CN113447187B - Shield tunnel segment vibration and impact pre-estimation control method and control system - Google Patents
Shield tunnel segment vibration and impact pre-estimation control method and control system Download PDFInfo
- Publication number
- CN113447187B CN113447187B CN202110733614.0A CN202110733614A CN113447187B CN 113447187 B CN113447187 B CN 113447187B CN 202110733614 A CN202110733614 A CN 202110733614A CN 113447187 B CN113447187 B CN 113447187B
- Authority
- CN
- China
- Prior art keywords
- impact
- damping
- load
- axial
- duct piece
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Classifications
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L5/00—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes
- G01L5/16—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes for measuring several components of force
- G01L5/165—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes for measuring several components of force using variations in capacitance
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/002—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion characterised by the control method or circuitry
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/03—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using magnetic or electromagnetic means
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01P—MEASURING LINEAR OR ANGULAR SPEED, ACCELERATION, DECELERATION, OR SHOCK; INDICATING PRESENCE, ABSENCE, OR DIRECTION, OF MOVEMENT
- G01P15/00—Measuring acceleration; Measuring deceleration; Measuring shock, i.e. sudden change of acceleration
- G01P15/16—Measuring acceleration; Measuring deceleration; Measuring shock, i.e. sudden change of acceleration by evaluating the time-derivative of a measured speed signal
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01S—RADIO DIRECTION-FINDING; RADIO NAVIGATION; DETERMINING DISTANCE OR VELOCITY BY USE OF RADIO WAVES; LOCATING OR PRESENCE-DETECTING BY USE OF THE REFLECTION OR RERADIATION OF RADIO WAVES; ANALOGOUS ARRANGEMENTS USING OTHER WAVES
- G01S13/00—Systems using the reflection or reradiation of radio waves, e.g. radar systems; Analogous systems using reflection or reradiation of waves whose nature or wavelength is irrelevant or unspecified
- G01S13/02—Systems using reflection of radio waves, e.g. primary radar systems; Analogous systems
- G01S13/06—Systems determining position data of a target
- G01S13/08—Systems for measuring distance only
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2224/00—Materials; Material properties
- F16F2224/04—Fluids
- F16F2224/045—Fluids magnetorheological
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- General Engineering & Computer Science (AREA)
- General Physics & Mathematics (AREA)
- Radar, Positioning & Navigation (AREA)
- Remote Sensing (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Electromagnetism (AREA)
- Computer Networks & Wireless Communication (AREA)
- Force Measurement Appropriate To Specific Purposes (AREA)
Abstract
The invention provides a shield tunnel segment vibration and impact prediction control method and a vibration and impact reduction device, wherein the method comprises the following steps: s1, detecting the characteristic quantity of the load of a duct piece, judging the type of the load, comparing the type of the load with a preset safety characteristic quantity, and starting a magnetic control damping device if the characteristic quantity of the load is larger than the preset safety characteristic quantity; s2, estimating load characteristic parameters borne by the duct piece; and S3, according to the segment load characteristic quantity and the load characteristic parameters, predicting a damping adjustment required direction and presetting an excitation coil initial current of the magnetic control damping device, so that the vibration and impact resistant device generates an expected ideal damping force in the vibration or impact load generation process, and the magnetic control damping system can predict and control the vibration or impact load characteristic at the same time.
Description
Technical Field
The invention relates to the technical field of structural health and safety of shield tunnel segments in the urban subway operation period, in particular to a shield tunnel segment vibration and impact prediction control method and a shield tunnel segment vibration and impact prediction control system.
Background
With the rapid development of economy in China, the construction of urban subways is increased explosively, and the urban subways bring great challenges to the safety of an operation period while shortening the communication distance between people, greatly relieving urban traffic pressure and bringing great convenience to the operation.
The shield construction method has the characteristics of rapidness, safety and environmental protection, and is widely applied to subway tunnel construction. However, the huge disturbance of the soil body in the shield construction method changes the stress field around the tunnel, and in addition, factors such as vibration and impact caused by the running of vehicles in the operation period make the tunnel structure health monitoring and stability control become a complex and difficult-to-control system engineering. The traditional method for reflecting the stability control mode of the tunnel structure health monitoring mode and the tunnel mechanism by the change of parameters such as segment displacement, deformation and stress change is carried out separately, the method is difficult to adapt to the actual condition that the shield tunnel in the operation period is subjected to long-term alternating load, and the real-time performance and the accuracy of control are difficult to guarantee.
Disclosure of Invention
In order to solve the technical problems, the invention provides a shield tunnel segment vibration and impact prediction control method and a control system, which solve the technical problems that a magnetic control damping system can predict and control the vibration or impact load characteristics at the same time and realize the stability control of the shield tunnel segments of the urban subway under the complex load condition.
