CN112696449A - Negative stiffness electromagnetic actuating mechanism suitable for low-frequency vibration reduction and isolation - Google Patents
Negative stiffness electromagnetic actuating mechanism suitable for low-frequency vibration reduction and isolation Download PDFInfo
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Abstract
The invention relates to a negative stiffness electromagnetic actuating mechanism suitable for low-frequency vibration reduction and isolation. The invention relates to the technical field of vibration control, wherein the mechanism comprises a displacement reducing device and an electromagnet mechanism; the invention can realize larger negative rigidity under the condition of moderate volume. The magnetic disc type electromagnet structure provides larger electromagnetic force, and the air gap size limits the working range of the dynamic displacement, and the size of the dynamic displacement can not exceed the size of the air gap. The invention has simple structure, easy processing, good anti-swing performance, simple and flexible installation mode and can be used in parallel with various positive stiffness springs and be randomly arranged on a controlled object or a base.
Description
Technical Field
The invention relates to the technical field of vibration control, in particular to a negative stiffness electromagnetic actuating mechanism suitable for low-frequency vibration reduction and isolation.
Background
The vibration isolation technology is used as an important technical means for vibration reduction and noise reduction, and aims to take certain measures between a vibration source and a system and arrange proper vibration suppression or vibration isolation equipment to isolate direct transmission of vibration. The traditional passive vibration isolator can only theoretically excite the frequency to be more than that of excitation frequency
The vibration of the multiple system natural frequency plays a role in attenuation, so in the field of low-frequency vibration isolation, the quasi-zero stiffness vibration isolation technology has gained more and more attention in recent years.
Most of the quasi-zero stiffness vibration isolators are formed by connecting positive and negative stiffness structures in parallel, and positive stiffness elements (such as springs and the like) provide static supporting capacity to offset positive stiffness by negative stiffness so as to realize quasi-zero stiffness. When the vibration isolation system displaces from a static balance position, the positive stiffness spring restrains the movement trend, the negative stiffness mechanism strengthens the movement trend of the displacement movement direction, the positive stiffness spring and the negative stiffness mechanism are connected in parallel, the total stiffness of the system can be reduced to be close to or equal to zero, meanwhile, high static stiffness and low dynamic stiffness are achieved, the vibration isolation frequency band is greatly widened, and the problem of low-frequency vibration isolation can be well solved.
The realization mode of the negative stiffness is taken as the key point of the quasi-zero stiffness technology, and the overall performance of the vibration isolation system is directly determined. Among a plurality of mechanisms for realizing negative stiffness, the electromagnetic mechanism has a flexible control mode, a control strategy can be formulated by designing a relevant controller, the control current can be adjusted on line according to the external excitation frequency, the vibration isolation performance of the mechanism is further improved, and the electromagnetic type negative stiffness executing mechanism has good accuracy and rapidity, so that the electromagnetic type negative stiffness executing mechanism gradually becomes a key point of research.
The magnetic disc type electromagnet mechanism has the characteristics of large electromagnetic force and quick suction, and when the magnetic disc type electromagnet mechanism is designed into a negative stiffness mechanism, the structure which is longitudinally arranged is adopted to realize negative stiffness, but the following problems can be caused: when the longitudinal arrangement is adopted, the overall longitudinal size of the vibration isolator is overlarge, the center of gravity is unstable during working, and the results of overturning, poor vibration isolation effect and the like are easily caused; in order to ensure that the vibration isolator has enough static supporting capacity, the positive stiffness spring is required to have enough compression space, in order to ensure the low dynamic stiffness of the vibration isolator, the negative stiffness mechanism is required to have high negative stiffness, the air gap of the electromagnet type negative stiffness mechanism is required to be small, the two requirements are mutually contradictory when the positive stiffness mechanism and the negative stiffness mechanism are connected in parallel, and due to the fact that the air gap is too small, when the vibration isolator works, the mechanism deviates from a static balance position, the working displacement of the vibration isolator is also limited by the size of the air gap, and the problems need to be solved urgently.
