CN203082103U - Vibration isolator - Google Patents
Vibration isolator Download PDFInfo
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- CN203082103U CN203082103U CN 201320030988 CN201320030988U CN203082103U CN 203082103 U CN203082103 U CN 203082103U CN 201320030988 CN201320030988 CN 201320030988 CN 201320030988 U CN201320030988 U CN 201320030988U CN 203082103 U CN203082103 U CN 203082103U
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Abstract
The utility model provides a vibration isolator which is suitable for the fields of automobiles, precision machine tools, measuring apparatuses, ships and warships, spacecrafts and aircrafts and the like. Through repulsive force produced when an electromagnet and a permanent magnet face towards each other through magnetic poles with the same polarity, the vibration isolator, a perpendicular linear spring and a motor are combined through connecting rods to form a geometrically nonlinear structure, the magnetic distance and rigidity of the perpendicular linear spring can meet a certain relationship through adjustment of a magnet distance regulator, and therefore rigidity of a system at the equilibrium position is zero, and low-frequency vibration isolation or ultra-low-frequency vibration isolation is achieved. According to the vibration isolator, the vibration isolator has large static rigidity and small dynamic rigidity, a good low-frequency vibration isolation effect and a good ultra-low-frequency vibration isolation effect, the vibration isolator can not only ensure zero rigidity characteristics of mass blocks with different weights in an equilibrium state, but also achieve a good vibration isolation effect when vibration isolated mass blocks are under the high excitation frequency.
Description
Technical field
The utility model relates to the vibration isolation field, relates in particular to a kind of vibration isolator.
Background technique
Along with being growing more intense of expanding economy and social competition, people require more and more higher to the vibration isolation technique of some equipment.Yet those bad vibrations affect a lot of mechanical structures, make their normal operations run into problem, or affect people's work, make the people produce discomfort, or produce the problem of others.Latent sound property during such as the high-comfort requirement of, automobile, navigation of submarine, the proper functioning of high-precision surveying instrument etc., all more and more stricter to the requirement of vibration isolation.
The modal method that is used for controlling bad vibration is to use the passive vibration isolation device in the prior art, as accurate zero stiffness magnetic force passive vibration isolation device, though accurate zero stiffness magnetic force passive vibration isolation device has solved the low frequency vibration isolation problem under the certain condition, but because there is intrinsic defective in passive vibration isolation, limited the further perfect of anti-vibration performance, in use find: when by the mass change of vibration isolation mass block, the zero stiffness of whole vibrating isolation system under equilibrium state disappears, and makes the low frequency vibration isolation effect descend; When by the vibration isolation mass block under upper frequency excitation, the vibration isolating effect of accurate zero stiffness vibrating isolation system is worse than the vibration isolating effect of corresponding linear system.
The model utility content
The technical problems to be solved in the utility model is, a kind of vibration isolator is provided, and this vibration isolator has bigger quiet rigidity and less dynamic rate, has good low frequency or superlow frequency vibration isolating effect.
In order to solve the problems of the technologies described above, the utility model provides a kind of vibration isolator, is used to isolate the vibrations by the vibration isolation thing, comprising:
Panel describedly is positioned on the described panel by the vibration isolation thing;
Hookean spring is provided with described panel is vertical, and first end of described Hookean spring is connected with described panel;
Motor comprises output shaft and shell, and described output shaft is connected with second end of described Hookean spring, controls described Hookean spring by the output length that changes described output shaft and is stretching or compressive state;
Be used to install the pedestal of described motor;
Be used for being controlled the decrement of described output shaft by the vibration isolation thing in the mass change and/or the frequency change of vibration processes to described Hookean spring according to described, the control unit that the positive rigidity that described Hookean spring is produced equates with the absolute value of negative stiffness, described control unit is installed on the described pedestal, and described control unit is connected with described motor.
Described vibration isolator comprises that also two groups are connected with described panel respectively, be used to support described panel, the magnetic force Flexible element that the further positive rigidity that guarantees that described Hookean spring produces equates with the absolute value of negative stiffness, described two groups of magnetic force Flexible elements are arranged on the described pedestal, are that symmetry axis is symmetrical distribution with described output shaft between described two groups of magnetic force Flexible elements.
