CN111927912A - Quasi-zero rigidity vertical vibration isolator capable of realizing balance position adjustment - Google Patents
Quasi-zero rigidity vertical vibration isolator capable of realizing balance position adjustment Download PDFInfo
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- CN111927912A CN111927912A CN202010678379.7A CN202010678379A CN111927912A CN 111927912 A CN111927912 A CN 111927912A CN 202010678379 A CN202010678379 A CN 202010678379A CN 111927912 A CN111927912 A CN 111927912A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F3/00—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic
- F16F3/02—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic with springs made of steel or of other material having low internal friction
- F16F3/026—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic with springs made of steel or of other material having low internal friction to give a zero-spring rate characteristic
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/002—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion characterised by the control method or circuitry
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
- F16F15/06—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs
- F16F15/067—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs using only wound springs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
- F16F2228/06—Stiffness
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2230/00—Purpose; Design features
- F16F2230/0005—Attachment, e.g. to facilitate mounting onto confer adjustability
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2230/00—Purpose; Design features
- F16F2230/0011—Balancing, e.g. counterbalancing to produce static balance
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2230/00—Purpose; Design features
- F16F2230/08—Sensor arrangement
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2230/00—Purpose; Design features
- F16F2230/18—Control arrangements
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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- Acoustics & Sound (AREA)
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Abstract
The invention provides a quasi-zero stiffness vertical vibration isolator capable of realizing balance position adjustment, which comprises a bearing platform, a base, a positive stiffness spring, a negative stiffness mechanism, a transmission module and a control module, wherein the bearing platform and the base are matched with a cylindrical hole through a cylinder to realize sliding connection, the positive stiffness spring is sleeved on the outer sides of the cylindrical hole and the cylinder, the negative stiffness mechanism consists of an inclined guide rod and a negative stiffness spring, one end of the inclined guide rod is hinged with a boss at the bottom of the bearing platform, the other end of the inclined guide rod is arranged in a chute at the upper part of a supporting plate, the transmission module comprises a ball screw, a slider nut and a push rod, one end of the push rod penetrates through the inclined guide rod to be arranged at one end in the chute of. When the heavy material amount borne by the bearing platform changes, the transmission module and the control module are matched, so that the vibration isolator can still be in a quasi-zero stiffness state, has lower dynamic stiffness, and can effectively isolate low-frequency vibration.
Description
Technical Field
The invention relates to the technical field of vibration isolators, in particular to a quasi-zero stiffness vertical vibration isolator capable of realizing balance position adjustment.
Background
With the continuous development of scientific technology, the position of vibration isolation technology in industrial production is more and more important, especially for low-frequency vibration isolation. The initial vibration isolation frequency of the linear vibration isolation system being the natural frequency of the vibration isolation system
The initial vibration isolation frequency can be reduced only by reducing the natural frequency of the vibration isolation system, and the low-frequency vibration isolation performance is improved. However, reducing the natural frequency of the linear vibration isolation system reduces the stiffness of the system, and too low stiffness results in too large static displacement, thereby reducing the carrying capacity of the system. Due to the above limitations of linear vibration isolation systems, the application of nonlinear vibration isolation systems to low frequency vibration isolation has become a hot spot of research. The quasi-zero stiffness vibration isolator enables the dynamic stiffness near the balance position to approach zero through a positive stiffness and negative stiffness parallel connection mode, and ideal requirements of high static stiffness and low dynamic stiffness of the vibration isolator are met. In practical application, the bearing mass of the vibration isolator can change, and when the bearing mass changes, the vibration isolator still ensures lower dynamic stiffness, which is a problem to be solved in the design of the vibration isolator.
Disclosure of Invention
Aiming at the defects in the prior art, the invention provides the quasi-zero stiffness vertical vibration isolator capable of realizing balance position adjustment, so that the vibration isolator can still be in a quasi-zero stiffness vibration isolation state under the condition that the bearing mass of the vibration isolator is changed, and the negative influence caused by low-frequency vibration is isolated to the greatest extent.
The present invention achieves the above-described object by the following technical means.