Disclosure of Invention
The invention considers the negative rigidity mechanism characteristic of the mechanism, the whole structure processing difficulty, the engineering applicability, the control difficulty and the like, and provides the following technical scheme:
a negative stiffness electromagnetic actuator suitable for low frequency vibration reduction and isolation is disclosed, which comprises a displacement zooming device and an electromagnet mechanism;
the displacement zooming device comprises a bottom rod, a top rod, a rod A, a rod B, a rod C, a rod D, a rod E and a rod F; the two ends of the ejector rod are connected with one ends of a rod E and a rod F, the other ends of the rod E and the rod F are respectively connected with one ends of a rod A and a rod B, the other ends of the rod A and the rod B are respectively connected with one ends of a rod C and a rod D, and the other ends of the rod C and the rod D are respectively connected with the two ends of the bottom rod;
the electromagnet mechanism includes: the magnetic isolation device comprises a stator A, a coil A, a stator B, a coil B, a magnetic isolation ring, a stator C, a coil C, a stator D, a coil D, an armature A and an armature B, wherein the armature A and the armature B are respectively arranged in the middle of a rod A and the rod B;
the coil A is wound in the stator A, the coil B is wound in the stator B, the coil C is wound in the stator C, the coil D is wound in the stator D, and the stator B and the stator C are fixed together with one surface of the magnetism isolating ring respectively.
Preferably, the armature a and the armature B correspond to the stator B and the stator C, respectively, an air gap exists between the armature a and the stator B, an air gap exists between the armature B and the stator C, the stator a and the stator B are symmetrical with respect to the armature a, and the stator D and the stator C are symmetrical with respect to the armature B.
Preferably, the displacement zooming device further comprises a rod M, a rod N, a rod O, a rod P, a rod Q and a rod R, wherein the rod M and the rod P are respectively connected with two ends of the bottom rod, one ends of the rod O and the rod R are respectively connected with two ends of the top rod, two ends of the rod N are respectively connected with the rod O and the rod M, and two ends of the rod Q are respectively connected with the rod P and the rod R.
Preferably, the electromagnet mechanism further includes: the motor comprises a stator E, a coil E, an armature C, a stator F, a coil F, a stator M, a coil M, an armature D, a stator N and a coil N;
the coil E is wound in the stator E, the coil F is wound in the stator F, the coil M is wound in the stator M, the coil N is wound in the stator N, the armature C is arranged in the middle of the rod N, and the armature D is arranged in the middle of the rod Q.
Preferably, the top rod and the bottom rod are the same in shape and size.
Preferably, the shape and size of the rod a, the rod B, the rod N and the rod Q are the same, and the shape and size of the rod C, the rod D, the rod E, the rod F, the rod M, the rod O, the rod P and the rod R are the same.
Preferably, the number of turns of the coil A, the coil B, the coil C, the coil D, the coil E, the coil F, the coil M and the coil N is the same, the diameters of the coils are equal, and the direct current is equal.
Preferably, the shape and size of the stator A, the stator B, the stator C, the stator D, the stator E and the stator F are the same, and the shape and size of the armature A, the armature B, the armature C and the armature D are the same.
Preferably, when in the static balance position, the air gaps among the stator A, the stator B and the armature A and the air gaps among the stator D, the stator C and the armature B are equal;
and air gaps among the stator E, the stator F and the armature C and air gaps among the stator M, the stator N and the armature D are all equal.
Preferably, the stator A, the stator B, the stator C, the stator D, the stator E, the stator F, the armature A, the armature B, the armature C and the armature D are all made of ferromagnetic materials with high magnetic permeability, and the magnetism isolating ring is made of magnetism isolating materials.
The invention has the following beneficial effects:
the invention can realize larger negative rigidity under the condition of moderate volume. The invention enlarges the range of the allowed dynamic displacement by the displacement zooming device, the electromagnetic force has better linearity, and simultaneously related structural parameters can be set to reduce the range of the allowed dynamic displacement, but the electromagnetic force and the negative stiffness generated by the mechanism can be improved, so the related structural parameters can be set according to different working requirements to realize different working characteristics, and the characteristics are not possessed by the existing negative stiffness spring. The invention has simple structure, easy processing, good anti-swing performance, simple and flexible installation mode and can be used in parallel with various positive stiffness springs and be randomly arranged on a controlled object or a base.