According to the technical problem, the technical scheme is as follows:
a shield tunnel segment vibration and impact pre-estimation control method is characterized by comprising the following steps of:
s1, detecting the characteristic quantity of the load of a duct piece, comparing the load type with a preset safety characteristic quantity, and starting a magnetic control damping device when the characteristic quantity of the load is greater than the preset safety characteristic quantity;
s2, estimating load characteristic parameters borne by the duct piece;
and S3, predicting a damping adjustment required position and presetting an initial current of a magnet exciting coil of the magnetic control damping device through the segment load characteristic quantity and the load characteristic parameter, so that the magnetic control damping device generates a corresponding damping force in the vibration or impact load generation process.
Further, the step S1 includes the steps of:
s11, respectively detecting the tension force applied to the segment bolt and the distance between a collision impact object and the segment through a pressure sensor;
s12, calculating the occurrence time of the impact load on the duct piece and the stress variation of the duct piece according to the measurement result of the step S11;
s13, respectively comparing the time of impact load with preset safe time, and comparing the stress variation of the duct piece with preset safe variation, wherein the preset safe time is the sum of the response lag time of the damping device and the detection period of the relative distance between the impact object and the duct piece, and the safe variation is set according to the measurement result of the shield duct piece connection comprehensive stress experiment;
s14, when the time of the impact load is more than or equal to the preset safety time or the stress variation of the duct piece is less than the preset safety variation, returning to the step S11; and when the time of the impact load is less than the preset safe time or the stress variation of the duct piece is more than or equal to the preset safe variation, starting the magnetic control damping device.
Further, the step S12 includes the steps of:
s121, when the stress of the duct piece changes, the connecting bolt acts on the damping regulators which are distributed in the circumferential direction, and the sensing units distributed on the damping regulators are extruded in different degrees, namely, the first pressure sensing unit, the second pressure sensing unit, the third pressure sensing unit, the fourth pressure sensing unit, the fifth pressure sensing unit, the sixth pressure sensing unit, the seventh pressure sensing unit and the eighth pressure sensing unit can deform, so that the capacitance change value of each sensing unit can be obtained.
S122, when the duct piece is impacted by external load, calculating the impact time of the duct piece through the distances of impact objects detected by the first radar sensor, the second radar sensor, the third radar sensor and the fourth radar sensor which are uniformly distributed on the duct piece.
Further, the step S121 includes the steps of:
s1211, calculating corresponding stress change according to the capacitance change value of the detection sensing unit, and acquiring the axial tension of the single damper according to the following formula:
F nz ＝F n1 +F n2 +…+F n8 (1)
in the formula (1), F nz Is a singleA damper axial force; f n1 Is the axial acting force of the first pressure sensing unit; f n2 Is the axial acting force of the second pressure sensing unit; f n3 Is the axial acting force of the third pressure sensing unit; f n4 Is the axial acting force of the fourth pressure sensing unit; f n5 Is the axial acting force of the fifth pressure sensing unit; f n6 Is the axial acting force of the sixth pressure sensing unit; f n7 Is the axial acting force of the seventh pressure sensing unit; f n8 Is the axial acting force of the eighth pressure sensing unit;
s1212, calculating the variation of the axial tension of the single damper in a detection period delta t according to the calculated axial tension of the single damper and 4 large directions of all dampers installed on the duct piece, wherein the 4 large directions of each damper installed on the duct piece are respectively an annular left side, an annular right side, an axial front end and an axial rear end; the circular left sides are respectively a first circular left side and a second circular left side; the circular right sides are respectively a first circular right side and a second circular right side; the axial front ends are respectively a first axial front end, a second axial front end and a third axial front end; the axial rear ends are respectively a first axial rear end, a second axial rear end and a third axial rear end, and the axial tension variation of a single damper in the detection period delta t is calculated; .
S1213, the process goes to step S13 according to the single damper axial tension variation amount to determine.
Further, the step S122 includes the steps of:
s1221, when the duct piece is impacted by an external load, obtaining the relative speed through the change of the distance between an impact load and the duct piece in a detection period delta t of a first radar sensor, a second radar sensor, a third radar sensor and a fourth radar sensor which are uniformly distributed in four directions of the duct piece;
s1222, calculating the acceleration of the impact load in the detection period delta t according to the speed obtained in the step S1221;
after S1223, the velocity and acceleration obtained in steps S1221 and S1222, and the distance obtained in step S11, the time to collision between the impact load and the segment and the initial velocity at the time of collision are calculated according to newton' S second law.
