CN114875775A - Cylinder spring and tuned mass damping system - Google Patents
Cylinder spring and tuned mass damping system Download PDFInfo
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- CN114875775A CN114875775A CN202210640480.2A CN202210640480A CN114875775A CN 114875775 A CN114875775 A CN 114875775A CN 202210640480 A CN202210640480 A CN 202210640480A CN 114875775 A CN114875775 A CN 114875775A
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- cylinder spring
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- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01D—CONSTRUCTION OF BRIDGES, ELEVATED ROADWAYS OR VIADUCTS; ASSEMBLY OF BRIDGES
- E01D19/00—Structural or constructional details of bridges
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- E—FIXED CONSTRUCTIONS
- E04—BUILDING
- E04B—GENERAL BUILDING CONSTRUCTIONS; WALLS, e.g. PARTITIONS; ROOFS; FLOORS; CEILINGS; INSULATION OR OTHER PROTECTION OF BUILDINGS
- E04B1/00—Constructions in general; Structures which are not restricted either to walls, e.g. partitions, or floors or ceilings or roofs
- E04B1/62—Insulation or other protection; Elements or use of specified material therefor
- E04B1/92—Protection against other undesired influences or dangers
- E04B1/98—Protection against other undesired influences or dangers against vibrations or shocks; against mechanical destruction, e.g. by air-raids
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- E—FIXED CONSTRUCTIONS
- E04—BUILDING
- E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
- E04H9/00—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate
- E04H9/02—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate withstanding earthquake or sinking of ground
- E04H9/021—Bearing, supporting or connecting constructions specially adapted for such buildings
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- E—FIXED CONSTRUCTIONS
- E04—BUILDING
- E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
- E04H9/00—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate
- E04H9/02—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate withstanding earthquake or sinking of ground
- E04H9/021—Bearing, supporting or connecting constructions specially adapted for such buildings
- E04H9/0215—Bearing, supporting or connecting constructions specially adapted for such buildings involving active or passive dynamic mass damping systems
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- E—FIXED CONSTRUCTIONS
- E04—BUILDING
- E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
- E04H9/00—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate
- E04H9/02—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate withstanding earthquake or sinking of ground
- E04H9/021—Bearing, supporting or connecting constructions specially adapted for such buildings
- E04H9/0235—Anti-seismic devices with hydraulic or pneumatic damping
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01B—MEASURING LENGTH, THICKNESS OR SIMILAR LINEAR DIMENSIONS; MEASURING ANGLES; MEASURING AREAS; MEASURING IRREGULARITIES OF SURFACES OR CONTOURS
- G01B11/00—Measuring arrangements characterised by the use of optical techniques
- G01B11/02—Measuring arrangements characterised by the use of optical techniques for measuring length, width or thickness
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01B—MEASURING LENGTH, THICKNESS OR SIMILAR LINEAR DIMENSIONS; MEASURING ANGLES; MEASURING AREAS; MEASURING IRREGULARITIES OF SURFACES OR CONTOURS
- G01B7/00—Measuring arrangements characterised by the use of electric or magnetic techniques
- G01B7/02—Measuring arrangements characterised by the use of electric or magnetic techniques for measuring length, width or thickness
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L11/00—Measuring steady or quasi-steady pressure of a fluid or a fluent solid material by means not provided for in group G01L7/00 or G01L9/00
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- Engineering & Computer Science (AREA)
- Architecture (AREA)
- Environmental & Geological Engineering (AREA)
- Business, Economics & Management (AREA)
- Emergency Management (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The invention discloses a cylinder spring and a tuned mass damping system comprising the same. The air cylinder spring respectively collects the displacement and air pressure of the double-acting air cylinder through the displacement collector and the dynamic pressure sensor, the control unit sends a control instruction to the flow and pressure servo controller according to the collected air pressure and displacement, and the flow and pressure servo controller adjusts the opening degree to adjust the air pressure of the double-acting air cylinder, so that the elastic coefficient of the air cylinder spring is adjusted. The tuning mass damping system provided by the embodiment of the invention is provided with the cylinder spring, so that the vibration of the bridge can be more quickly suppressed.
Description
Technical Field
The invention relates to the technical field of bridge testing, in particular to a cylinder spring and a tuned mass damping system.