Drawings
FIG. 1 is a schematic structural diagram of a displacement zoom apparatus;
FIG. 2 is a schematic diagram of a displacement relationship of the displacement scaling device;
FIG. 3 is a schematic structural diagram of a negative stiffness electromagnetic actuator;
FIG. 4 is a schematic structural diagram of the expanded displacement zooming device;
FIG. 5 is a schematic structural diagram of the expanded negative stiffness electromagnetic actuator;
FIG. 6 is a schematic structural diagram of the negative stiffness electromagnetic actuator before a static load is not applied;
FIG. 7 is a schematic structural diagram of a negative stiffness electromagnetic actuator after a static load is applied;
FIG. 8 is a schematic structural view of the negative stiffness electromagnetic actuator in a static equilibrium position after being energized;
FIG. 9 is a schematic structural view of the negative stiffness electromagnetic actuator applying upward dynamic displacement after being energized;
FIG. 10 is a schematic structural view of the negative stiffness electromagnetic actuator applying downward dynamic displacement after being energized;
FIG. 11 is a graph of electromagnetic force versus displacement for a negative stiffness electromagnetic actuator;
FIG. 12 is a magnetic field profile for a negative stiffness electromagnetic actuator in a static equilibrium position;
FIG. 13 is a magnetic field profile for a negative stiffness electromagnetic actuator applying upward dynamic displacement;
FIG. 14 is a magnetic field profile for a negative stiffness electromagnetic actuator applying downward dynamic displacement;
Detailed Description
The present invention will be described in detail with reference to specific examples.
The first embodiment is as follows:
the invention aims to provide a negative-stiffness electromagnetic actuating mechanism suitable for low-frequency vibration reduction and isolation. The invention discloses a negative stiffness electromagnetic actuating mechanism suitable for low-frequency vibration reduction and isolation. In the invention, the realization principle of the negative rigidity is as follows: the vertical-direction dynamic displacement is converted into the changes of an air gap 1 between the armature A and the stator B, an air gap 2 between the armature B and the stator C, an air gap 3 between the stator A and the armature A and an air gap 4 between the stator D and the armature B in the horizontal direction, so that the change of the air gaps causes the change of electromagnetic force, and the negative stiffness is realized. The invention enlarges the range of the allowed dynamic displacement by the displacement scaling device, has better linearity, can set related structural parameters and reduce the range of the allowed dynamic displacement, but can improve the electromagnetic force and the negative rigidity generated by the mechanism, so the related structural parameters can be set according to different working requirements to realize different working characteristics, and the characteristics are not possessed by the traditional negative rigidity execution mechanism.
According to fig. 1 to 14, the present invention provides a negative stiffness electromagnetic actuator suitable for low frequency vibration reduction and isolation, and a negative stiffness electromagnetic actuator suitable for low frequency vibration reduction and isolation, wherein the actuators comprise a displacement zooming device and an electromagnet mechanism;
the displacement zooming device comprises a bottom rod, a top rod, a rod A, a rod B, a rod C, a rod D, a rod E and a rod F; the two ends of the ejector rod are connected with one ends of a rod E and a rod F, the other ends of the rod E and the rod F are respectively connected with one ends of a rod A and a rod B, the other ends of the rod A and the rod B are respectively connected with one ends of a rod C and a rod D, and the other ends of the rod C and the rod D are respectively connected with the two ends of the bottom rod;
the electromagnet mechanism includes: the magnetic isolation device comprises a stator A, a coil A, a stator B, a coil B, a magnetic isolation ring, a stator C, a coil C, a stator D, a coil D, an armature A and an armature B, wherein the armature A and the armature B are respectively arranged in the middle of a rod A and the rod B;
the coil A is wound in the stator A, the coil B is wound in the stator B, the coil C is wound in the stator C, the coil D is wound in the stator D, and the stator B and the stator C are fixed together with one surface of the magnetism isolating ring respectively.
The armature A and the armature B respectively correspond to the stator B and the stator C, an air gap exists between the armature A and the stator B, an air gap exists between the armature B and the stator C, the stator A and the stator B are symmetrical relative to the armature A, and the stator D and the stator C are symmetrical relative to the armature B.