Described magnetic force Flexible element comprises:
Linear rail, described linear rail are installed on the described pedestal, and wherein an end is connected with described shell;
First slide block, described first slide block is placed on the described linear rail, and can on described linear rail, be free to slide, upper end at described first slide block is equipped with permanent magnet by mounting bracket, described mounting bracket is hinged by connecting rod and described panel, and articulating point and described linear rail are in the homonymy of described output shaft;
Second slide block, described second slide block is placed on the described linear rail, and the upper end of described second slide block is equipped with electromagnet, and described electromagnet is connected with described control unit, and described second slide block can slide on described linear rail;
Be used to regulate the range adjuster of the relative distance between described second slide block and described first slide block, described range adjuster is installed on the described pedestal, and is connected with described second slide block.
The distance of described output shaft is arrived at the center of described first slide block less than the center of described second slide block to the distance of described output shaft.
Described permanent magnet is relative with the homopolarity of described electromagnet
The axis of described output shaft and described Hookean spring is on the same axis.
Described panel comprises:
Top plate describedly is placed on the described top plate by the vibration isolation thing, and is provided with also on the described top plate that to be used for perception described by the frequency sensor of vibration isolation thing;
Lower panel, described lower panel places the top of described Hookean spring, and be connected with described Hookean spring, be parastate between described top plate and the described lower panel, and be provided with between described top plate and the described lower panel that to be used for perception described by the mass sensor of vibration isolation amount of substance.
The beneficial effects of the utility model are:
1, this vibration isolator has bigger quiet rigidity and less dynamic rate, has good low frequency or superlow frequency vibration isolating effect.
2, this vibration isolator not only can guarantee the zero stiffness characteristic of mass block when equilibrium state of different quality, and can realize by vibration isolation mass block vibration isolating effect preferably under higher energizing frequency.
Description of drawings
Fig. 1 is the mechanical construction drawing of the utility model embodiment's vibration isolator;
Fig. 2 is the schematic diagram of mechanical structure of the utility model embodiment's vibration isolator;
Fig. 3 is the structural drawing of electronic control system.
Embodiment
For making the purpose of this utility model, technological scheme and advantage clearer, below in conjunction with the accompanying drawings and the specific embodiments the utility model is described in detail.
In following embodiment of the present utility model, the utility model is described in detail from mechanical construction drawing and working principle two aspects.
It at first is mechanical construction drawing.
The mechanical construction drawing of vibration isolator described in the utility model please refer to Fig. 1 as shown in Figure 1, and described vibration isolator comprises:
Motor 3, described motor 3 comprises output shaft 4 and shell 5, described output shaft 4 is connected with second end of described Hookean spring 2, controls described Hookean spring 2 by the output length that changes described output shaft 4 and is stretching or compressive state;
Be used to install the pedestal 7 of described motor 3, described pedestal 7 is a smooth panel, is seamless the contact with surface of contact in the use, plays the effect of supporting described vibration isolator miscellaneous part.
Be used for the decrement of being controlled 4 pairs of described Hookean springs 2 of described output shaft by vibration isolation thing 25 in the mass change and/or the frequency change of vibration processes according to described, the control unit 6 that the positive rigidity that described Hookean spring 2 is produced equates with the absolute value of negative stiffness, described control unit 6 is installed in an end of described pedestal 7, and described control unit 6 is connected with described motor 3.
The power that is produced when compressing described Hookean spring 2 for the power that guarantees described Hookean spring 2 to be produced in when vibration by vibration isolation thing 25 and described output shaft 4 is in same straight line, and then make above-mentioned vibration isolator have good vibration isolating effect, so the axis of described output shaft 4 and described Hookean spring 2 is on the same axis.
For perception by the vibration frequency of vibration isolation thing 25 and quality, described panel 1 comprises top plate 16, wherein, describedly be placed on the described top plate 16 by vibration isolation thing 25, plate 16 is provided with that to be used for perception described by the frequency sensor 18 of the vibration frequency of vibration isolation thing 25 in the above;
The working procedure of above-mentioned vibration isolator is such, after being placed on the panel 1 by vibration isolation thing 25, control unit 6 is according to by the vibration frequency of vibration isolation thing 25 and weight, control the decrement of 3 pairs of Hookean springs 2 of motor according to the stiffness coefficient of Hookean spring 2, make the positive rigidity that decrement produced exhausted of under the decrement of correspondence 4 pairs of Hookean springs 2 of output shaft absolute value with by 25 vibrations of vibration isolation thing the time equate to the negative stiffness of Hookean spring 2 generations, positive negative stiffness is offset, and reaches the effect of shock insulation.