Further, in step S11, relative changes Δ S11F, Δ S11B, Δ S11L, and Δ S11R of the relative distances measured by the respective radar sensors within Δ t are calculated, and the magnitudes are compared;
when max { Δ S11B, Δ S11R } is less than or equal to min { Δ S11F, Δ S11L }, the impact acting force area is in the area I;
when max { Δ S11F, Δ S11R } is less than or equal to min { Δ S11B, Δ S11L }, the impact acting force area is in the area II;
when max { Δ S11F, Δ S11L }. Is less than or equal to min { Δ S11B, Δ S11R }, the impact acting force area is in a zone III;
when max (delta S11B, delta S11L) is less than or equal to min (delta S11F, delta S11R), the impact acting force area is in an IV area;
the area I, the area II, the area III and the area IV divide the inner wall of the pipe piece into four areas which are opposite in pairs;
wherein, the region I is positioned between the first axial front end and the second axial front end; the second zone is located between the first axial rear end and the second axial rear end; zone III is located between the second rearward end and the third rearward end; the IV area is positioned between the second axial front end and the third axial front end.
Further, the step S3 includes the steps of:
s31, according to the distance change values delta S11F, delta S11B, delta S11L and delta S11R measured in the step S11 and the axial tension change value measured in the step S121, when the distance change value is larger than a preset safety value, judging that impact external load occurs; when the axial tension variation value is larger than a preset safety value, judging that vibration occurs;
and S32, estimating the damping adjustment required position and presetting the initial current of the magnet exciting coil of the magnetic control damping device according to the judgment result of the step S31.
Further, the step S32 includes the steps of:
s321, when an impact external load occurs, determining a damping adjustment demand direction according to the impact force acting area in the step S11, and predicting a damping adjustment sequence;
meanwhile, according to the load characteristic parameters estimated in the step S2, an impact dynamics model and a required magnetic control damping device ideal damping force model are constructed;
wherein the ideal damping force model is obtained by the following formula:
in the formula (2), F Need to For desired damping force, v First stage The initial velocity at which the impact occurs, L MR Is the compression stroke m of a disc spring in a magnetic control damping device 0 Mass as impact load;
presetting initial current of a damping regulator in the magnetic control damping device through an impact dynamics model and an ideal damping force model;
s322, when a vibration load occurs, determining a damping adjustment demand direction according to the impact force acting area in the step S11, and predicting a damping adjustment sequence; and (5) constructing an impact dynamics model and a required magnetic control damping device ideal damping force model through the load characteristic parameters estimated in the step (S2).
By adopting the method, the magnetic control damping system can be used for estimating and controlling the vibration or impact load characteristics at the same time, and the stability control of the shield tunnel segment of the urban subway under the complex load condition is realized.
The invention provides a shield tunnel segment vibration and impact pre-estimation control system, which comprises a detection system and a magnetic control damping device, wherein the detection system comprises a magnetic control damping device; the detection system comprises a sensing unit and a signal conditioning module and is used for detecting the stress variation of the duct piece; the magnetic control damping device comprises a program control power supply and damping regulators, the damping regulators are respectively a first damping regulator, a second damping regulator, a third damping regulator and a fourth damping regulator, and the damping regulators are connected with the controller through the program control power supply;
the damping regulator changes the magnetic control cement and the magnetorheological elastomer in the damping regulator to generate damping force by changing applied current, and after the magnetorheological cement is injected into the oil storage cylinder of the impact damper, the magnetic field of the coil changes the flow characteristic of the magnetorheological cement, so that the motion of the piston of the impact damper can be controlled to be blocked, and impact buffering is realized; the magnetorheological elastomer is arranged in series connection to resist impact to form the vibration isolator, and is changed by the damping force of the magnetic field of the coil, so that the vibration is controllably isolated.
Further, the controller comprises a load judgment unit, a parameter estimation unit and a current control unit; the load judging unit is used for judging and judging the variation of the stress of the duct piece, the preset safe variation and the variation among the load types, the input end of the load judging unit is connected with the output end of the signal conditioning module, and the output end of the load judging unit is connected with the input end of the parameter estimating unit; the parameter pre-estimating unit is used for pre-estimating the load grade, the damping adjusting direction, the damping force and the initial current of the damping adjuster; the current control unit is used for controlling the programmable power supply to change output current to the damping regulator, the input end of the current control unit is connected with the output end of the parameter estimation unit, and the output end of the current control unit is connected with the input end of the programmable power supply;
the signal conditioning module comprises a signal amplifier, a filter and an A/D converter, wherein the input end of the amplifier is connected with the output end of the pressure sensor, the output end of the amplifier is connected with the input end of the filter, the output end of the filter is connected with the input end of the A/D converter, and the output end of the A/D converter is connected with the input end of the controller.
Compared with the prior art, the invention has the beneficial effects that:
by adopting the shield tunnel segment vibration and impact estimation control method in the technical scheme, the change of parameters such as segment displacement, deformation and stress change reflects the fact that a tunnel structure health monitoring mode and a tunnel mechanism stability control mode can be carried out together, the actual condition that a shield tunnel in an operation period is subjected to long-term alternating load is effectively suitable, and the real-time performance and the accuracy of control are guaranteed; the method is operated by the shield tunnel segment vibration and impact estimation control system provided by the invention.
