Self-adaptive pneumatic vibration isolation platform

Abstract

The invention discloses a self-adaptive pneumatic vibration isolation platform which comprises a supporting mechanism and a rigidity correction mechanism, and the supporting mechanism comprises a first air spring, a first roller and a supporting leg; the first air spring is connected with the first roller; the first roller is attached to the supporting leg; the supporting leg has an inclined angle as a wedge block to be connected with the load plate; the rigidity correction mechanism comprises a second air spring, a second roller and a semicircular cam; the second air spring is connected with the second roller; the second roller is attached to the semicircular cam; the semicircular cam is connected with the supporting leg; in the working process, force of the first air spring is transmitted to the load plate through the first rolling wheel and the supporting legs, and vertical supporting force is provided to support the load plate. The second rolling wheel rolls on the surface of the semicircular cam, the state of the second air spring is changed, restoring force opposite to the supporting mechanism is generated, and correction of the rigidity of the platform is achieved. The rigidity is flexibly adjusted according to the mass change of a vibration isolation object by utilizing the combination of the positive and negative rigidity mechanisms.

Description

Technical Field

[0001] The present invention relates to the technical field of pneumatic vibration isolation, and particularly to an adaptive pneumatic vibration isolation platform. Background Art

[0002] Vibration isolation systems are widely used in engineering practice, and their research has been relatively in-depth. A variety of methods for reducing the stiffness of isolation systems have been proposed, such as forming a non-linear spring through specific structural design (research by Virgin et al.) or adopting anti-spring technology (research by Chin et al.). These methods have improved the vibration isolation effect to a certain extent. In recent years, vibration isolation systems with high static and low dynamic stiffness or quasi-zero stiffness characteristics have become a research hotspot. Many researchers have proposed a variety of related vibration isolation models and technologies from different perspectives, including using different structural combinations (such as the combination of a linear mechanical spring and a magnet, a composite bistable plate, etc.) and proposing new dynamic models (such as a model similar to a Duffing oscillator, a stable quasi-zero stiffness model, etc.), and have analyzed their performance in many aspects, such as research on natural frequency, dynamic response, stability, steady-state response, limit cases, and bifurcation phenomena.

[0003] However, although reducing stiffness can suppress vibration, it will lead to a decrease in the load capacity of the system, which is a difficult problem to balance in practical engineering applications. For example, in some vibration isolation scenarios that need to bear a large load, the existing methods for reducing stiffness may not meet the load requirements. Many previous studies focused on passive isolation with a constant isolation load. The passive quasi-zero stiffness vibration isolator is only effective for a specific isolation load for a given configuration parameter. When the isolation load changes, its dynamic stiffness needs to be adjusted. However, the existing adjustment methods (such as replacing elastic elements or adjusting configuration parameters) are difficult to operate in practical applications, which limits their wide application in practical engineering. Summary of the Invention

[0004] In view of this, the present invention proposes an adaptive pneumatic vibration isolation platform. The Adaptive Pneumatic Vibration Isolation Platform (APVIP) combines pneumatic technology and mechanical transmission technology. It supports the load through a positive stiffness mechanism (support mechanism), and uses a stiffness correction mechanism with negative stiffness to reduce the dynamic stiffness, facilitating flexible adjustment of the stiffness according to the change in the mass of the isolation object. In this way, it not only maintains the load support capacity but also obtains a low dynamic stiffness at the desired static equilibrium position (DSEP), effectively broadening the isolation area and improving the isolation effect, overcoming the problems of poor load adaptability and difficult stiffness adjustment of passive isolators in the prior art.

[0005] To achieve the above object, the technical solution adopted by the present invention is as follows:

[0006] An embodiment of the present invention provides an adaptive pneumatic vibration isolation platform, which includes: a support mechanism and a stiffness correction mechanism, where:

[0007] The support mechanism includes: a first air spring, a first roller and a leg; the first air spring is connected to the first roller; the first roller is in contact with the leg; the leg has an inclination angle and is connected to the load plate as a wedge; during the working process, the force of the first air spring is transmitted to the load plate through the first roller and the leg, providing a vertical support force to support the load plate;

[0008] The stiffness correction mechanism includes: a second air spring, a second roller and a semi-circular cam; the second air spring is connected to the second roller; the second roller is in contact with the semi-circular cam; the semi-circular cam is connected to the leg; during the working process, the second roller rolls on the surface of the semi-circular cam, changing the state of the second air spring, generating a restoring force opposite to that of the support mechanism, and realizing the correction of the platform stiffness.