A quasi-zero stiffness vertical vibration isolator capable of realizing balance position adjustment comprises a bearing platform, a base, a positive stiffness spring, a negative stiffness mechanism, a transmission module and a control module;
the bottom of the bearing platform is symmetrically provided with a cylinder, and the cylinder is matched with a cylindrical hole at the upper end of the base to realize sliding connection; the positive stiffness spring is sleeved outside the cylindrical hole and the cylinder; a supporting plate is fixed on the base;
the negative stiffness mechanism consists of an inclined guide rod and a negative stiffness spring sleeved on the inclined guide rod, one end of the inclined guide rod is hinged with a boss at the bottom of the bearing platform, and the other end of the inclined guide rod is arranged in a sliding groove at the upper part of the supporting plate;
the transmission module comprises a ball screw, a slider nut and a push rod, one end of the push rod penetrates through the inclined guide rod and is arranged at one end inside the sliding chute of the supporting plate, and the other end of the push rod is in pin connection with the slider nut to form a revolute pair; the slide block nut is matched with the ball screw;
the control module comprises a motor, a controller and a weight sensor, the weight sensor is arranged on the bearing platform, the weight sensor and the motor are both connected with the controller, and an output shaft of the motor is connected with the ball screw.
In a further technical scheme, the positive stiffness spring and the negative stiffness spring meet the requirements
Wherein k is1Stiffness of a positive stiffness spring, k2The stiffness of the negative stiffness spring, a is the distance between the tail end of the negative stiffness spring and the central axis of the vibration isolator, and theta0The angle between the initial position of the negative stiffness spring and the horizontal plane.
According to the further technical scheme, when the mass of the heavy object on the bearing platform changes, the control module and the transmission module adjust the position of the balance point of the vibration isolator, and the quasi-zero rigidity is achieved again.
In a further technical scheme, the adjustment of the balance point position of the vibration isolator is realized by controlling the rotation angle of a motor.
In a further technical scheme, the motor corner is used
Wherein m is the variation of the weight, p is the pitch of the ball screw, g is the gravitational acceleration, k1Is the stiffness of a positive stiffness spring.
According to a further technical scheme, the inclined guide rod is formed by slidably connecting a group of cylindrical bolts and is I-shaped.
According to a further technical scheme, the weight sensor, the controller and the motor are all powered by an external power supply.
According to a further technical scheme, two ends of the positive stiffness spring are respectively connected with the bearing platform and the base.
Compared with the prior vibration isolation technology, the invention has the following beneficial effects:
(1) according to the invention, the control module and the transmission module are introduced into the vibration isolator, when the heavy material amount borne by the bearing platform changes, the vibration isolator can still be in a quasi-zero stiffness state, has lower dynamic stiffness, and can effectively isolate low-frequency vibration;
(2) the distance between the support plate and the central axis of the vibration isolator can be adjusted, and when the vibration isolator is applied in different places and springs with different positive and negative stiffness need to be replaced, the distance between the support plate and the central axis of the vibration isolator is adjusted, so that the vibration isolator is in a quasi-zero stiffness state;
(3) the invention reduces the natural frequency of the vibration isolator by connecting the positive and negative stiffness springs in parallel, the dynamic stiffness of the balance point position is close to zero, and the low-frequency vibration isolation performance of the vibration isolator is improved.
Drawings
FIG. 1 is a schematic view of the quasi-zero stiffness vertical vibration isolator of the present invention in an unbalanced position;
FIG. 2 is a schematic view of the quasi-zero stiffness vertical vibration isolator of the present invention in a balanced position;
FIG. 3 is a schematic view of the base structure of the present invention;
FIG. 4 is a schematic diagram of a support plate structure according to the present invention;
FIG. 5 is a schematic view of a negative stiffness mechanism according to the present invention;
FIG. 6 is a three-dimensional view of a slider nut according to the present invention;
FIG. 7 is a schematic view of the quasi-zero stiffness vertical vibration isolator of the present invention showing negative stiffness stress;
FIG. 8 is a simplified schematic view of the quasi-zero stiffness vertical vibration isolator of the present invention in an initial operating state;
fig. 9 is a schematic diagram of a first balancing position of the quasi-zero stiffness vertical vibration isolator according to the present invention;
FIG. 10 is a simplified schematic diagram of the non-equilibrium position of the quasi-zero stiffness vertical vibration isolator according to the present invention;
fig. 11 is a schematic diagram of a second balancing position of the quasi-zero stiffness vertical vibration isolator according to the present invention;
wherein: 1. the device comprises a base, 2 positive stiffness springs, 3 supporting plates, 4 push rods, 5 negative stiffness springs, 6 inclined guide rods, 7 bearing platforms, 8 weight sensors, 9 controllers, 10 slide block nuts, 11 ball screws and 12 motors.