Drawings
FIG. 1 is a schematic structural diagram of a shield tunnel segment vibration and impact prediction control system provided by the present invention;
FIG. 2 is a schematic structural diagram of a magnetic damping device in an embodiment;
FIG. 3 is a schematic view of the cover plate on one side of the segment connection collar of FIG. 2 with the segment connection collar removed;
fig. 4 is a schematic diagram of the internal structure of the magnetic control damping device.
Detailed Description
The present invention will be further described with reference to the following examples and the accompanying drawings.
Referring to fig. 1, the detecting system of the present invention includes a sensing unit and a signal conditioning module 14, and is configured to detect a variation of a force applied to a segment 1;
the magnetic control damping device comprises a program control power supply 12 and four damping regulators, namely a first damping regulator 3, a second damping regulator 5, a third damping regulator 7 and a fourth damping regulator 10, wherein each damping regulator is connected with a controller 13 through the program control power supply 12; each damping regulator changes the magnetic control cement and the magnetorheological elastomer in the damping regulator to generate damping force by changing the applied current, and after the magnetorheological cement is injected into the oil storage cylinder of the impact damper, the magnetic field of the coil changes the flow characteristic of the magnetorheological cement, so that the movement of the piston of the impact damper is controlled to be blocked, and impact buffering is realized; the magnetorheological elastomer is arranged in series connection to resist impact to form the vibration isolator, and is also changed by the damping characteristic of the magnetic field of the coil, so that vibration controllable isolation is realized.
The controller 13 includes: the device comprises a load judgment unit, a parameter estimation unit and a current control unit. The load judging unit is used for judging whether the stress variation of the duct piece 1 is larger than the preset safety variation and the load type, and can be vibration, impact or mixed, the input end of the load judging unit is connected with the output end of the signal conditioning module 14, and the output end of the load judging unit is connected with the input end of the parameter estimating unit; the parameter pre-estimating unit is used for pre-estimating the load grade, the damping adjusting direction, the ideal damping force and the initial current of the damping adjuster; the current control unit is used for controlling the programmable power supply 12 to change output current to the damping regulator, the input end of the current control unit is connected with the output end of the parameter estimation unit, and the output end of the current control unit is connected with the input end of the programmable power supply 12.
Wherein, the sensing element is section of jurisdiction 1 load type and judges that detect the decision unit, and vibration load detects and judges that can be pressure sensor or vibration sensor, and the impact load detects and judges that can be radar or distance sensor etc.. In the embodiment, a pressure-capacitance type magnetorheological elastomer pressure sensor is adopted to detect and judge the vibration load, a radar sensor is adopted to detect and judge the impact load, and the number of the two is at least 4; the pressure sensors are uniformly arranged between the positive pressure wall surface of the spoke of the damping regulator and the vibration isolation magnetorheological elastomer, preferably, the number of the pressure sensors is 8, the comprehensive acting force borne by the bolts is mainly measured, the force acted on the segment 1 by the damper on the axial component is measured, most of the comprehensive acting force borne by the bolts is finally expressed as axial tension, and the capacitance value is measured by adopting the existing capacitance detection equipment unit, such as a capacitance and inductance measuring instrument, and the like, and can be directly purchased; the radar sensors are uniformly arranged on the surfaces of the inner circular rings in the four connecting directions of the duct piece 1, preferably, the number of the adopted radar sensors is 4, and the first radar sensor 11F, the second radar sensor 11B, the third radar sensor 11R and the fourth radar sensor 11L are respectively arranged.
Vibration isolation and shock absorption can be realized simultaneously to the damping adjustment ware, quantity sets up 4 at least, preferably, set up 4, be first damping adjustment ware 3 respectively, second damping adjustment ware 5, third damping adjustment ware 7, fourth damping adjustment ware 10, and evenly distributed is in four connection end directions of section of jurisdiction 1, preferably, the quantity of adoption is 10, each equipartition is three in six directions on the front end connection face 9 of section of jurisdiction 1 and the rear end connection face, six directions are first axial forward end 10F1 respectively, second axial forward end 10F2, third axial forward end 10F3, first axial rear end 5B1, second axial rear end 5B2 and third axial rear end 5B3, section of jurisdiction 1 left end connection face 4, each equipartition is 2 in eight directions on the right-hand member connection face, eight directions are first hoop left side 3L1 respectively, second hoop left side 3L2, first hoop right side 7R1, second hoop right side 7R2, the damping adjustment ware compresses tightly at section of jurisdiction 1 inboard surface through central through the through-hole bolt.