The displacement zooming device further comprises a rod M, a rod N, a rod O, a rod P, a rod Q and a rod R, wherein the rod M and the rod P are respectively connected with the two ends of the bottom rod, one end of the rod O and one end of the rod R are respectively connected with the two ends of the ejector rod, the two ends of the rod N are respectively connected with the rod O and the rod M, and the two ends of the rod Q are respectively connected with the rod P and the rod R.
The electromagnet mechanism further includes: the motor comprises a stator E, a coil E, an armature C, a stator F, a coil F, a stator M, a coil M, an armature D, a stator N and a coil N;
the coil E is wound in the stator E, the coil F is wound in the stator F, the coil M is wound in the stator M, the coil N is wound in the stator N, the armature C is arranged in the middle of the rod N, and the armature D is arranged in the middle of the rod Q.
The top rod and the bottom rod are the same in shape and size.
Preferably, the shape and size of the rod a, the rod B, the rod N and the rod Q are the same, and the shape and size of the rod C, the rod D, the rod E, the rod F, the rod M, the rod O, the rod P and the rod R are the same.
And the number of turns of the coil A, the coil B, the coil C, the coil D, the coil E, the coil F, the coil M and the coil N is the same, the diameters of the coils are equal, and the direct current is equal.
The shape and the size of the stator A, the stator B, the stator C, the stator D, the stator E and the stator F are the same, and the shape and the size of the armature A, the armature B, the armature C and the armature D are the same.
When the stator is in a static balance position, air gaps among the stator A, the stator B and the armature A are equal to air gaps among the stator D, the stator C and the armature B;
and air gaps among the stator E, the stator F and the armature C and air gaps among the stator M, the stator N and the armature D are all equal.
The stator A, the stator B, the stator C, the stator D, the stator E, the stator F, the armature A, the armature B, the armature C and the armature D are all made of ferromagnetic materials with high magnetic conductivity, and the magnetism isolating ring is made of magnetism isolating materials.
The second embodiment is as follows:
as shown in fig. 1 to 5, the negative stiffness electromagnetic actuator suitable for low frequency vibration reduction and isolation according to the present invention comprises a displacement scaling device and an electromagnet mechanism, and the specific structure and connection manner are as follows:
as shown in fig. 1, the displacement zooming device is composed of a bottom rod, a top rod, a rod a, a rod B, a rod C, a rod D, a rod E and a rod F, and is characterized in that: the bottom rod is fixed with the basis, and the ejector pin bears the load, and pole C, pole D one end are connected with the bottom rod through the hinge respectively, and pole E, pole F one end are connected with the ejector pin through the hinge respectively, and pole A both ends are connected with pole C, pole E through the hinge respectively, and pole B both ends are connected with pole D, pole F through the hinge respectively.
As shown in fig. 2, when the displacement of the push rod of the displacement scaling device is Δ y, the respective displacements of the rod a and the rod B are both
According to the formulas (1), (2) and (3), the sizes of the structures in the displacement scaling device can be determined.
T＝T′+Δx，H＝H′+Δy (2)
In the formula, W is the distance between two hinge seats at the bottom; t-distance between the rods A, B when no load is applied; t' -the distance between the bars A, B after application of a load; l is1-the length of the bar A, B; h is the height of the displacement zooming device when no load is applied; h' -height of the displacement scaling device after applying the load; Δ x — the amount of displacement between the rod A, B before and after application of the load; and delta y represents the displacement of the ejector rod before and after the load is applied.
As shown in fig. 3, the electromagnet mechanism is composed of a stator a, a coil a, an armature a, a stator B, a coil B, a magnetic isolation plate, a stator C, a coil C, an armature B, a stator D, and a coil D, and is characterized in that: the coil A is wound in the stator A, the coil B is wound in the stator B, the coil C is wound in the stator C, the coil D is wound in the stator D, the stator B and the stator C are respectively fixed with one surface of the magnetic isolation plate, and the armature A and the armature B are respectively arranged in the middle of the rod A and the rod B. When in the static balance position, air gaps among the stator A, the stator B and the armature A and air gaps among the stator D, the stator C and the armature B are equal.