Detailed Description
The invention will be further described with reference to the following figures and specific examples, but the scope of the invention is not limited thereto.
As shown in fig. 1 and 2, the invention provides a quasi-zero stiffness vertical vibration isolator capable of realizing balance position adjustment, which comprises a bearing platform 7, a support module, a positive stiffness mechanism, a negative stiffness mechanism, a transmission module and a control module.
Four cylinders are symmetrically arranged at the bottom of the bearing platform 7, as shown in fig. 3, four cylindrical holes for inserting the cylinders are formed in the upper end of the base 1, and the cylinders are slidably connected with the cylindrical holes.
The positive stiffness mechanism is composed of four positive stiffness springs 2, the positive stiffness springs 2 are sleeved on the outer sides of the cylindrical hole and the cylinder, and two ends of each positive stiffness spring 2 are respectively connected with the bearing platform 7 and the base 1 to provide positive stiffness.
The supporting module consists of a base 1 and supporting plates 3, and the supporting plates 3 are symmetrically distributed at the upper end of the base 1 and positioned between the cylindrical holes; fig. 4 is a schematic view of the support plate 3, which has a sliding groove at the upper part and a T-bolt at the lower part to be fixed on the base 1.
A boss is arranged at the center of the bottom of the bearing platform 7 and is used for being connected with one end of the inclined guide rod 6, and the connection mode is revolute pair connection.
As shown in fig. 5, the negative stiffness mechanism comprises an inclined guide rod 6 and a negative stiffness spring 5 sleeved on the inclined guide rod, the inclined guide rod 6 is formed by slidably connecting a group of cylindrical pins, is i-shaped, and can extend or shorten along with the up-and-down movement of the bearing platform 7, one end of the inclined guide rod 6 is hinged with a boss at the bottom of the bearing platform 7, and the other end of the inclined guide rod is installed inside a sliding groove of the support plate 3.
The transmission module consists of a ball screw 11, a slider nut 10 and a push rod 4, one end of the push rod 4 passes through the inclined guide rod 6 and is arranged at one end inside the sliding chute of the support plate 3, and the other end of the push rod 4 is in pin connection with the slider nut 10 to form a revolute pair; fig. 6 is a schematic structural diagram of a slider nut 10 according to the present invention, in which the slider nut 10 is engaged with a ball screw 11, and moves up and down along with the rotation of the ball screw 11, and when the slider nut 10 moves up and down, the push rod 4 is driven to move, so that the other end of the inclined guide rod 6 moves up and down in the slide slot of the support plate 3, and the position of the negative stiffness mechanism is adjusted, thereby adjusting the balance position of the vibration isolator.
The control module comprises motor 12, controller 9 and weight sensor 8, and weight sensor 8 sets up on load-bearing platform 7, and motor 12 sets up in the square groove on base 1, and weight sensor 8 and motor 12 all are connected with controller 9 through the wire, and weight sensor 8, controller 9 and motor 12 are supplied power by external power source. An output shaft of the motor 12 is connected with the ball screw 11.
As shown in fig. 7, the stress diagram of the negative stiffness of the quasi-zero stiffness vertical vibration isolator is shown in the figures, AB and AC represent the i-shaped inclined guide rod 6, point a is the connection position of the inclined guide rod 6 and the boss at the bottom of the load-bearing platform 7, point B, C is the connection position of the inclined guide rod 6 and the sliding slot of the support plate 3, point a is the revolute pair connection, and point B, C is the sliding pair connection. The initial length of the negative rate spring 5 is L0Rigidity k2The angle between the initial position and the horizontal plane is theta0. The distance between the point A and the point B C is h0B, C is a distance from point O.
When the load-bearing platform 7 is loaded with a mass of heavy material, the vertical downward force F causes the load-bearing platform 7 to displace x, causing the negative rate spring 5 to compress, producing a vertical upward restoring force. According to the geometric relationship and the stress relationship of the positive and negative stiffness springs, the restoring force equation of the quasi-zero stiffness vertical vibration isolator is established as follows:
wherein: k is a radical of1Is the stiffness, k, of the positive stiffness spring 22The stiffness of the negative rate spring 5, the distance from the end of the negative rate spring to the point O is a, and the distance from the point A to the point O is h0Initial length of negative rate spring is L0The angle between the initial position of the negative stiffness spring and the horizontal plane is theta0And x is the displacement of the bearing platform 7 in the vertical direction.