The signal conditioning module 14 includes a signal amplifier, a filter and an a/D converter, an input end of the amplifier is connected to an output end of the pressure sensor, an output end of the amplifier is connected to an input end of the filter, an output end of the filter is connected to an input end of the a/D converter, and an output end of the a/D converter is connected to an input end of the controller 13. The sensor unit converts the acquired bolt stress change signal into a digital signal, and then transmits the digital signal to the controller 13, and the signal conditioning module 14 can improve the accuracy of the acquired bolt stress change signal of the sensor unit and effectively remove noise interference.
Referring to fig. 1 and 4, a method for predicting and controlling vibration and impact of a shield tunnel segment includes the following steps:
s1, detecting the load characteristic quantity of a duct piece 1, comparing the load type with a preset safety characteristic quantity, and starting a magnetic control damping device when the load characteristic quantity is larger than the preset safety characteristic quantity;
s2, estimating load characteristic parameters borne by the duct piece 1;
and S3, predicting the damping adjustment required position and presetting the initial current of a magnet exciting coil of the magnetic control damping device through the load characteristic quantity and the load characteristic parameter of the duct piece 1, so that the magnetic control damping device generates corresponding damping force in the vibration or impact load generation process.
Wherein, the step S1 is divided into the following steps:
s11, respectively detecting the tensile force applied to the bolts of the duct piece 1 and the distance between an impact object and the duct piece through a pressure sensor;
s12, calculating the occurrence time of the impact load on the duct piece and the stress variation of the duct piece according to the measurement result of the step S11;
s13, respectively comparing the time of impact load with preset safe time, and comparing the stress variation of the duct piece with preset safe variation, wherein the preset safe time is the sum of the response lag time of the damping device and the detection period of the relative distance between the impact object and the duct piece, and the safe variation is set according to the measurement result of the shield duct piece connection comprehensive stress experiment;
s14, when the time of the impact load is more than or equal to the preset safety time or the stress variation of the duct piece is less than the preset safety variation, returning to the step S11; and when the time of the impact load is less than the preset safe time or the stress variation of the duct piece is more than or equal to the preset safe variation, starting the magnetic control damping device.
Wherein, the step S12 is divided into the following steps:
s121, when the stress of the duct piece changes, the connecting bolts apply force to the damping regulators distributed in the circumferential direction, so that the sensing units distributed on the damping regulators are extruded in different degrees, namely the first pressure sensing unit n1, the second pressure sensing unit n2, the third pressure sensing unit n3, the fourth pressure sensing unit n4, the fifth pressure sensing unit n5, the sixth pressure sensing unit n6, the seventh pressure sensing unit n7 and the eighth pressure sensing unit n8 deform, and the capacitance change value of each sensing unit can be obtained.
And S122, when the duct piece is impacted by external load, calculating the time of impact of the duct piece through the distances of impact objects detected by the first radar sensor 11F, the second radar sensor 11B, the third radar sensor 11L and the fourth radar sensor 11R which are uniformly distributed on the duct piece.
Wherein, the step S121 is further divided into the following steps:
s1211, calculating corresponding stress change according to the capacitance change value of the detection sensing unit, and acquiring the axial tension of the single damper according to the following formula:
F nz ＝F n1 +F n2 +…+F n8 (1)
in the formula (1), F nz Is a single damper axial force; f n1 Is the axial acting force of the first pressure sensing unit; f n2 Is the axial acting force of the second pressure sensing unit; f n3 Is the axial acting force of the third pressure sensing unit; f n4 Is the axial acting force of the fourth pressure sensing unit; f n5 Is the axial acting force of the fifth pressure sensing unit; f n6 Is axial direction of the sixth pressure sensing unitActing force; f n7 Is the axial acting force of the seventh pressure sensing unit; f n8 Is the axial acting force of the eighth pressure sensing unit;
s1212, calculating the variation of the axial tension of the single damper in a detection period delta t according to the calculated axial tension of the single damper and 4 large directions of all dampers installed on the duct piece, wherein the 4 large directions of all dampers installed on the duct piece are respectively an annular left side, an annular right side, an axial front end and an axial rear end; the circular left sides are respectively a first circular left side 3L1 and a second circular left side 3L2; the annular right sides are respectively a first annular right side 7R1 and a second annular right side 7R2; the axial front ends are respectively a first axial front end 10F1, a second axial front end 10F2 and a third axial front end 10F3; the axial rear ends are respectively a first axial rear end 5B1, a second axial rear end 5B2 and a third axial rear end 5B3, and the axial tension variation of a single damper in the detection period delta t is calculated; .
S1213, the process goes to step S13 according to the single damper axial tension variation amount to determine.