[0009] In an optional embodiment, the number of the first air springs is two.

[0010] In an optional embodiment, the first air spring is connected to the first roller through a linear bearing.

[0011] In an optional embodiment, the number of the second air springs is two.

[0012] In an optional embodiment, the second air spring is connected to the second roller through a linear bearing.

[0013] In an optional embodiment, the first roller moves in the horizontal direction and always rolls on the surface of the leg without sliding.

[0014] In an optional embodiment, the second roller moves in the horizontal direction and always rolls on the surface of the semi-circular cam without sliding.

[0015] In an optional embodiment, the centers of the semi-circular cam and the second roller are on the same horizontal line.

[0016] Compared with the prior art, the present invention has at least the following beneficial effects:

[0017] The present invention provides an adaptive pneumatic vibration isolation platform. By combining pneumatic technology and mechanical transmission technology and utilizing the combination of positive and negative stiffness mechanisms, it helps to achieve flexible adjustment of stiffness according to the change in the mass of the vibration isolation object, obtain a low dynamic stiffness at the desired static equilibrium position (DSEP), effectively broaden the vibration isolation region, and improve the vibration isolation effect. The present invention maintains the DSEP and obtains an ideal low dynamic stiffness by adjusting the pressure of the air spring. When the vibration isolation load changes, by adjusting the pressure of the air spring, the vibration isolation performance of the system can be effectively improved, avoiding problems such as excessive static deformation or offset of the equilibrium position caused by load changes, and enabling the platform to maintain a good working state under different load conditions, which is difficult to achieve by traditional vibration isolation technologies.

[0018] Other features and advantages of the present invention will be described in the subsequent description, and part of them will be obvious from the description or will be understood by implementing the present invention. The objectives and other advantages of the present invention can be achieved and obtained through the structures specifically pointed out in the written description and the drawings.

[0019] The technical solution of the present invention will be further described in detail below through the drawings and embodiments. Description of the Drawings

[0020] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the following will briefly introduce the drawings required for the description of the embodiments or the prior art. Obviously, the drawings in the following description are some embodiments of the present application. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.

[0021] The drawings are used to provide a further understanding of the present invention and constitute a part of the specification. They are used to explain the present invention together with the embodiments of the present invention and do not constitute a limitation to the present invention.

[0022] Figure 1 Schematic diagram of the structure of an adaptive pneumatic vibration isolation platform provided by an embodiment of the present invention.

[0023] Figure 2 Schematic diagram of the air spring provided by an embodiment of the present invention.

[0024] Figure 3 Schematic diagram of the geometric relationship among the roller, the wedge block, and the semi-circular cam provided by an embodiment of the present invention.

[0025] Among them, 1 - the first air spring; 2 - the second air spring; 3 - the first roller; 4 - the second roller; 5 - positive damping; 6 - semi-circular cam; 7 - load plate; 8 - leg; 9 - guide rod; 10 - base. Detailed Embodiments

[0026] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the following will clearly and completely describe the technical solutions in the embodiments of the present invention with reference to the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are some, but not all, of the embodiments of the present invention.

[0027] In the description of the present invention, it should be noted that, unless otherwise clearly defined and limited, terms such as "installation", "provided with", "connection", etc. shall be understood in a broad sense. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the communication inside two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific situations.

[0028] In the description of the present invention, it should be noted that the orientation or positional relationship indicated by terms such as "upper", "lower", "inner", "outer", "front end", "rear end", "both ends", "one end", "the other end", etc. is based on the orientation or positional relationship shown in the accompanying drawings. It is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and should not be construed as a limitation of the present invention. Therefore, the following detailed description of the embodiments of the present invention provided in the accompanying drawings is not intended to limit the scope of the claimed present invention, but merely represents selected embodiments of the present invention. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts fall within the scope of protection of the present invention.

[0029] See Figure 1 As shown, the present invention provides an adaptive pneumatic vibration isolation platform, which mainly consists of a load-bearing mechanism (represented by a dashed rectangle) and a stiffness correction mechanism (represented by a dotted rectangle). Among them: the former is used to provide vertical positive stiffness to support the load plate 7, and it consists of two first air springs 1, four first rollers 3, and four legs 8 serving as wedges, and the inclination angle of the wedge is α. While the latter has vertical negative stiffness and includes two second air springs 2, four semi-circular cams 6, and four second rollers 4. Since the stiffnesses of the load-bearing mechanism and the stiffness correction mechanism are opposite, the proposed platform can maintain the load support capacity and obtain the required low dynamic stiffness at the ideal static equilibrium position, where the centers of the semi-circular cams 6 and the second rollers 4 are on the same horizontal line, which means that the vibration isolation area of the adaptive pneumatic vibration isolation platform can be extended to low frequencies, and its vibration isolation effect can be significantly improved.