And (3) the restoring force is subjected to derivation about x, and the stiffness equation of the quasi-zero stiffness vertical vibration isolator is obtained as follows:
in order to make the vertical vibration isolator of quasi-zero rigidity have zero dynamic rigidity at the equilibrium position (when the equilibrium position is the maximum compression amount of the inclined spring, the horizontal position of the negative rigidity mechanism, at this moment, x is 0), substitute the stiffness equation with x being 0, make K being 0, obtain:
stiffness k of a positive stiffness spring1Stiffness k of negative stiffness spring2Distance a between the end of the negative rate spring and point O, and initial length L of the negative rate spring 50When the relation is satisfied, the vibration isolator realizes quasi-zero rigidity vibration isolation.
When the vibration isolator is applied in different places and different positive and negative stiffness springs need to be replaced, the distance between the support plate 3 and the central axis of the vibration isolator is adjusted (namely, the distance a is adjusted), so that the formula (3) is always established, and the vibration isolator is in a quasi-zero stiffness state through the control module.
When the mass of the weight on the bearing platform 7 changes, the variable quantity is m, at the moment, the positive stiffness spring 2 is recovered or further compressed to a certain extent, the negative stiffness mechanism is not horizontal any more, and the original quasi-zero stiffness vibration isolation state is broken. The position of the balance point of the vibration isolator is adjusted through the action of the control module and the transmission module, and the quasi-zero rigidity is achieved again. The regulation of isolator balance point position is realized through the motor corner, and load-bearing platform's altitude variation can express through two kinds of modes, one kind is that the weight mass volume change on obtaining load-bearing platform by weight sensor 8 sensor, and the controller combines positive rigidity spring rate, calculates and obtains, and concrete formula is:
the second type is obtained by a ball screw principle, and the specific formula is as follows:
simultaneous equations (4), (5) can be obtained:
in the formula: theta is the rotation angle of the motor, p is the pitch of the ball screw, h is the height variation of the bearing platform, and g is the gravity acceleration.
The invention discloses a method for realizing a quasi-zero stiffness vertical vibration isolator capable of realizing balance position adjustment, which comprises the following steps of:
the method comprises the following steps: as shown in fig. 8, in an initial state, the quasi-zero stiffness vertical vibration isolator is unloaded, the dead weight of the bearing platform 7 is borne by the positive stiffness spring 2, and the negative stiffness spring 5 is in a free state;
step two: as shown in fig. 9, let mass m1The weight is placed on the bearing platform 7, and the positive and negative stiffness springs are compressed; the weight sensor 8 measures the change m of the weight substance quantity on the bearing platform 71The mass variation is transmitted to the controller 9, and the controller 9 calculates the rotation angle of the motor 12
The motor 12 is controlled to rotate, the ball screw 11 is driven to rotate,thereby driving the slide block nut 10 to slide on the ball screw 11, further driving the push rod 4 to move, and finally enabling one end of the negative stiffness mechanism to move up and down in the chute of the support plate 3, so that the negative stiffness mechanism is in a horizontal state, and realizing quasi-zero stiffness;
step three: as shown in FIGS. 10 and 11, the mass of the weight on the load bearing platform 7 changes without increasing the mass by m2At this time, the positive stiffness spring 2 is further compressed, the negative stiffness spring 5 is no longer in a horizontal state, that is, the vibration isolator is no longer in a quasi-zero stiffness state, and the vibration isolation effect is deteriorated; the weight sensor 8 measures the amount m of the heavy substance on the bearing platform 72The mass variation signal is transmitted to the controller 9, and the controller 9 calculates the rotation angle of the motor
The motor is controlled to rotate to drive the ball screw 11 to rotate, so that the slider nut 10 is driven to slide on the ball screw 11, the push rod 4 is driven to move, and finally one end of the negative stiffness mechanism moves up and down in the chute of the support plate 3, so that the negative stiffness mechanism is in a horizontal state, and quasi-zero stiffness is realized; when the mass of the heavy object on the bearing platform 7 is reduced, the implementation method is similar to the process;
step four: as shown in fig. 8, when the heavy object on the bearing platform 7 is unloaded, namely the vibration isolator is unloaded, the controller controls the reverse rotation angle theta of the motor3＝θ1+θ2So that the vibration isolator is restored to the initial state.
In summary, the vibration isolator in this embodiment can adjust the position of the quasi-zero stiffness balance point according to different bearing qualities, so that the vibration isolator works in a quasi-zero stiffness state, and the low-frequency vibration isolation performance is improved.
