through the adjusting bolt 30, and the inclined surfaces of the inclined sliding blocks 16 abut against the support plate 12, the bearing support frame 6 is provided with a notch at the lower part, and one end of the support plate 12 is clamped in the notch of the bearing support frame 6.

[0026] The basic working principle is as follows: by rotating the adjusting bolt 30 arranged on the rear panel 27, a pair of threaded inclined sliding blocks 16 can be driven to move one by one. The two inclined sliding blocks 16 are oppositely arranged in the sliding grooves of the bottom plate 14, and the screw rotation directions matched with the adjusting bolt 30 are opposite. Therefore, when the adjusting bolt 30 rotates, the two sliding blocks can only move towards or away from each other along the sliding grooves. When the sliding blocks move towards each other, the support plate 12 in contact with them will be squeezed, forcing the support plate 30 to move upwards along the sliding groove of the bearing support frame 6, thereby increasing the compression amount of the positive stiffness spring 17. Conversely, if the adjusting bolt 30 rotates in the opposite direction, the sliding blocks move away from each other, the support plate 12 moves downward, and the compression amount of the positive stiffness spring 17 decreases. Through the above adjusting mechanism, the needs of different weights of heavy objects can be met, effectively expanding the application scenarios of the system.

[0027] The frameless torque motor 7 adopts a special integrated installation scheme: the rotor end of the frameless torque motor 7 is fixed to the motor inner sleeve 9 through industrial adhesive, the motor inner sleeve 9 is connected with the transmission shaft 22 through a flat key, and the axial position of the motor inner sleeve 9 is limited by the two side shaft sleeves 23 and the shaft end retainer 8; the stator end of the frameless torque motor 7 is interference-fitted on the side wall of the housing.

[0028] The mover assembly is permanently fixed to the sleeve 9 in the motor through high-strength structural adhesive, the sleeve is rotationally coupled with the transmission shaft 22 through key groove matching, and the axial displacement constraint mechanism is formed by the double-sided shaft sleeve 23 and the shaft end check ring 8; the stator assembly is press-fitted in the installation cavity of the special motor support frame 5 in an interference fit manner, and the support frame is rigidly connected with the bottom plate 14 through an internal hexagonal bolt. The motor system inputs precise and controllable electromagnetic torque to the vibration isolation platform through the transmission shaft 22, and the active closed-loop adjustment of the dynamic response of the platform is realized in combination with the synergistic action of the negative stiffness mechanism 24 and the force amplification mechanism 25, and the vibration suppression performance in a complex disturbance environment is significantly improved.

[0029] The core transmission assembly of the system adopts an axial stacking integrated scheme: the negative stiffness mechanism 24, the force amplification mechanism 7 and the frameless torque motor 7 are spatially optimized and arranged along the axial direction of the transmission shaft 22. The transmission shaft system is supported by two groups of high-precision bearings 11, wherein the inner ring of the bearing is tightly fitted with the transmission shaft 22 through an interference press-fitting process, and is mechanically constrained in both directions by means of the shaft sleeve 23 and the shaft shoulder structure; the outer ring of the bearing is fixed in the installation hole of the special bearing support frame 6 in an interference fit manner, forming a stable rotating support system.

[0030] The system structure framework adopts a modular assembly design: the negative stiffness support frame 18, the motor support frame 5 and the bearing support frame 6 are rigidly connected with the bottom plate 14 through an internal hexagonal bolt. The end of the output shaft 22 is bolted to the load plate 2 through the fixing ring 1 to form a complete force transmission path.