Background
With the rapid development of economy, large-span bridges are continuously appearing and increasing. Along with the increase of the bridge span, the rigidity and the damping of the bridge structure can be reduced, the vibration influence under the excitation of external conditions such as earthquake, wind or vehicles is larger and larger, the discomfort of traveling and pedestrians is caused to affect the use function of the bridge structure, and the fatigue damage and even the dynamic instability of the bridge structure are caused to be serious due to the overlarge response.
Currently, a commonly used means for suppressing bridge vibration is a tuned mass damping system. The existing tuned mass damping system can only achieve the effect of vibration suppression by adjusting frequency parameters, and cannot adjust the elastic coefficient of the system, so that the vibration of a bridge cannot be suppressed quickly.
Therefore, aiming at the problem of bridge vibration suppression in the prior art, the cylinder spring capable of adjusting the elastic coefficient in the vibration suppression process according to the bridge vibration condition and the tuned mass damping system with the cylinder spring are provided.
Disclosure of Invention
Aiming at the problem that a tuned mass damping system in the prior art cannot adjust a proper elastic coefficient according to the vibration condition of a bridge, the embodiment of the invention provides a cylinder spring capable of adjusting the elastic coefficient according to the vibration condition of the bridge and the tuned mass damping system with the cylinder spring.
In order to achieve the above object, an embodiment of the present invention provides the following technical solutions: a cylinder spring comprising: a double-acting cylinder for acting as a power source for the cylinder spring; the displacement collector is connected with the double-acting air cylinder and used for measuring the displacement of the double-acting air cylinder; the dynamic pressure sensor is connected with the double-acting air cylinder and used for measuring the air pressure in the double-acting air cylinder; the control unit is respectively connected with the displacement collector and the dynamic pressure sensor and is used for receiving the displacement data and the air pressure data; the flow and pressure servo controller is respectively connected with the control unit and the double-acting air cylinder; according to the instruction of the control unit, the flow and pressure servo controller adjusts the opening degree of the flow and pressure servo controller so as to change the elastic coefficient of the cylinder spring.
As a further improvement of the invention, the displacement collector comprises a grating ruler or a potentiometer.
As a further improvement of the invention, the grating ruler comprises a reading head connecting rod, the reading head connecting rod is connected with the double-acting air cylinder, and the reading head connecting rod and the double-acting air cylinder keep movement synchronism.
As a further improvement of the invention, the control unit prestores the simulation elastic coefficient of the cylinder spring.
As a further development of the invention, the command of the control unit is calculated according to the formula
Wherein P is the pressure of the double-acting cylinder, K is the simulated elastic coefficient of the pre-stored cylinder spring, S is the cross-sectional area of the double-acting cylinder, and Delta l is the displacement of the double-acting cylinder.
The embodiment of the invention also provides a tuned mass damping system. The tuned mass damping system comprises: the mass block can move up and down along the guide post; a vibration suppression driving mechanism selectively contacted with the mass block and used for suppressing the mass block from moving up and down along the guide post; the cylinder spring keeps synchronous motion with the vibration damping driving mechanism.
As a further improvement of the present invention, the vibration suppressing drive mechanism includes: a vibration suppressing support column for contacting the mass block and supporting the mass block; and the linear motor is connected with the vibration suppression support column and used for driving the vibration suppression support column to generate vertical displacement motion.
As a further improvement of the present invention, the vibration damping driving mechanism further includes an electromagnetic damping adjusting unit, the electromagnetic damping adjusting unit including: the three resistors are connected in parallel and respectively connected into three phases of the linear motor, and the resistance values of the three resistors are equal; the resistance sliding platform is electrically connected with the three resistors simultaneously; the three-phase resistance values of the three resistors connected into the linear motor are changed along with the movement position of the resistance value sliding platform
The invention has the following advantages:
the cylinder spring provided by the embodiment of the invention acquires the displacement and air pressure of the double-acting cylinder through the displacement acquisition device and the dynamic pressure sensor, the control unit sends a control instruction to the flow and pressure servo controller according to the acquired air pressure and displacement, and the flow and pressure servo controller adjusts the opening degree to adjust the air pressure of the double-acting cylinder, so that the elastic coefficient of the cylinder spring is adjusted. The tuned mass damping system provided by the embodiment of the invention is provided with the cylinder spring, and the elastic coefficient of the cylinder spring can be adjusted to quickly realize the optimal parameter matching of the tuned mass damping system, so that the vibration suppression of a bridge is performed more quickly.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments described in the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
FIG. 1 is a schematic structural view of a cylinder spring according to a first embodiment of the present invention;
FIG. 2 is a schematic diagram of a tuned mass damping system in an embodiment of the present invention;
FIG. 3 is a schematic structural diagram including a tuned mass damping system in an embodiment of the present invention;
fig. 4 is an electrical connection diagram of an electromagnetic damping adjustment unit and a linear motor according to an embodiment of the present invention;
fig. 5 is a schematic structural diagram of the electromagnetic damping adjustment unit in the embodiment of fig. 4.