Above-mentioned vibration isolator, control the decrement of 4 pairs of Hookean springs 2 of output shaft owing to use control unit 6, make under the decrement of correspondence the exhausted of positive rigidity that Hookean spring 2 is produced absolute value to the negative stiffness of Hookean spring 2 generations with the time equate by 25 vibrations of vibration isolation thing, even so be in low-frequency vibration by the vibration isolation thing, above-mentioned vibration isolator also can play vibration isolating effect.
For above-mentioned vibration isolator when being in low frequency or superlow frequency vibrating by the vibration isolation thing has better vibration isolating effect, above-mentioned vibration isolator comprises that also two groups are used for auxiliary magnetic force Flexible element of isolating low-frequency vibration or superlow frequency vibrating, described two groups of magnetic force Flexible elements are arranged on the described pedestal 7, be that symmetry axis is symmetrical distribution with described output shaft 4 between described two groups of magnetic force Flexible elements, and described two groups of magnetic force Flexible elements are connected with described panel 1 respectively.
With reference to Fig. 1, wherein one group of magnetic force Flexible element comprises:
The upper end of described second slide block 13 is equipped with electromagnet 14, and described electromagnet 14 is connected with described control unit 6, and described second slide block 13 can slide on described linear rail 8;
Be used to regulate the range adjuster 15 of the relative distance between described second slide block 13 and described first slide block 9, described range adjuster 15 is installed on the described pedestal 7, and is connected with described second slide block 13.
Above-mentioned magnetic force Flexible element is to utilize the repulsive force of 14 of described permanent magnet 10 and described electromagnet to realize low frequency vibration isolation, so be that homopolarity is relative between described permanent magnet 10 and the described electromagnet 14.
After increasing above-mentioned two groups of magnetic force Flexible elements, the working procedure of whole vibration isolator is such: at first, after being placed on the top plate 19 by vibration isolation thing 25, mass sensor 20 is sensed described by the weight of vibration isolation thing, and give control unit 6 with this weight transmitting, control unit 6 is according to by the weight signal of vibration isolation thing 25, and controls the decrement of 3 pairs of Hookean springs 2 of motor according to the stiffness coefficient of Hookean spring 2, guarantees that connecting rod 12 is the level of state when the equipoise; Then, control unit 6 is according to the stiffness coefficient of Hookean spring 2, and by the spacing that range adjuster 15 comes regulating magnet 14 and corresponding permanent magnet 10, what realize system is the zero stiffness characteristic when the equipoise; At last, during by vibration isolation thing 25 vibrations, frequency sensor 18 records by the frequency of the vibrations of vibration isolation thing 25, and this vibration frequency is passed to control unit 6 when described, and whether control unit 6 switches on to electromagnet 14 according to the size decision of vibration frequency.If system is in low-frequency vibration, electromagnet 14 continues energising, and system has good low frequency vibration isolation effect.But find by theoretical and experiment, if under the vibration frequency condition with higher of vibration isolation thing 25, vibration isolating effect is undesirable, this moment, control unit 6 can stop the energising to electromagnet 14, system recovery is linear vibrating isolation system, has good vibration isolating effect equally.
Next is a working principle.
Fig. 2 is that the working principle of vibration isolator described in the utility model is, in conjunction with Fig. 2, because this vibration isolator is a symplex structure, present embodiment is an example with permanent magnet 10 places one side, and opposite side in like manner.
Under original state, a distance that to be permanent magnet 10 order with B, wherein the B point is the axis at output shaft 4 places and the intersection point of pedestal 7, the A point is the upper extreme point of Hookean spring 3, h be A point and B dot spacing from,
X is the displacement that the A point leaves initial position.Distance between D electromagnet 14 and the permanent magnet 10.In addition, p hereinafter
1, p
2, q
1It is the magnetic force coefficient.The magnetic force coefficient records by experiment, does not elaborate herein.