Wherein, the step S122 is further divided into the following steps:
s1221, when the duct piece is impacted by an external load, obtaining the relative speed through the change of the distance between an impact load and the duct piece in a detection period delta t of a first radar sensor 11F, a second radar sensor 11B, a third radar sensor 11L and a fourth radar sensor 11R which are uniformly distributed in four directions of the duct piece;
s1222, calculating the acceleration of the impact load in the detection period delta t according to the relative speed obtained in the step S1221;
after S1223, the relative velocity and acceleration obtained in steps S1221 and S1222, and the relative distance obtained in step S11, the time to collision between the impact load and the segment and the initial velocity at the time of collision are calculated according to newton' S second law.
In step S11, calculating relative changes Δ S11F, Δ S11B, Δ S11L, and Δ S11R of the relative distances measured by the respective radar sensors within Δ t, and comparing the relative changes Δ S11F, Δ S11B, Δ S11L, and Δ S11R;
referring to FIG. 1, when max { Δ S11B, Δ S11R }. Ltoreq min { Δ S11F, Δ S11L }, the impact force area is in zone I;
when max { Δ S11F, Δ S11R } is less than or equal to min { Δ S11B, Δ S11L }, the impact acting force area is in the area II;
when max { Δ S11F, Δ S11L }. Is less than or equal to min { Δ S11B, Δ S11R }, the impact acting force area is in a zone III;
when max (delta S11B, delta S11L) is less than or equal to min (delta S11F, delta S11R), the impact acting force area is in an IV area;
the inner wall of the pipe piece is divided into four regions which are opposite in pairs by the I region, the II region, the III region and the IV region;
the region I is located between the first axial forward end 10F1 and the second axial forward end 10F 2; said region II is located between the first axial rear end 5B1 and the second axial rear end 5B 2; the zone III is located between the second rearward end 5B2 and the third rearward end 5B 3; the IV zone is located between the second axial front end 10F2 and the third axial front end 10F 3.
Wherein, the step S3 is divided into the following steps:
s31, according to the distance change values delta S11F, delta S11B, delta S11L and delta S11R measured in the step S11 and the axial tension change value measured in the step S121, when the distance change value is larger than a preset safety value, judging that impact external load occurs; when the axial tension variation value is larger than a preset safety value, judging that vibration occurs;
and S32, estimating the damping adjustment required position and presetting the initial current of the magnet exciting coil of the magnetic control damping device according to the judgment result of the step S31.
Wherein, the step S32 is further divided into the following steps:
s321, when an impact external load occurs, determining a damping adjustment demand direction according to the impact force acting area in the step S11, and predicting a damping adjustment sequence;
meanwhile, according to the load characteristic parameters estimated in the step S2, an impact dynamics model and a required magnetic control damping device ideal damping force model are constructed;
wherein the ideal damping force model is obtained by:
in the formula (2), F Need to For desired damping force, v Beginning of the design The initial velocity at which the impact occurs, L MR Is the compression stroke m of a disc spring in a magnetic control damping device 0 Mass of impact load;
presetting initial current of a damping regulator in the magnetic control damping device through an impact dynamics model and an ideal damping force model;
s322, when a vibration load occurs, determining a damping adjustment demand direction according to the impact force acting area in the step S11, and predicting a damping adjustment sequence; and (5) constructing an impact dynamics model and a required magnetic control damping device ideal damping force model through the load characteristic parameters estimated in the step (S2).
Referring to fig. 2, 3 and 4, the magnetic control damping device 15 used in the shield tunnel segment vibration and impact prediction control system mainly includes a piston cylinder 15a, a piston head 15b, a bolt connection piston rod 15c and a segment connection ring sleeve 15d, and the piston cylinder 15a and the segment connection ring sleeve 15d are provided with pressure detection components for detecting stress changes of the piston cylinder 15 a. The piston head 15b and the piston cylinder 15a are both made of magnetic conductive materials, and the bolt connection piston rod 15c and the segment connection ring sleeve 15d are both made of magnetic non-conductive materials. Magnetorheological fluid 15e is filled between the piston cylinder 15a and the piston head 15b, an exciting coil 15f is arranged in an inner cavity of the piston cylinder 15a, and the pressure detection assembly can transmit detection data to the control assembly, so that the control assembly can adjust the current of the exciting coil 15f, the magnetic field intensity excited by the exciting coil 15f is adjusted, and the flowing characteristic of the magnetorheological fluid 15e is changed. When the flow characteristics of the magnetorheological fluid 15e change, the damping of the piston head 15b and the bolt connection piston rod 15c by the magnetorheological fluid 15e correspondingly changes, and finally the function of adaptively adjusting the damping is realized, so that a better vibration reduction and impact resistance effect is achieved.