Description of the reference symbols in the drawings:
100. cylinder spring 1, mass block
2(11), guide column 1-1(1-2), guide hole 5(8), vibration damping driving mechanism
51(81), vibration suppression support column 4(9), vibration excitation drive mechanism 41(91), vibration excitation support column
42(92), elastic energy storage driving part 52(82), linear motor 500 and electromagnetic damping adjusting unit
3(10), a limiting block 6, a displacement collector 7 and a double-acting cylinder
501. Contact piece 503, sliding table 505 and motor
12. Support platform 74, dynamic pressure sensor 76, control unit
75. Flow and pressure servo controller 62, reading head connecting rod
Detailed Description
In order to make those skilled in the art better understand the technical solution of the present invention, the technical solution in the embodiment of the present invention will be clearly and completely described below with reference to the drawings in the embodiment of the present invention, and it is obvious that the described embodiment is only a part of the embodiment of the present invention, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention. In the present invention, the vertical direction along the paper surface is defined as a vertical direction, and the horizontal direction along the paper surface is defined as a horizontal direction.
As shown in fig. 1, a schematic structural diagram of a cylinder spring according to a first embodiment of the present invention is shown. In this embodiment, cylinder spring 100 includes a double acting cylinder 7, a displacement pickup 6, a dynamic pressure sensor 74, a control unit 76, and a flow and pressure servo controller 75.
A double acting cylinder 7 serves as a power source for the cylinder spring 100. The double acting cylinder 7 can guide the piston to do linear reciprocating motion in the cylinder, and can move in the up and down directions, so that the double acting cylinder can follow the two moving directions of the tuned mass damping system.
The displacement collector 6 is connected with the double-acting cylinder 7 and is used for measuring the displacement of the double-acting cylinder 7. The displacement collector 6 comprises a grating ruler or a potentiometer. In the embodiment shown in fig. 1, the displacement collector 6 employs a grating scale with higher precision. In this embodiment, the grating scale includes a reading head connecting rod 62. The reading head connecting rod 62 is connected with the double-acting air cylinder 7, wherein the reading head connecting rod 62 and the double-acting air cylinder 7 keep the movement synchronism, so that the grating ruler can reflect the displacement of the air cylinder 7 in real time. Specifically, the reading head connecting rod 62 is connected to the piston rod of the cylinder 7 through a cross rod. The piston mandril displaces along with the change of air pressure in the air cylinder 7, the piston mandril drives the cross rod to synchronously move upwards or downwards, and the cross rod drives the reading head connecting rod 62 to synchronously move upwards or downwards.
A dynamic pressure sensor 74 is connected to the double acting cylinder 7. The dynamic pressure sensor 74 is used to measure the air pressure inside the double acting cylinder 7. The dynamic pressure sensor 74 may be a conventional pressure sensor, and the type and parameters are not specifically described herein. The control unit 76 is connected to the displacement collector 6 and the dynamic pressure sensor 74, respectively, and is configured to receive the displacement data of the double acting cylinder 7 collected by the displacement collector 6 and the air pressure data of the double acting cylinder 7 detected by the dynamic pressure sensor 74.
The flow and pressure servo controller 75 is connected to the control unit 76 and the double acting cylinder 7, respectively. The flow and pressure servo controller 75 adjusts its opening according to the command of the control unit 76 to change the pressure of the double acting cylinder 7 and thus the spring constant of the cylinder spring 100.
In this embodiment, the control unit 76 prestores a simulated spring constant of the cylinder spring 100. The command of the control unit 76 is determined according to the calculation of formula 1
Wherein P is the pressure of the double-acting cylinder, K is the simulated elastic coefficient of the pre-stored cylinder spring, S is the cross-sectional area of the double-acting cylinder, and Delta l is the displacement of the double-acting cylinder.