As shown in fig. 4, the displacement zooming device can be expanded in the transverse direction, and the above structure is added with a rod M, a rod N, a rod O, a rod P, a rod Q, and a rod R, and is characterized in that: one ends of the rod M and the rod P are respectively connected with the two ends of the bottom rod through hinges, and one ends of the rod O and the rod R are respectively connected with the two ends of the ejector rod through hinges.
As shown in fig. 5, correspondingly, the electromagnet mechanism may further include a stator E, a coil E, an armature C, a stator F, a coil F, a stator M, a coil M, an armature D, a stator N, and a coil N in the expanded structure, and is characterized in that: the coil E is wound in the stator E, the coil F is wound in the stator F, the coil M is wound in the stator M, the coil N is wound in the stator N, and the armature C is mounted in the middle of the rod N. When in the static equilibrium position, the air gaps between the stator E, the stator F and the armature C and between the stator M, the stator N and the armature D are all equal.
The positions of the bottom rod and the top rod can be changed according to the actual installation condition.
In the invention, the realization principle of the negative rigidity is as follows: the vertical-direction dynamic displacement is converted into the changes of an air gap 1 between the armature A and the stator B, an air gap 2 between the armature B and the stator C, an air gap 3 between the stator A and the armature A and an air gap 4 between the stator D and the armature B in the horizontal direction, so that the change of the air gaps causes the change of electromagnetic force, and the negative stiffness is realized.
The specific working process and principle are as follows:
as shown in fig. 6, for the negative stiffness electromagnetic actuator suitable for low frequency vibration reduction and isolation, when no static load is applied, the stator B and the stator C are respectively fixed with one surface of the magnetic isolation plate, the stator B and the stator C are fixed in the middle of the displacement zooming device, and the air gap 1 between the armature a and the stator B is
The air gap 2 between the armature B and the stator C is
The natural height of the displacement scaling device is H.
As shown in fig. 7, when a static load is applied, the height of the displacement scaling device is reduced by Δ y, which is H', and the air gap 1 between the armature a and the stator B and the air gap 2 between the armature B and the stator C are both reduced
The magnitude is g, and the position of the stator A, D is adjusted such that the air gap 3 between the stator a and the armature a, and the air gap 4 between the stator D and the armature B are g.
As shown in fig. 8, before a dynamic load is applied, the coil a, the coil B, the coil C and the coil D are energized, the electromagnetic attraction force between the stator a and the armature a is F1, the electromagnetic attraction force between the stator B and the armature a is F2, the electromagnetic attraction force between the stator C and the armature B is F3, the electromagnetic attraction force of the stator D to the armature B is F4, F1, F2, F3 and F4 are equal in size, the directions of F1 and F2 are opposite, the directions of F3 and F4 are opposite, and the armature a and the armature B are at a balanced position.
When an upward dynamic displacement Δ y' is applied, the armature a is displaced leftward as shown in fig. 9
Armature B is displaced to the right
The air gaps 3 and 4 are respectively reduced
The electromagnetic attraction forces F1 and F4 become larger, and the air gaps 1 and 2 become larger respectively
The electromagnetic attraction forces F2 and F3 become smaller, the system accelerates the upward movement trend, and the negative rigidity characteristic is realized.
When a downward dynamic displacement deltay' is applied, the armature a moves to the right, as shown in figure 10
The armature B moves leftwards
The air gaps 3 and 4 are enlarged respectively
The electromagnetic attraction forces F1 and F4 are reduced, and the air gaps 1 and 2 are respectively reduced
The electromagnetic attraction forces F2 and F3 become larger, the system accelerates the downward movement trend, and the negative rigidity characteristic is realized.
The relation between Δ y ' and Δ x ' conforms to equation (4), and accordingly, the relevant structural parameters can be designed to control the working range of the dynamic displacement Δ y '.