By adopting the structure, the segment bolt is arranged in the bolt through hole, the acting force applied to the segment bolt is transmitted to the piston cylinder through the piston head and the bolt connecting piston rod, then transmitted to the segment connecting ring sleeve through the mounting seat and finally transmitted to the shield segment through the segment connecting ring sleeve; the stress change of each mounting seat is detected through the pressure detection assembly, the detection data are transmitted to the control assembly, the stress size and the stress direction of the piston head and the bolt connecting piston rod can be calculated by the control assembly, the current of the magnet exciting coil is adjusted, namely, the magnetic field intensity excited by the magnet exciting coil is changed, the purpose of changing the flow characteristic of the magnetorheological fluid is realized, the flow characteristic of the magnetorheological fluid is changed, the magnetorheological fluid can correspondingly change the damping size of the piston head and the bolt connecting piston rod, the function of adaptively adjusting the damping size is finally realized, the better vibration and impact resistance effect is achieved, the fatigue life of a segment bolt is prolonged, and the phenomenon that a tunnel is damaged due to overload damage of the segment bolt is avoided.
Wherein, two bolt connecting piston rods 15c are coaxially and fixedly arranged at two ends of the piston head 15b and both penetrate out of the piston cylinder 15a; the piston head 15b and the two bolt-connected piston rods 15c have bolt through holes a coaxially passing therethrough, and segment bolts are installed in the bolt through holes a.
And the bolt-connected piston rods 15c are respectively sleeved with a reset compression spring 15p, one end of each reset compression spring 15p is abutted against the corresponding end face of the piston head 15b, and the other end of each reset compression spring 15p is abutted against the cavity wall of the inner cavity of the piston cylinder 15a, so that the piston heads 15b are elastically supported in the inner cavities of the piston cylinders 15 a. Therefore, the piston head 15b and the bolt-connected piston rod 15c at both ends can move axially relative to the piston cylinder 15a in synchronization with each other against the elastic force, and at the same time, can be restored by the elastic force of the two restoring compression springs 15p after the external force is lost.
The outer circumferential surface of the piston cylinder 15a is distributed with mounting seats 15a1 which protrude outwards, a gap B is reserved between the segment connecting ring sleeve 15d and the piston cylinder 15a, the segment connecting ring sleeve is provided with mounting grooves 15d1 which are matched with the corresponding mounting seats 15a1, the mounting seats 15a1 are respectively inserted into the corresponding mounting grooves 15d1, and pressure detection components for detecting stress changes of the piston cylinder 15a are arranged. Two force transmission springs 15k are sleeved outside the piston cylinder 15a, the two force transmission springs 15k are respectively located on two sides of each mounting seat 15a1, one end of each force transmission spring is supported on each mounting seat 15a1, and the other end of each force transmission spring is supported on the segment connecting ring sleeve 15d, so that the segment connecting ring sleeve 15d is elastically sleeved outside the piston cylinder 1.
In order to facilitate the assembly of the internal components, the piston cylinder 15a is composed of two symmetrical sub-piston cylinders 15a ', and the segment connecting ring 15d is composed of a connecting ring body 15d ' and cover plates 15d ″ located on both sides of the connecting ring body 15d '.
The pressure detection assembly comprises a radial force detection unit 15g arranged at the outer end of the mounting seat 15a1 along the radial direction of the piston cylinder 15a, a rotating force detection unit 15h arranged at two sides of the mounting seat 15a1 along the rotating direction of the piston cylinder 15a, and an axial force detection unit 15i and a damping pad 15j arranged at two sides of the mounting seat 15a1 along the axial direction of the piston cylinder 15a, wherein the radial force detection unit 15g, the rotating force detection unit 15h, the axial force detection unit 15i and the damping pad 15j are all supported between the corresponding mounting seat 15a1 and the mounting groove 15d 1. Because the segment bolt is installed, the axial direction of the piston cylinder 15a only has acting force in one direction, therefore, the embodiment only sets up the axial force detection unit 15i on one side, and the opposite side sets up the damping pad 15j, can reduce cost and the algorithm difficulty of control assembly.
The control assembly comprises a data collector 15L, a controller 15m and an adjustable direct-current power supply 15n, and the controller 15m can adjust the current supplied to the magnet exciting coil 15f by the adjustable direct-current power supply 15m according to the output signal of the pressure detection assembly collected by the data collector 15L. The segment bolt is arranged in the bolt through hole A, acting force applied to the segment bolt is transmitted to the piston cylinder 15a through the piston head 15b and the bolt connecting piston rod 15c, then transmitted to the segment connecting ring sleeve 15d through the mounting seat 15a1, and finally transmitted to the shield segment through the segment connecting ring sleeve 15 d. Therefore, the radial force detection units 15g, the rotational force detection units 15h and the axial force detection units 15i can detect the stress changes of the installation bases 15a1 in the radial direction, the axial direction and the rotation direction, and transmit the detection data to the data collector 15L, the data collector 15L transmits the signal to the controller 15m, the controller 15m can calculate the stress magnitude and the stress direction of the piston head 15b and the bolt connection piston rod 15c (namely, the stress magnitude and the stress direction of the segment bolt can be known in real time), so that the output current magnitude of the adjustable direct current power supply 15n (namely, the current magnitude of the excitation coil 15 f) can be adjusted adaptively according to the information, the magnetic field intensity excited by the excitation coil 15f is changed, the purpose of changing the flow characteristic of the variable liquid 15e is achieved, the function of adaptively adjusting the damping magnitude is finally achieved, and a better shock absorption effect is achieved.