The specific derivation process of equation 1 is as follows:
assuming that the gas inlet of the double-acting cylinder 7 is closed, the air pressure detected by the dynamic pressure sensor is P, and at this time, the displacement and the displacement change value of the double-acting cylinder 7 measured by the grating ruler are l and delta l respectively. If the cross-sectional area of the piston of the double-acting cylinder 7 is S, the required simulated elastic coefficient of the pneumatic spring is K, and the thrust of the cylinder is F.
Using the ideal gas equation, one can know:
where V-l.S is the volume of the double acting cylinder 7, where nRT is a constant.
The thrust formula for the double acting cylinder 7 is then:
can finally obtain
It can be seen that the desired simulated spring constant K is related to the displacement l of the double acting cylinder 7 and the displacement variation Δ l, and thus the spring constant required for the pressure to reach the cylinder spring 100 can be dynamically changed.
The cylinder spring provided by the embodiment of the invention acquires the displacement and air pressure of the double-acting cylinder through the displacement acquisition device and the dynamic pressure sensor, the control unit sends a control instruction to the flow and pressure servo controller according to the acquired air pressure and displacement, and the flow and pressure servo controller adjusts the opening degree to adjust the air pressure of the double-acting cylinder, so that the elastic coefficient of the cylinder spring is adjusted.
As shown in fig. 3, embodiments of the present invention also provide a tuned mass damping system. The tuned mass damping system comprises a mass 1, a vibration damping drive 5 and a cylinder spring 100. As shown in fig. 2, a schematic diagram of the tuned mass damping system of the embodiment shown in fig. 3 is shown. The mass block 1 is connected with a spring and a damper, and the amplitude of the exciting force of the spring and the frequency of the damper can be self-adaptively adjusted according to the current vibration of the mass block 1, so that the mass block 1 is quickly damped. In the embodiment of fig. 3, the cylinder spring 100 corresponds to the spring of fig. 2, and the vibration suppressing drive mechanism 5 corresponds to the damper of fig. 2; the mass 1, the cylinder spring 100 and the vibration damping drive 5 form a tuned mass damper. Wherein the cylinder spring 100 and the vibration damping driving mechanism 5 keep synchronous movement.
The mass 1 can move up and down along the guide posts 2. In this embodiment, the guide post 2 is vertically disposed. The mass block 1 is provided with a guide hole 1-1, and the mass block 1 is sleeved on the guide post 2 through the guide hole 1-1. The inner diameter of the guide hole 1-1 is slightly larger than the outer diameter of the guide post 2, so that the mass block 1 and the guide post 2 do not generate any interference in the process of moving along the guide post 2. Preferably, the guide post 2 is further fixedly provided with a limiting block 3. The limiting block 3 is used for limiting the movement lower limit position of the mass block 1 and can also support the mass block 1.
The vibration damping driving mechanism 5 is selectively contacted with the mass block 1 and is used for damping the mass block 1 from moving up and down along the guide post 2. The vibration damping drive mechanism 5 includes a vibration damping support column 51 and a linear motor 52. The vibration suppressing support columns 51 are used to contact the mass block 1 and support the mass block 1. The linear motor 52 is connected to the vibration suppressing support column 51, and is used for driving the vibration suppressing support column 51 to generate a vertical displacement motion. The linear motor 2 drives the vibration suppressing support column 51 to move upward to contact and support the mass 1, so that the mass 1 stops vibrating. The mass 1 can rapidly achieve the stop vibration state by the adjustment of the cylinder spring 100.
The tuning mass damping system provided by the embodiment of the invention is provided with the cylinder spring 100, and the elastic coefficient of the cylinder spring 100 can be adjusted, so that the bridge vibration suppression can be carried out more quickly.
As shown in fig. 4, in the preferred embodiment, the vibration damping driving mechanism 5 further includes an electromagnetic damping adjusting unit 500. The electromagnetic damping adjustment unit 500 includes three resistors and a slip resistant platform. The three resistors are respectively R1, R2 and R3, and R1, R2 and R3 are connected in parallel with each other and respectively connected to the three-phase resistors of the linear motor 52. Preferably, the three resistors R1, R2 and R3 are connected in a heart-shaped connection to the three phases of the linear motor 52. Wherein the resistances of R1, R2 and R3 are equal. The resistance sliding platform is simultaneously and electrically connected with three resistors R1, R2 and R3; the resistance values of the three phases of the three resistors R1, R2 and R3 connected to the linear motor 52 are changed along with the movement position of the resistance sliding platform. The electromagnetic damping adjustment unit 500 can effectively adjust the drive input signal of the vibration damping drive mechanism 5, thereby stably controlling the vibration damping motion of the vibration damping drive mechanism 5.