[0030] The adaptive pneumatic vibration isolation platform always maintains an ideal static equilibrium position and can avoid static deformation exceeding the maximum value by adjusting the pressure in the first air spring 1 because the isolation load changes. However, as a result of this adjustment, the total stiffness of the adaptive pneumatic vibration isolation platform at the ideal static equilibrium position may increase or decrease compared to before adjusting the pressure in the first air spring 1. This problem can be overcome by adjusting the pressure in the second air spring 2, indicating that the proposed platform can achieve the required low dynamic stiffness at the ideal static equilibrium position.

[0031] It should be noted that the semi-circular cam 6 is fixed on the leg 8. During operation, the first roller 3 and the second roller 4 only move in the horizontal direction and always roll on the surfaces of the wedge (leg 8) and the semi-circular cam 6 without slipping. The leg 8 and the semi-circular cam 6 of the cam can only achieve vertical movement through the guide rod 9, and the base 10 is used to fix the guide rod 9. The free vibration of the system will be attenuated in a timely manner by using positive damping 5.

[0032] The following combines Figures 1 to 3 As shown, the relevant principles and specific implementation methods involved in the present invention are introduced in detail;

[0033] I. Relevant principles: |

[0034] 1. Air spring model:

[0035] As Figure 2 shown in the air spring, assuming that the air spring is compressed by x from the non-compressed state (drawn with a dashed line), and the heat flow between the air and the air spring wall is ignored. According to the ideal gas law, the rate of change of the internal energy U of the air in the air spring with time is expressed as:

[0036]

[0037] Among them, m is the mass of the air in the air spring, c v is the specific heat capacity, and T is the absolute air temperature;

[0038] P represents the absolute air pressure in the air spring. From PV = mGT, we can get:

[0039]

[0040] Among them, is the air mass flow rate, V is the volume of the air spring, and G is the gas constant (G = 287 J / (Kg*K)).

[0041] Since there is no air entering or leaving, Substituting Equation (2) into Equation (1), the mathematical model of the pressure in the air spring is expressed as:

[0042]

[0043] Among them, n is the specific heat ratio.

[0044] The force (F AS ) of the air spring is calculated as:

[0045] F AS = (P - P atm ) A #(4)

[0046] Among them, A is the effective area of the air spring, and P atm is the ambient pressure.

[0047] The stiffness (K AS ) of the air spring is defined as:

[0048]

[0049] Considering small oscillations of the air spring near the design height (h d ), its stiffness is linearized near this height as follows:

[0050]

[0051] Among them, K LAS is the linearized stiffness of the air spring, V dh , A dh and P dh are the volume, effective area and pressure of the air spring at the design height respectively, and δ Adh , δ Vdh are the change amounts of the effective area and volume near the design height h d .

[0052] The restoring force (F LAS ) of the air spring is linearized:

[0053] F LAS = -K LAS Δh + (P dh - P atm ) A dh #(7)

[0054] Among them, Δh is the height change of the air spring, as Figure 2 shown.

[0055] Through this model, the dynamic changes in pressure of the air spring under different compression or expansion states can be understood, thus providing key parameters for the mechanical analysis of the entire platform. Among them, the force model directly reflects the load-bearing capacity of the air spring under different pressures, while the stiffness model describes the ability of the air spring to resist deformation, which is important for analyzing the deformation of the platform when bearing loads and vibrations. When studying the dynamic response of the platform, an accurate stiffness model can help predict the vibration characteristics of the platform under different working conditions. Finally, through linearization, the analysis process is simplified, so that when studying the dynamic response of the platform under small-amplitude vibrations, simpler and more effective mathematical methods can be used for calculation and analysis. At the same time, within a certain design position area, the error of the approximate model is small and can meet the accuracy requirements for the study of the dynamic characteristics of the platform.