After being placed the A point, make by vibration isolation thing 25 arrival equilibrium position B points by motor 3 by vibration isolation thing 25.The magnetic force Flexible element that repulsion produced that electromagnet 14 and permanent magnet are 10 provides negative stiffness in vertical direction, owing to Hookean spring 2 is compressed, so Hookean spring 2 provides positive rigidity in vertical direction.By adjustable range regulator 6 come regulating magnet 14 and permanent magnet 10 between distance, can change the negative stiffness of magnetic force Flexible element, make positive rigidity just equate with the absolute value of negative stiffness, positive rigidity is just just offset with negative under state of equilibrium, the rigidity of system when the equilibrium position is zero, thereby realizes vibration isolation.
The power f that whole system is subjected to can be expressed as:
Y=x-h wherein, the rigidity of whole system can draw by the differentiate to formula (1):
The condition that accurate zero stiffness is realized is:
According to formula (3), can the regulating magnet range adjuster system that makes when the equilibrium position, have accurate zero stiffness characteristic.Can be expressed as by the quality of vibration isolation thing 25:
m=k
qzs(h+d)/g （4）
When being changed by the quality of vibration isolation thing 25, weighing transducer 20 can be the weight information transmit control unit 6 of vibration isolation thing 25.Control unit 6 calculates the pre compressed magnitude d of Hookean spring 2 according to formula (4).Then, control unit 6 is controlled the elongation and the contour projector of the output shaft 4 of motor 2 according to decrement d.Thereby the realization system is when the equilibrium position, and connecting rod is a substantially horizontal, has accurate zero stiffness characteristic, also just has best vibration isolating effect.
Electronic control system of the present utility model as shown in Figure 3, in conjunction with Fig. 3, when vibration frequency was low frequency (0-10Hz), frequency sensor 18 passed to control unit 6 to signal.Control unit 6 makes electromagnet 14 energisings according to this signal, produces the magnetic force that repels mutually with permanent magnet 10.When vibration frequency was high frequency (greater than 10HZ), control unit 6 made electromagnet 14 outages according to signal, and this moment, repulsive force disappeared, and no negative stiffness produces.Whole vibrating isolation system is linear vibrating isolation system, also has good vibration isolating effect.
Because two groups of magnetic force Flexible elements are symmetrically distributed, so other one group of magnetic force Flexible element is in full accord at mechanical structure, working principle and above-mentioned magnetic force Flexible element, repeat no more here.
It is to be noted, originally be the magnetic force Flexible element that the embodiment of model utility is not limited to said structure, can also use other similar or close Flexible elements of mode of structure with it, as long as working principle with above-mentioned consistent, all is the scope that the utility model is contained.
The above only is a preferred implementation of the present utility model; should be pointed out that for those skilled in the art, under the prerequisite that does not break away from the utility model principle; can also make some improvements and modifications, these improvements and modifications also should be considered as protection domain of the present utility model.
Claims (7)
1. a vibration isolator is used to isolate the vibrations by the vibration isolation thing, it is characterized in that, comprising:
Panel describedly is positioned on the described panel by the vibration isolation thing;
Hookean spring is provided with described panel is vertical, and first end of described Hookean spring is connected with described panel;
Motor comprises output shaft and shell, and described output shaft is connected with second end of described Hookean spring, controls described Hookean spring by the output length that changes described output shaft and is stretching or compressive state;
Be used to install the pedestal of described motor;
Be used for being controlled the decrement of described output shaft by the vibration isolation thing in the mass change and/or the frequency change of vibration processes to described Hookean spring according to described, the control unit that the positive rigidity that described Hookean spring is produced equates with the absolute value of negative stiffness, described control unit is installed on the described pedestal, and described control unit is connected with described motor.
2. vibration isolator according to claim 1 is characterized in that:
Described vibration isolator comprises that also two groups are connected with described panel respectively, be used to support described panel, the magnetic force Flexible element that the further positive rigidity that guarantees that described Hookean spring produces equates with the absolute value of negative stiffness, described two groups of magnetic force Flexible elements are arranged on the described pedestal, are that symmetry axis is symmetrical distribution with described output shaft between described two groups of magnetic force Flexible elements.