As shown in fig. 5, the resistance value sliding platform includes a contact piece 501, a sliding table 503, and a motor 505. The contact plate 501 electrically contacts the three resistors R1, R2 and R3 in synchronization and in parallel, respectively, and one end of the contact plate 501 is fixedly connected to the slide table 503. The motor 505 drives the sliding table 503 to move horizontally, so as to drive the contact piece 501 to move horizontally, and accordingly, the resistance values of three phases of the three resistors R1, R2 and R3 connected to the linear motor 52 are changed.
As shown in fig. 1, in this embodiment, the vibration excitation driving mechanism 4 is further included, and the vibration excitation driving mechanism 4 includes a vibration excitation support column 41 and an elastic energy storage driving portion 42. The excitation driving mechanism 4 is used for generating the vibration of the mass block 1 with a preset frequency. After the excitation driving mechanism 4 is started for a period of time, if the mass block 1 is not needed to vibrate any more, a worker can start the vibration suppression driving mechanism 5 to suppress vibration.
In the embodiment of fig. 1, there are two guiding pillars, which are the guiding pillar 2 and the guiding pillar 11, respectively, and since the characteristics of the guiding pillar 11 are the same as those of the guiding pillar 2, only the guiding pillar 2 is used as a detailed embodiment for description herein, and the guiding pillar 11, the guiding hole 1-2, and the limiting block 10 are not described again. The vibration excitation driving mechanism 4 and the vibration excitation driving mechanism 9 are two, and the characteristics of the vibration excitation driving mechanism 4 are the same as those of the vibration excitation driving mechanism 9, so that the vibration excitation driving mechanism 4 is only described as a detailed embodiment herein, and the vibration excitation driving mechanism 9, the vibration excitation support column 91 and the elastic energy storage driving portion 92 are not described again. The vibration suppression driving mechanism 5 and the vibration suppression driving mechanism 8 are two, and the characteristics of the vibration suppression driving mechanism 5 are the same as those of the vibration suppression driving mechanism 8, so that only the vibration suppression driving mechanism 5 is described as a detailed embodiment herein, and the vibration suppression driving mechanism 8, the vibration suppression supporting column 81, and the linear motor 82 are not described again.
It will be evident to those skilled in the art that the invention is not limited to the details of the foregoing illustrative embodiments, and that the present invention may be embodied in other specific forms without departing from the spirit or essential attributes thereof. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein. Any reference sign in a claim should not be construed as limiting the claim concerned.
Furthermore, it should be understood that although the present description refers to embodiments, not every embodiment may contain only a single embodiment, and such description is for clarity only, and those skilled in the art should integrate the description, and the embodiments may be combined as appropriate to form other embodiments understood by those skilled in the art.
Claims (8)
1. A cylinder spring, comprising:
a double-acting cylinder for acting as a power source for the cylinder spring;
the displacement collector is connected with the double-acting air cylinder and is used for measuring the displacement of the double-acting air cylinder;
the dynamic pressure sensor is connected with the double-acting air cylinder and used for measuring the air pressure in the double-acting air cylinder;
the control unit is respectively connected with the displacement collector and the dynamic pressure sensor and is used for receiving the displacement data and the air pressure data;
the flow and pressure servo controller is respectively connected with the control unit and the double-acting air cylinder; according to the instruction of the control unit, the flow and pressure servo controller adjusts the opening degree of the flow and pressure servo controller so as to change the elastic coefficient of the cylinder spring.
2. The cylinder spring according to claim 1, wherein the displacement collector comprises a grating ruler or a potentiometer.
3. The cylinder spring according to claim 2, wherein the grating scale comprises a reading head connecting rod, the reading head connecting rod is connected with the double-acting cylinder, and the reading head connecting rod and the double-acting cylinder keep synchronous movement.
4. A cylinder spring according to claim 1, characterized in that said control unit prestores a simulated spring constant of said cylinder spring.
5. Cylinder spring according to claim 4, characterised in that the command of the control unit is calculated according to the formula
Wherein P is the pressure of the double-acting cylinder, K is the simulated elastic coefficient of the pre-stored cylinder spring, S is the cross-sectional area of the double-acting cylinder, and Delta l is the displacement of the double-acting cylinder.