The present invention is not limited to the above-described embodiments, and any obvious improvements, substitutions or modifications can be made by those skilled in the art without departing from the spirit of the present invention.
Claims (8)
1. A quasi-zero stiffness vertical vibration isolator capable of achieving balance position adjustment is characterized by comprising a bearing platform (7), a base (1), a positive stiffness spring (2), a negative stiffness mechanism, a transmission module and a control module;
cylinders are symmetrically arranged at the bottom of the bearing platform (7), and are matched with cylindrical holes at the upper end of the base (1) to realize sliding connection; the positive stiffness spring (2) is sleeved on the outer sides of the cylindrical hole and the cylinder; a support plate (3) is fixed on the base (1);
the negative stiffness mechanism consists of an inclined guide rod (6) and a negative stiffness spring (5) sleeved on the inclined guide rod, one end of the inclined guide rod (6) is hinged with a boss at the bottom of the bearing platform (7), and the other end of the inclined guide rod is arranged in a sliding groove at the upper part of the support plate (3);
the transmission module comprises a ball screw (11), a slider nut (10) and a push rod (4), one end of the push rod (4) penetrates through the inclined guide rod (6) and is installed at one end inside the sliding groove of the support plate (3), and the other end of the push rod (4) is in pin connection with the slider nut (10) to form a revolute pair; the slide block nut (10) is matched with the ball screw (11);
the control module comprises a motor (12), a controller (9) and a weight sensor (8), the weight sensor (8) is arranged on the bearing platform (7), the weight sensor (8) and the motor (12) are both connected with the controller (9), and an output shaft of the motor (12) is connected with a ball screw (11).
2. The quasi-zero stiffness vertical vibration isolator capable of achieving balance position adjustment according to claim 1, wherein the positive stiffness spring and the negative stiffness spring meet the requirement
Wherein k is1Stiffness of a positive stiffness spring, k2The stiffness of the negative stiffness spring, a is the distance between the tail end of the negative stiffness spring and the central axis of the vibration isolator, and theta0The angle between the initial position of the negative stiffness spring and the horizontal plane.
3. The quasi-zero stiffness vertical vibration isolator capable of achieving balance position adjustment according to claim 1, characterized in that when the mass of a heavy object on the bearing platform (7) changes, the control module and the transmission module adjust the position of the balance point of the vibration isolator to achieve quasi-zero stiffness again.
4. The quasi-zero stiffness vertical vibration isolator with adjustable balance position according to claim 3, wherein the adjustment of the balance position of the vibration isolator is realized by controlling the rotation angle of a motor.
5. The quasi-zero stiffness vertical vibration isolator capable of achieving balance position adjustment according to claim 4, wherein the motor corner passing through is
Wherein m is the variation of the weight, p is the pitch of the ball screw, g is the gravitational acceleration, k1Is the stiffness of a positive stiffness spring.
6. The quasi-zero stiffness vertical vibration isolator capable of realizing balance position adjustment according to claim 1, characterized in that the inclined guide rod (6) is formed by slidably connecting a group of cylindrical pins and is in an I shape.
7. The quasi-zero stiffness vertical vibration isolator capable of achieving balance position adjustment according to claim 1, characterized in that the weight sensor (8), the controller (9) and the motor (12) are all powered by an external power supply.
8. The quasi-zero stiffness vertical vibration isolator capable of realizing balance position adjustment according to claim 1, characterized in that two ends of the positive stiffness spring (2) are respectively connected with the bearing platform (7) and the base (1).
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| CN114183495A (en) * | 2021-12-10 | 2022-03-15 | 中国人民解放军海军工程大学 | Quasi-zero stiffness vibration isolator with negative stiffness capable of being adaptively adjusted |
| CN114321248A (en) * | 2021-12-11 | 2022-04-12 | 北京工业大学 | Dynamic balance type vertical shock isolator |
| CN114838074A (en) * | 2022-05-30 | 2022-08-02 | 黑龙江大学 | Constant-tension buffer mechanism based on hinge zero-stiffness spring |
| CN115523254A (en) * | 2022-09-23 | 2022-12-27 | 北京工业大学 | Wide-stroke high-static-load connecting rod type quasi-zero stiffness vibration isolator |
| CN116164065A (en) * | 2023-02-24 | 2023-05-26 | 东莞理工学院 | Two-degree-of-freedom quasi-zero stiffness vibration isolator for polishing equipment |
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