[0031] The working process or working principle of the present application is as follows: When external vibration excitation acts on the load plate 2, the displacement is transmitted to the inside of the system through the axial movement of the T-shaped output shaft 26, triggering the following dynamic process: The displacement of the load plate 2 drives the T-shaped output shaft 26 to move axially, compressing or stretching the positive stiffness spring 17, which generates a linear restoring force; the axial movement of the T-shaped output shaft 26 makes its head slide inside the guide sliding groove of the conversion mechanism 10, and due to the circumferential constraint of the sliding groove, the T-shaped output shaft 26 forces the conversion mechanism 10 to rotate around the transmission shaft 22. The rotation of the conversion mechanism 10 drives the mover assembly of the negative stiffness mechanism 24 to rotate relative to the stator assembly through the transmission shaft 22; the arc-shaped permanent magnets of the mover and the stator generate a radial magnetic repulsion due to same-pole repulsion, forming a non-linear negative stiffness; the negative stiffness torque is transmitted to the conversion mechanism 10 through the transmission shaft 22 in the opposite direction, and is amplified through the geometric lever effect, and is finally converted into an axial negative stiffness force. The positive stiffness mechanism and the negative stiffness mechanism are connected in parallel to realize passive vibration isolation of the quasi-zero stiffness system. When the active force of the motor is involved, quasi-zero stiffness active vibration isolation is realized.

[0032] The application adopts coaxial nested layout of the mover and the stator of the double-loop nested magnetic negative stiffness mechanism, realizes high negative stiffness output in limited space through the radial magnetic repulsion coupling of the arc-shaped permanent magnet, and significantly improves the space utilization and energy density of the system. Through the differential design that the guide rail radius of the conversion mechanism 10 is smaller than the action radius of the negative stiffness mechanism, the magnetic repulsion torque is converted into amplified axial force by using the lever principle, which simplifies the mechanical complexity and improves the output efficiency of the negative stiffness, effectively breaking the bottleneck of insufficient output force of the traditional magnetic negative stiffness mechanism. The frameless torque motor 7 is directly integrated with the transmission shaft 22, and the real-time compensation of load fluctuation and environmental disturbance is realized through active input control torque, combined with the passive quasi-zero stiffness characteristics, the wide frequency domain adaptive vibration isolation is realized, and the vibration isolation capacity is further enhanced. At the same time, the positive stiffness spring adjusting mechanism 15 can make the vibration isolator adapt to different weights by adjusting the pre-compression amount of the spring, and increase the application scene. The negative stiffness mechanism 24, the force amplification mechanism 25 and the motor are layered along the transmission shaft, and each functional module is bolted through the support frame and the bottom plate, which not only guarantees the rigidity of the system, but also is convenient for disassembly and maintenance, and is suitable for the scene of precision equipment with limited space.

Claims

1. A quasi-zero stiffness active-passive vibration isolation platform based on a force amplification mechanism, characterized in that, It includes a shell, a load-bearing plate (2), a negative stiffness mechanism (24), a force amplification mechanism (25), a positive stiffness spring adjustment mechanism (15), and a frameless torque motor (7). The frameless torque motor (7) and the negative stiffness mechanism (24) are located on opposite side walls of the shell. One end of the force amplification mechanism (25) is inserted into the shell and connected to the negative stiffness mechanism (24) and the frameless torque motor (7), while the other end is connected to the load-bearing plate (2). One end of the positive stiffness spring adjustment mechanism (15) is located inside the shell, while the other end passes through the shell and is connected to the load-bearing plate (2).

2. The quasi-zero stiffness active-passive vibration isolation platform based on a force amplification mechanism according to claim 1, characterized in that, The shell consists of a negative stiffness support frame (18), a motor support frame (5), two bearing support frames (6), a base plate (14), a front panel (28), and a rear panel (27). The negative stiffness support frame (18) and the motor support frame (5) are located on the base plate (14) and arranged opposite to each other. The front panel (28) and the rear panel (27) are located on the base plate (14) and arranged opposite to each other. The negative stiffness support frame (18), the front panel (28), the motor support frame (5), and the rear panel (27) are connected in sequence to form a shell structure with an open top. The two bearing support frames (6) are arranged at intervals on the base plate (14) along the axial direction of the negative stiffness support frame (18) and the motor support frame (5) and are located inside the shell.