6. A tuned mass damping system, the system comprising:
the mass block can move up and down along the guide post;
the vibration suppression driving mechanism is selectively contacted with the mass block and is used for suppressing the mass block from moving up and down along the guide post;
a cylinder spring according to any one of claims 1 to 5, which is held in synchronous motion with the vibration damping drive mechanism.
7. The tuned mass damping system according to claim 6, wherein said vibration canceling drive mechanism comprises: the vibration suppression support column is used for contacting with the mass block and supporting the mass block; and the linear motor is connected with the vibration suppression supporting column and used for driving the vibration suppression supporting column to generate vertical displacement motion.
8. The tuned mass damping system according to claim 7, wherein said vibration damping drive mechanism further comprises an electromagnetic damping adjustment unit, said electromagnetic damping adjustment unit comprising: the three resistors are connected in parallel and respectively connected into three phases of the linear motor, and the resistance values of the three resistors are equal; the resistance sliding platform is electrically connected with the three resistors simultaneously; the three-phase resistance values of the three resistors connected to the linear motor are changed along with the movement position of the resistance value sliding platform.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210640480.2A CN114875775A (en) | 2022-06-07 | 2022-06-07 | Cylinder spring and tuned mass damping system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210640480.2A CN114875775A (en) | 2022-06-07 | 2022-06-07 | Cylinder spring and tuned mass damping system |
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| CN114875775A true CN114875775A (en) | 2022-08-09 |
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| US20090294234A1 (en) * | 2008-05-30 | 2009-12-03 | Design, Imaging & Control, Inc. | Adjustable vibration isolation and tuned mass damper systems |
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| CN103225668A (en) * | 2013-04-02 | 2013-07-31 | 江苏大学 | Load-sensing variable-damping electromagnetic shock absorption system |
| CN203653017U (en) * | 2013-12-25 | 2014-06-18 | 北京升华电梯有限公司 | Balanced oil supply resistor for straight elevator with laterally arranged hydraulic oil cylinders |
| CN106704439A (en) * | 2016-11-21 | 2017-05-24 | 大连理工大学 | Tuned mass damper based on symmetrical combination-type air springs |
| CN111396499A (en) * | 2020-03-24 | 2020-07-10 | 上海材料研究所 | Three-dimensional vibration isolation table with active control |
| CN112878528A (en) * | 2021-02-26 | 2021-06-01 | 同济大学 | Self-adaptive variable-stiffness gas spring tuned mass damper |
| CN113638515A (en) * | 2021-08-25 | 2021-11-12 | 湖南大学 | Variable-rigidity variable-mass variable-damping tuned mass damper and design method thereof |
| CN113883204A (en) * | 2021-10-22 | 2022-01-04 | 山东交通学院 | Piston type air spring damping system with variable rigidity |
-
2022
- 2022-06-07 CN CN202210640480.2A patent/CN114875775A/en active Pending
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20090294234A1 (en) * | 2008-05-30 | 2009-12-03 | Design, Imaging & Control, Inc. | Adjustable vibration isolation and tuned mass damper systems |
| CN102537196A (en) * | 2010-12-24 | 2012-07-04 | 上海微电子装备有限公司 | Active vibration damping system as well as vibration damping unit and absolute displacement measuring device thereof |
| CN103225668A (en) * | 2013-04-02 | 2013-07-31 | 江苏大学 | Load-sensing variable-damping electromagnetic shock absorption system |
| CN203653017U (en) * | 2013-12-25 | 2014-06-18 | 北京升华电梯有限公司 | Balanced oil supply resistor for straight elevator with laterally arranged hydraulic oil cylinders |
| CN106704439A (en) * | 2016-11-21 | 2017-05-24 | 大连理工大学 | Tuned mass damper based on symmetrical combination-type air springs |
| CN111396499A (en) * | 2020-03-24 | 2020-07-10 | 上海材料研究所 | Three-dimensional vibration isolation table with active control |
| CN112878528A (en) * | 2021-02-26 | 2021-06-01 | 同济大学 | Self-adaptive variable-stiffness gas spring tuned mass damper |
| CN113638515A (en) * | 2021-08-25 | 2021-11-12 | 湖南大学 | Variable-rigidity variable-mass variable-damping tuned mass damper and design method thereof |
| CN113883204A (en) * | 2021-10-22 | 2022-01-04 | 山东交通学院 | Piston type air spring damping system with variable rigidity |
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