[0056] 2. Load Support and Stiffness Correction Mechanism Restoring Force Model:

[0057] The load (F LB ) and the restoring force of the stiffness correction (F SC ) mechanism are determined as follows:

[0058]

[0059] Among them, the forces of the air spring and the spring are defined by the previous formula. The wedge angle is represented by α, H 0 is the static deformation of the platform, and R and r are the radii of the semi-circular cam and the roller respectively. y is the displacement of the load plate from the initial position to any position, as shown in Figure 3 .

[0060] Based on what is shown in Figure 3 , the height changes of the first air spring 1 and the second air spring 2 are determined as follows:

[0061] Δh 1 = (H 0 - y)tanα #(10)

[0062]

[0063] Among them, the superscripts "1" and "2" represent the first air spring 1 and the second air spring 2 respectively.

[0064] By letting u = H 0 - y, the vertical resultant force acting on the load plate is expressed as:

[0065]

[0066] Among them, and are expressed as:

[0067]

[0068] The restoring force of the load support mechanism is related to the restoring force of the air spring and the wedge angle, which determines its ability to support the load and the way it acts on the load during vibration; the restoring force of the stiffness correction mechanism is related to the restoring force of the air spring, the geometric relationship between the cam and the roller, and the displacement of the load plate. This model reflects its mechanism of action on the platform stiffness correction. The two act together to affect the overall performance of the platform and the vibration isolation effect. Finally, considering the load support mechanism, the stiffness correction mechanism, and other relevant parameters, the vertical resultant force acting on the load plate is obtained. This resultant force model is the core for analyzing the dynamic response of the platform when bearing the load and being externally excited. Through it, the vibration characteristics, equilibrium state, and isolation performance of the platform can be further studied.

[0069] 3. Dimensionless model:

[0070] By introducing the non-dimensional parameters as follows:

[0071]

[0072]

[0073] Among them, A, B, C, and D are complex combinations involving multiple parameters. For example, A includes the environmental pressure P atm , the change amount δ of the effective area, and the stiffness K L of the parameter combination. B includes the specific heat capacity n, the change amounts of the effective area and volume at different positions, etc. The introduction of these non-dimensional parameters can simplify the dynamic analysis, make the equations easier to handle and understand, and at the same time highlight the relative importance of different parameters in the system. Through non-dimensionalization, the quantities with physical units can be transformed into dimensionless forms, so as to better compare and analyze the characteristics of the system.

[0074] Then, equation (12) is rewritten as follows:

[0075]

[0076] By differentiating the dimensionless restoring force given in the equation with respect to the dimensionless displacement u, the dimensionless dynamic stiffness in the vertical direction is obtained as follows:

[0077]

[0078] Then, substitute into equation (16), and the dynamic stiffness at the ideal static equilibrium position is expressed as follows:

[0079]

[0080] In addition, to obtain DSEP, the restoring force F s must be equal to the gravity of the isolated object, which means that the weight of the isolated object must satisfy the following equation:

[0081]

[0082] where g is the acceleration due to gravity.

[0083] The role of this model is to transform the relationship of complex physical quantities into a dimensionless form. The advantage of doing so is that it can reduce the number of parameters, simplify the equation form, facilitate general analysis and research, and can more clearly reveal the influence of the relative relationship between different parameters on the platform performance.

[0084] II. Introduction to the platform structure:

[0085] As Figure 1As shown, the platform includes a Loadbearing mechanism (LBM) and a Stiffness Correction mechanism (SCM). The Loadbearing mechanism (LBM) has two first air springs 1, which play an important role in providing vertical support force in the platform. The internal pressure change follows the relevant pneumatic model, and supports the load through the force and stiffness characteristics during the compression and recovery processes. The first rollers 3 are distributed at specific positions and cooperate with the wedges (legs 8). The main movement mode of the first rollers 3 is rolling in the horizontal direction and always rolling on the surface of the wedges. This rolling connection method enables the Loadbearing mechanism to flexibly adjust when bearing the load and undergoing displacement, reducing friction and achieving effective force transmission. The legs 8, as wedges, have an inclination angle α. The legs 8 are directly connected to the load plate 7, transmitting the forces borne and transmitted by the first air springs 1 and the first rollers 3 to the load plate 7. At the same time, the design of the inclination angle α affects the mechanical characteristics of the Loadbearing mechanism, such as the magnitude and direction of the load support force. The Stiffness Correction mechanism (SCM) also includes two second air springs 2, which work in coordination with the first air springs 1 in the Loadbearing mechanism but play a unique role in stiffness correction. Through its own compression and recovery processes, corresponding forces are generated according to different displacement conditions, thereby correcting the overall stiffness of the platform. The semi-circular cams 6 are fixed on the legs 8 and interact with the second rollers 4. During operation, the second rollers 4 roll on the surface of the semi-circular cams 6. This connection method enables, when the platform has a vertical displacement, the compression state of the second air springs 2 to be changed through the change in the geometric relationship between the semi-circular cams 6 and the second rollers 4, and then a restoring force opposite to that of the Loadbearing mechanism is generated to achieve the correction of the platform stiffness. The second rollers 4 roll on the semi-circular cams 6, and their movement mode is similar to that of the first rollers 3, only rolling in the horizontal direction and maintaining a good contact and rolling relationship with the semi-circular cams 6. The change in the position and movement state of the second rollers 4 will cause the state change of the second air springs 2, thereby affecting the restoring force of the Stiffness Correction mechanism and having an important impact on the overall dynamic stiffness of the platform.