Taking the structural parameters in the table 1 as an example, when the parameter 1 is adopted, the range which can be reached by the electromagnetic force is the largest, the maximum value of the electromagnetic force and the magnitude of the negative stiffness are also the largest, but the allowable working displacement range is the smallest; when the parameter 3 is adopted, the range which can be reached by the electromagnetic force is the minimum, the maximum value of the electromagnetic force and the negative rigidity are also the minimum, but the allowable working range is the maximum; when the parameter 2 is adopted, the range which can be reached by the electromagnetic force, the maximum value of the electromagnetic force and the negative rigidity are between the parameter 1 and the parameter 3, and the allowable working displacement range is between the parameter 1 and the parameter 3.
TABLE 1 structural parameters
In the structure of the negative stiffness electromagnetic actuator, comsol software is selected as finite element electromagnetic field simulation software, an electromagnetic force-displacement curve of the negative stiffness electromagnetic actuator is shown in fig. 11, a magnetic field distribution diagram when the negative stiffness electromagnetic actuator is located at a static balance position is shown in fig. 12, a magnetic field distribution diagram when the negative stiffness electromagnetic actuator applies upward dynamic displacement is shown in fig. 13, and a magnetic field distribution diagram when the negative stiffness electromagnetic actuator applies downward dynamic displacement is shown in fig. 14.
The above description is only a preferred embodiment of the negative stiffness electromagnetic actuator suitable for low-frequency vibration reduction and isolation, and the protection range of the negative stiffness electromagnetic actuator suitable for low-frequency vibration reduction and isolation is not limited to the above embodiments, and all technical solutions belonging to the idea belong to the protection range of the present invention. It should be noted that modifications and variations which do not depart from the gist of the invention will be those skilled in the art to which the invention pertains and which are intended to be within the scope of the invention.
Claims (10)
1. The utility model provides a negative stiffness electromagnetic actuator suitable for vibration isolation is subtracted to low frequency which characterized by: the mechanism comprises a displacement zooming device and an electromagnet mechanism;
the displacement zooming device comprises a bottom rod, a top rod, a rod A, a rod B, a rod C, a rod D, a rod E and a rod F; the two ends of the ejector rod are connected with one ends of a rod E and a rod F, the other ends of the rod E and the rod F are respectively connected with one ends of a rod A and a rod B, the other ends of the rod A and the rod B are respectively connected with one ends of a rod C and a rod D, and the other ends of the rod C and the rod D are respectively connected with the two ends of the bottom rod;
the electromagnet mechanism includes: the magnetic isolation device comprises a stator A, a coil A, a stator B, a coil B, a magnetic isolation ring, a stator C, a coil C, a stator D, a coil D, an armature A and an armature B, wherein the armature A and the armature B are respectively arranged in the middle of a rod A and the rod B;
the coil A is wound in the stator A, the coil B is wound in the stator B, the coil C is wound in the stator C, the coil D is wound in the stator D, and the stator B and the stator C are fixed together with one surface of the magnetism isolating ring respectively.
2. The negative stiffness electromagnetic actuator of claim 1, wherein the negative stiffness electromagnetic actuator is adapted for low frequency vibration damping and isolation, and further comprises: the armature A and the armature B respectively correspond to the stator B and the stator C, an air gap exists between the armature A and the stator B, an air gap exists between the armature B and the stator C, the stator A and the stator B are symmetrical relative to the armature A, and the stator D and the stator C are symmetrical relative to the armature B.
3. The negative stiffness electromagnetic actuator of claim 1, wherein the negative stiffness electromagnetic actuator is adapted for low frequency vibration damping and isolation, and further comprises: the displacement zooming device further comprises a rod M, a rod N, a rod O, a rod P, a rod Q and a rod R, wherein the rod M and the rod P are respectively connected with the two ends of the bottom rod, one end of the rod O and one end of the rod R are respectively connected with the two ends of the ejector rod, the two ends of the rod N are respectively connected with the rod O and the rod M, and the two ends of the rod Q are respectively connected with the rod P and the rod R.
4. The negative stiffness electromagnetic actuator of claim 1, wherein the negative stiffness electromagnetic actuator is adapted for low frequency vibration damping and isolation, and further comprises: the electromagnet mechanism further includes: the motor comprises a stator E, a coil E, an armature C, a stator F, a coil F, a stator M, a coil M, an armature D, a stator N and a coil N;
the coil E is wound in the stator E, the coil F is wound in the stator F, the coil M is wound in the stator M, the coil N is wound in the stator N, the armature C is arranged in the middle of the rod N, and the armature D is arranged in the middle of the rod Q.