3. vibration isolator according to claim 2 is characterized in that, described magnetic force Flexible element comprises:
Linear rail, described linear rail are installed on the described pedestal, and wherein an end is connected with described shell;
First slide block, described first slide block is placed on the described linear rail, and can on described linear rail, be free to slide, upper end at described first slide block is equipped with permanent magnet by mounting bracket, described mounting bracket is hinged by connecting rod and described panel, and articulating point and described linear rail are in the homonymy of described output shaft;
Second slide block, described second slide block is placed on the described linear rail, and the upper end of described second slide block is equipped with electromagnet, and described electromagnet is connected with described control unit, and described second slide block can slide on described linear rail;
Be used to regulate the range adjuster of the relative distance between described second slide block and described first slide block, described range adjuster is installed on the described pedestal, and is connected with described second slide block.
4. vibration isolator according to claim 3 is characterized in that: the distance of described output shaft is arrived at the center of described first slide block less than the center of described second slide block to the distance of described output shaft.
5. vibration isolator according to claim 3 is characterized in that: described permanent magnet is relative with the homopolarity of described electromagnet.
6. vibration isolator according to claim 1 is characterized in that: the axis of described output shaft and described Hookean spring is on the same axis.
7. vibration isolator according to claim 1 is characterized in that, described panel comprises:
Top plate describedly is placed on the described top plate by the vibration isolation thing, and is provided with also on the described top plate that to be used for perception described by the frequency sensor of vibration isolation thing;
Lower panel, described lower panel places the top of described Hookean spring, and be connected with described Hookean spring, be parastate between described top plate and the described lower panel, and be provided with between described top plate and the described lower panel that to be used for perception described by the mass sensor of vibration isolation amount of substance.
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| CN 201320030988 CN203082103U (en) | 2013-01-21 | 2013-01-21 | Vibration isolator |
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Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104154170A (en) * | 2014-08-01 | 2014-11-19 | 安徽工程大学 | Parallel mechanism based multidimensional vibration platform |
| CN104329407A (en) * | 2014-10-20 | 2015-02-04 | 中科院南京天文仪器有限公司 | Vibration reducing device for mobile type equipment |
| CN104763765A (en) * | 2015-04-10 | 2015-07-08 | 山东大学 | Novel high static and low dynamic rigidity piecewise linear vibration isolator and work method thereof |
| CN105546028A (en) * | 2016-02-02 | 2016-05-04 | 泰州市凯华柴油发电机组有限公司 | Diesel generator with variable spring support and vibration reducing control method of diesel generator |
| CN105587822A (en) * | 2014-10-22 | 2016-05-18 | 无锡利博科技有限公司 | Supporting and looseness preventing buffer structure of machine tool equipment |
| CN105864339A (en) * | 2016-06-01 | 2016-08-17 | 福州大学 | Quasi-zero stiffness vibration isolator applicable to isolation of micro-amplitude and low-frequency vibration and realization method of quasi-zero stiffness vibration isolator |
| CN106763466A (en) * | 2015-11-21 | 2017-05-31 | 北京工业大学 | A kind of novel positive and negative Stiffness low frequency vibration isolation mechanism |
| CN108533653A (en) * | 2018-04-26 | 2018-09-14 | 合肥工业大学 | It is a kind of that novel negative stiffness structure that stablizing negative stiffness value can be provided |
| CN108953448A (en) * | 2018-08-10 | 2018-12-07 | 浙江理工大学 | A kind of novel permanent magnetic formula bistable state vibration isolator |
| CN108953482A (en) * | 2018-09-20 | 2018-12-07 | 南京航空航天大学 | A kind of quasi- zero stiffness vibrating isolation system of centering type |