[0086] The Loadbearing mechanism and the Stiffness Correction mechanism act together on the load plate 7. Through the coordinated work of their respective components, the mechanical properties of the platform are adjusted under different working conditions. For example, when the load changes, the pressures of the first air springs 1 and the second air springs 2 can be adjusted, and at the same time, the rolling states of the first rollers 3 and the second rollers 4 on the wedges and cams will also change accordingly, so as to maintain the platform at the desired static equilibrium position (DSEP) or adjust the dynamic stiffness of the platform.

[0087] In the embodiments of the present invention, the air spring is connected to other components in the platform and realizes the transmission of force and the supporting effect through its own compression and expansion. When the platform is subjected to load or vibration excitation, the air spring will be compressed or expanded, and the internal air volume V changes. According to the ideal gas law, this will cause a change in air pressure, and thus a corresponding force F is generated. AS The effective area A of the air spring also plays an important role in the force transmission process. Its connection with other components of the platform enables the air spring to effectively transmit the generated force to the entire platform system and participate in the mechanical balance and vibration isolation processes of the platform. At the same time, the height change Δh (related to the displacement of the load plate) of the air spring will affect its restoring force F. LAS By working together with other components, they jointly maintain the performance of the platform.

[0088] Furthermore, it can be seen from Figure 3 that when the load plate undergoes displacement (such as the displacement amount y), it will cause height changes (Δh 1 and Δh 2 ) of the first air spring 1 and the second air spring 2. These height changes are closely related to geometric parameters such as the wedge angle α, the radius R of the semi-circular cam, the radius r of the roller, and the displacement y of the load plate. For example, the height change Δh 1 of the first air spring 1 = (H 0 -y)tan α. This geometric relationship determines the change in the compression state of the first air spring 1 during the displacement of the load plate, and thus affects the magnitude of its restoring force. Similarly, the height change of the second air spring 2 is also related to geometric parameters. This change will change the mechanical state of the stiffness correction mechanism and affect its correction effect on the platform stiffness. During the working process, the position change of the roller (roller) on the wedge and the cam always follows these geometric relationships, enabling the force transmission and mechanical property adjustment between the components of the platform to be carried out according to the design requirements, ensuring the stability and vibration isolation performance of the platform under different working conditions.

[0089] III. Experimental verification:

[0090] Through matlab simulation experiments, the performance of the adaptive vibration isolation platform is verified in the presence of external disturbances and parameter changes. The specific content is as follows:

[0091] A sine excitation with an amplitude of 10 mm and a frequency sweep from 0 to 6 Hz is applied to a 140 kg vibration isolation load. By comparing the vibration transmissibility of APVIP (pressure ratio μ = 1.8) and the platform without SCM, it is found that the vibration transmissibility of APVIP is smaller (about 1.4) at the resonance frequency (close to 2 Hz), and the isolation region extends to lower frequencies, proving that its isolation effect is better.

[0092] For a 90 kg vibration isolation load, the influence of different pressure ratios (μ = 1.1 and μ = 1.6) on the vibration transfer rate curve of the APVIP was experimentally evaluated. The results show that the isolation frequency range is wider, the resonance peak value is lower, and the frequency jump phenomenon disappears.

[0093] Experiments on the APVIP with a pressure ratio of 1.6 and an isolation mass of 90 kg and the SCM-free platform were carried out with multi-frequency excitation (a linear combination of 3 Hz, 3.5 Hz, and 4 Hz). By comparing the absolute displacement and acceleration responses, it is again proven that the isolation effect of the APVIP is better than that of the SCM-free platform. Moreover, the experiment also found that the displacement response frequency of the load plate is the same as the excitation, and the free vibration term decays due to positive damping, verifying the correctness of the theory.