5. The negative stiffness electromagnetic actuator of claim 1, wherein the negative stiffness electromagnetic actuator is adapted for low frequency vibration damping and isolation, and further comprises: the top rod and the bottom rod are the same in shape and size.
6. The negative stiffness electromagnetic actuator of claim 3, wherein the negative stiffness electromagnetic actuator is adapted for low frequency vibration damping and isolation, and further comprises: the shape and size of the rod A, the rod B, the rod N and the rod Q are the same, and the shape and size of the rod C, the rod D, the rod E, the rod F, the rod M, the rod O, the rod P and the rod R are the same.
7. The negative stiffness electromagnetic actuator of claim 4, wherein the negative stiffness electromagnetic actuator is adapted for low frequency vibration reduction and isolation, and further comprises: and the number of turns of the coil A, the coil B, the coil C, the coil D, the coil E, the coil F, the coil M and the coil N is the same, the diameters of the coils are equal, and the direct current is equal.
8. The negative stiffness electromagnetic actuator of claim 4, wherein the negative stiffness electromagnetic actuator is adapted for low frequency vibration reduction and isolation, and further comprises: the shape and the size of the stator A, the stator B, the stator C, the stator D, the stator E and the stator F are the same, and the shape and the size of the armature A, the armature B, the armature C and the armature D are the same.
9. The negative stiffness electromagnetic actuator of claim 4, wherein the negative stiffness electromagnetic actuator is adapted for low frequency vibration reduction and isolation, and further comprises: when the stator is in a static balance position, air gaps among the stator A, the stator B and the armature A are equal to air gaps among the stator D, the stator C and the armature B;
and air gaps among the stator E, the stator F and the armature C and air gaps among the stator M, the stator N and the armature D are all equal.
10. The negative stiffness electromagnetic actuator of claim 4, wherein the negative stiffness electromagnetic actuator is adapted for low frequency vibration reduction and isolation, and further comprises: the stator A, the stator B, the stator C, the stator D, the stator E, the stator F, the armature A, the armature B, the armature C and the armature D are all made of ferromagnetic materials with high magnetic conductivity, and the magnetism isolating ring is made of magnetism isolating materials.
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| CN113202898A (en) * | 2021-05-27 | 2021-08-03 | 长沙理工大学 | Ultralow frequency vibration isolation device with real-time adjustable natural frequency |
| WO2021207633A3 (en) * | 2020-04-09 | 2021-11-18 | The Regents Of The University Of California | Prestrain adhesive for external respiratory measurement sensors |
| CN114215877A (en) * | 2021-12-27 | 2022-03-22 | 西安交通大学 | Hourglass-shaped wide-width broadband quasi-zero stiffness electromagnetic vibration isolator |
| CN114810928A (en) * | 2022-05-20 | 2022-07-29 | 浙江理工大学 | Hexagonal geometric amplification type magnetic suspension low-frequency vibration isolation structure |
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| CN109296684A (en) * | 2018-11-28 | 2019-02-01 | 西安交通大学 | A kind of 3 D electromagnetic vibration isolator based on the design of bidirectional displacement enlarging function |
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Cited By (5)
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| WO2021207633A3 (en) * | 2020-04-09 | 2021-11-18 | The Regents Of The University Of California | Prestrain adhesive for external respiratory measurement sensors |
| CN113202898A (en) * | 2021-05-27 | 2021-08-03 | 长沙理工大学 | Ultralow frequency vibration isolation device with real-time adjustable natural frequency |
| CN113202898B (en) * | 2021-05-27 | 2022-06-21 | 长沙理工大学 | Ultralow frequency vibration isolation device with real-time adjustable natural frequency |
| CN114215877A (en) * | 2021-12-27 | 2022-03-22 | 西安交通大学 | Hourglass-shaped wide-width broadband quasi-zero stiffness electromagnetic vibration isolator |
| CN114810928A (en) * | 2022-05-20 | 2022-07-29 | 浙江理工大学 | Hexagonal geometric amplification type magnetic suspension low-frequency vibration isolation structure |
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