| CN112696454A (en) * | 2020-12-28 | 2021-04-23 | 哈尔滨工程大学 | Magnetic suspension type quasi-zero stiffness electromagnetic vibration isolator with active negative stiffness |
| CN112963499A (en) * | 2021-02-22 | 2021-06-15 | 江苏大学 | Vibration isolator based on parallel connection of positive stiffness and negative stiffness of magnetic attraction member and control method of vibration isolator |
| CN114658783A (en) * | 2022-03-22 | 2022-06-24 | 中国人民解放军海军工程大学 | Quasi-zero stiffness vibration isolator with adjustable positive and negative stiffness |
| CN114857194A (en) * | 2022-03-22 | 2022-08-05 | 中国人民解放军海军工程大学 | Electromagnetic negative stiffness device |
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2013
- 2013-01-21 CN CN 201320030988 patent/CN203082103U/en not_active Expired - Fee Related
Cited By (21)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN104154170A (en) * | 2014-08-01 | 2014-11-19 | 安徽工程大学 | Parallel mechanism based multidimensional vibration platform |
| CN104329407A (en) * | 2014-10-20 | 2015-02-04 | 中科院南京天文仪器有限公司 | Vibration reducing device for mobile type equipment |
| CN105587822A (en) * | 2014-10-22 | 2016-05-18 | 无锡利博科技有限公司 | Supporting and looseness preventing buffer structure of machine tool equipment |
| CN104763765A (en) * | 2015-04-10 | 2015-07-08 | 山东大学 | Novel high static and low dynamic rigidity piecewise linear vibration isolator and work method thereof |
| CN104763765B (en) * | 2015-04-10 | 2016-10-05 | 山东大学 | The piecewise linearity vibration isolator of a kind of high quiet low dynamic stiffness and method of work thereof |
| CN106763466B (en) * | 2015-11-21 | 2019-04-16 | 北京工业大学 | A kind of novel positive and negative Stiffness low frequency vibration isolation mechanism |
| CN106763466A (en) * | 2015-11-21 | 2017-05-31 | 北京工业大学 | A kind of novel positive and negative Stiffness low frequency vibration isolation mechanism |
| CN105546028A (en) * | 2016-02-02 | 2016-05-04 | 泰州市凯华柴油发电机组有限公司 | Diesel generator with variable spring support and vibration reducing control method of diesel generator |
| CN105546028B (en) * | 2016-02-02 | 2018-01-30 | 泰州市凯华柴油发电机组有限公司 | Diesel-driven generator and its vibration-reducing control method with variable spring support |
| CN105864339A (en) * | 2016-06-01 | 2016-08-17 | 福州大学 | Quasi-zero stiffness vibration isolator applicable to isolation of micro-amplitude and low-frequency vibration and realization method of quasi-zero stiffness vibration isolator |
| CN105864339B (en) * | 2016-06-01 | 2017-11-17 | 福州大学 | A kind of quasi-zero stiffness vibration isolators and its implementation for being applied to isolate low-frequency vibration a little |
| CN108533653A (en) * | 2018-04-26 | 2018-09-14 | 合肥工业大学 | It is a kind of that novel negative stiffness structure that stablizing negative stiffness value can be provided |
| CN108953448A (en) * | 2018-08-10 | 2018-12-07 | 浙江理工大学 | A kind of novel permanent magnetic formula bistable state vibration isolator |
| CN108953448B (en) * | 2018-08-10 | 2024-03-26 | 浙江理工大学 | Permanent magnet bistable vibration isolator |
| CN108953482A (en) * | 2018-09-20 | 2018-12-07 | 南京航空航天大学 | A kind of quasi- zero stiffness vibrating isolation system of centering type |
| CN108953482B (en) * | 2018-09-20 | 2023-09-22 | 南京航空航天大学 | Eccentric quasi-zero stiffness vibration isolation system |
| CN112696454A (en) * | 2020-12-28 | 2021-04-23 | 哈尔滨工程大学 | Magnetic suspension type quasi-zero stiffness electromagnetic vibration isolator with active negative stiffness |
| CN112963499A (en) * | 2021-02-22 | 2021-06-15 | 江苏大学 | Vibration isolator based on parallel connection of positive stiffness and negative stiffness of magnetic attraction member and control method of vibration isolator |
| CN112963499B (en) * | 2021-02-22 | 2022-07-22 | 江苏大学 | Vibration isolator based on parallel connection of positive stiffness and negative stiffness of magnetic attraction member and control method of vibration isolator |
| CN114658783A (en) * | 2022-03-22 | 2022-06-24 | 中国人民解放军海军工程大学 | Quasi-zero stiffness vibration isolator with adjustable positive and negative stiffness |
| CN114857194A (en) * | 2022-03-22 | 2022-08-05 | 中国人民解放军海军工程大学 | Electromagnetic negative stiffness device |
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