[0094] From the description of the above embodiments, those skilled in the art can learn that the present invention aims at the problem that in a vibration isolation system, the dynamic stiffness of the vibration isolator needs to replace the elastic element or adjust the configuration parameters according to the change of the isolation load, and proposes an adaptive pneumatic vibration isolation platform to obtain an effective vibration isolation response of a quasi-zero stiffness vibration isolator when the vibration isolation mass changes. The adaptive pneumatic vibration isolation platform (APVIP) proposed by the present invention combines pneumatic technology and mechanical transmission technology. The load is supported by a positive stiffness mechanism, and the dynamic stiffness is reduced by a stiffness correction mechanism with negative stiffness, realizing flexible adjustment of the stiffness according to the change of the mass of the isolation object. In this way, both the load support ability is maintained, and a low dynamic stiffness can be obtained at the desired static equilibrium position (DSEP), effectively broadening the isolation area and improving the isolation effect, overcoming the problems of poor load adaptability and difficult stiffness adjustment of passive vibration isolators in the prior art. The present invention adjusts the pressure of the air spring to maintain the DSEP and obtain an ideal low dynamic stiffness. When the vibration isolation load changes, by adjusting the pressure of the air spring, the vibration isolation performance of the system can be effectively improved, avoiding problems such as excessive static deformation or balance position offset caused by load changes, and enabling the platform to maintain a good working state under different load conditions, which is difficult to achieve by traditional vibration isolation technology.

[0095] It should be noted that the word "comprising" does not exclude the existence of components or steps not listed in the claims. The word "a" or "an" preceding a component does not exclude the existence of a plurality of such components. The present invention can be implemented by means of hardware including several different components and by means of a suitably programmed computer.

[0096] This specification is described in a progressive manner. For the same or similar parts between each embodiment, reference can be made to each other. The unelaborated parts of the embodiments of the present invention can be obtained from the corresponding product specifications or the prior art in the art, which belong to the well-known content in the art and will not be elaborated too much.

[0097] The above has introduced the embodiments of the present invention in detail, and expounded the principles and implementation manners of the present invention. The description of the above embodiments is only used to help understand the method and its core idea of the present invention.

[0098] The above description of the disclosed embodiments enables those skilled in the art to implement or use the present invention. Various modifications to these embodiments will be obvious to those skilled in the art, and the general principles defined herein can be implemented in other embodiments without departing from the spirit or scope of the present invention. Therefore, the present invention will not be limited to these embodiments shown herein, but rather should be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. An adaptive pneumatic vibration isolation platform, characterized in that: The platform includes: a supporting mechanism and a stiffness correction mechanism, wherein: The support mechanism comprises: a first air spring, a first roller and a leg; the first air spring is connected to the first roller; the first roller is fitted with the leg; the leg has an inclined angle and is connected to the load plate as a wedge; during operation, the force of the first air spring is transmitted to the load plate through the first roller and the leg, providing a vertical support force to support the load plate; The stiffness correction mechanism includes: a second air spring, a second roller and a semicircular cam; the second air spring is connected to the second roller; the second roller is in contact with the semicircular cam; the semicircular cam is connected to the support leg; during operation, the second roller rolls on the surface of the semicircular cam, changes the state of the second air spring, generates a restoring force opposite to the supporting mechanism, and realizes the correction of the platform stiffness.

2. The adaptive pneumatic vibration isolation platform according to claim 1, characterized in that: The number of the first air springs is two.

3. The adaptive pneumatic vibration isolation platform according to claim 1, characterized in that: The first air spring is connected to the first roller through a linear bearing.

4. The adaptive pneumatic vibration isolation platform according to claim 1, characterized in that: The number of the second air springs is two.

5. The adaptive pneumatic vibration isolation platform according to claim 1, characterized in that: The second air spring is connected to the second roller via a linear bearing.

6. The adaptive pneumatic vibration isolation platform according to claim 1, characterized in that: The first roller moves in the horizontal direction and always rolls on the surface of the leg without sliding.

7. The adaptive pneumatic vibration isolation platform according to claim 1, characterized in that: The second roller moves in the horizontal direction and always rolls on the surface of the semicircular cam without sliding.

8. The adaptive pneumatic vibration isolation platform according to claim 1, characterized in that: The centers of the semicircular cam and the second roller are located on the same horizontal line.

Images