3. The quasi-zero stiffness active-passive vibration isolation platform based on a force amplification mechanism according to claim 1, characterized in that, The force amplification mechanism (25) includes a conversion mechanism (10), a T-shaped output shaft (26), and a transmission shaft (22). The two ends of the transmission shaft (22) are connected to the frameless torque motor (7) and the negative stiffness mechanism (24). The conversion mechanism (10) is sleeved on the transmission shaft (22) and forms a rigid connection with the transmission shaft (22) through a flat key (29). The conversion mechanism (10) is also provided with a sliding groove. The head of the T-shaped output shaft (26) is engaged in the sliding groove, and the tail of the T-shaped output shaft (26) is fixedly connected to the load-bearing plate (2) through a fixing ring (1).

4. The quasi-zero stiffness active-passive vibration isolation platform based on a force amplification mechanism according to claim 3, characterized in that, The negative stiffness mechanism (24) consists of a mover assembly and a stator assembly. The mover assembly includes an inner ring fixing sleeve (21) and an inner ring arc-shaped permanent magnet (20) bonded to its outer side. The inner ring arc-shaped permanent magnet (20) is fixed to the outer side of the inner ring fixing sleeve (21) by industrial adhesive in an alternating arrangement of magnetic poles. The inner ring fixing sleeve (21) is rigidly connected to the drive shaft (22) by a flat key. The two sides of the inner ring fixing sleeve (21) in the axial direction are limited and fixed by bushings (23) and shaft end retaining rings (8). The stator assembly is an outer ring arc-shaped permanent magnet (19) and is fixed to the outer shell by industrial adhesive in an alternating arrangement of magnetic poles.

5. The quasi-zero stiffness active-passive vibration isolation platform based on a force amplification mechanism according to claim 3, characterized in that, The moving end of the frameless torque motor (7) is fixed to the inner sleeve (9) of the motor by industrial adhesive. The inner sleeve (9) of the motor is connected to the drive shaft (22) by a flat key. The axial position of the inner sleeve (9) of the motor is limited by the bushings (23) on both sides and the shaft end retaining ring (8). The stator end of the frameless torque motor (7) is interference-fitted to the side wall of the housing.

6. The quasi-zero stiffness active-passive vibration isolation platform based on a force amplification mechanism according to claim 2, characterized in that, The positive stiffness spring adjustment mechanism (15) includes a support plate (12), a spring cover (13) and a positive stiffness spring (17). The support plate (12) is located at the bottom of the housing, and the spring cover (13) is located at the upper end of the support plate (12). One end of the positive stiffness spring (17) is connected to the spring cover (13), and the other end is connected to the load-bearing plate (2) through the spring cover (13).

7. The quasi-zero stiffness active-passive vibration isolation platform based on a force amplification mechanism according to claim 5, characterized in that, The positive stiffness spring adjustment mechanism (15) also includes two inclined sliders (16), the support plate (12) has a cross-shaped structure, the two inclined sliders (16) are spaced apart at the bottom of the housing, and are connected to the front panel (28) and the rear panel (27) respectively by adjusting bolts (30), and the inclined surface of the inclined slider (16) abuts against the support plate (12), the bearing support frame (6) has a slot at the bottom, and one end of the support plate (12) is engaged in the slot of the bearing support frame (6).

8. The quasi-zero stiffness active-passive vibration isolation platform based on a force amplification mechanism according to claim 2, characterized in that, Multiple guide shafts (3) are provided at the lower end of the load-bearing plate (2). Multiple shaft holes are provided on the negative stiffness support frame (18) and the motor support frame (5) along the vertical direction. The guide shafts (3) are connected to the shaft holes of the negative stiffness support frame (18) and the motor support frame (5) through the oil-free bushing (4).

9. The quasi-zero stiffness active-passive vibration isolation platform based on a force amplification mechanism according to claim 2, characterized in that, The bearing support frame (6) is provided with a bearing (11), and the inner ring of the bearing (11) is interference-fitted with the drive shaft (22) of the force amplification mechanism (25).

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