Reference is made above in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described above with reference to the drawings are exemplary and intended to be illustrative of the invention and are not to be construed as limiting the invention.
In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "clockwise", "counterclockwise", and the like, indicate orientations and positional relationships based on those shown in the drawings, and are used only for convenience of description and simplicity of description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed in a particular orientation, and be operated, and thus, are not to be construed as limiting the present invention.
In the present invention, unless otherwise explicitly stated or limited, the terms "mounted," "connected," "fixed," and the like are to be construed broadly and may, for example, be fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In the present invention, unless otherwise expressly stated or limited, "above" or "below" a first feature means that the first and second features are in direct contact, or that the first and second features are not in direct contact but are in contact with each other via another feature therebetween. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.
Finally, it should be noted that the above-mentioned description is only a preferred embodiment of the present invention, and that those skilled in the art can make various similar representations without departing from the spirit and scope of the present invention.
Claims (8)
1. A shield tunnel segment vibration and impact pre-estimation control method is characterized by comprising the following steps:
s1, detecting the characteristic quantity of the load of a duct piece, comparing the load type with a preset safety characteristic quantity, and starting a magnetic control damping device when the characteristic quantity of the load is greater than the preset safety characteristic quantity;
s2, estimating load characteristic parameters borne by the duct piece;
s3, estimating a damping adjustment required position and presetting an initial current of a magnet exciting coil of the magnetic control damping device through the segment load characteristic quantity and the load characteristic parameter, so that the magnetic control damping device generates a corresponding damping force in the vibration or impact load generation process;
wherein, the step S1 is carried out according to the following steps:
s11, respectively detecting the tension force applied to the segment bolt and the distance between a collision impact object and the segment through a pressure sensor;
s12, calculating the occurrence time of the impact load on the duct piece and the stress variation of the duct piece according to the measurement result of the step S11;
s13, respectively comparing the time of impact load with preset safe time, and comparing the stress variation of the duct piece with preset safe variation, wherein the preset safe time is the sum of the response lag time of the damping device and the detection period of the relative distance between the impact object and the duct piece, and the safe variation is set according to the measurement result of the shield duct piece connection comprehensive stress experiment;
s14, when the time of the impact load is more than or equal to the preset safe time or the stress variation of the duct piece is less than the preset safe variation, returning to the step S11; when the time of the impact load is less than the preset safe time or the stress variation of the duct piece is more than or equal to the preset safe variation, starting the magnetic control damping device;
wherein, the step S12 is carried out according to the following steps:
s121, when the pipe piece is stressed and changed, the connecting bolt acts on the damping regulators which are circumferentially distributed, so that the sensing units which are distributed on the damping regulators are extruded to different degrees, namely the first pressure sensing unit (n 1), the second pressure sensing unit (n 2), the third pressure sensing unit (n 3), the fourth pressure sensing unit (n 4), the fifth pressure sensing unit (n 5), the sixth pressure sensing unit (n 6), the seventh pressure sensing unit (n 7) and the eighth pressure sensing unit (n 8) are deformed, and the capacitance change value of each sensing unit can be obtained;
and S122, when the duct piece is impacted by external load, calculating the time of impact of the duct piece through the distances of impact objects detected by the first radar sensor (11F), the second radar sensor (11B), the third radar sensor (11L) and the fourth radar sensor (11R) which are uniformly distributed on the duct piece.
2. The shield tunnel segment vibration and impact prediction control method according to claim 1, wherein the step S121 comprises the steps of:
s1211, calculating corresponding stress change according to the capacitance change value of the detection sensing unit, and acquiring the axial tension of the single damper according to the following formula:
F nz ＝F n1 +F n2 +…+F n8 (1)
in the formula (1), F nz Is a single damper axial force; f n1 Is the axial acting force of the first pressure sensing unit; f n2 Is the axial acting force of the second pressure sensing unit; f n3 Is the axial acting force of the third pressure sensing unit; f n4 Is the axial acting force of the fourth pressure sensing unit; f n5 Is the axial acting force of the fifth pressure sensing unit; f n6 Is the axial acting force of the sixth pressure sensing unit; f n7 Is the axial acting force of the seventh pressure sensing unit; f n8 Is the axial acting force of the eighth pressure sensing unit;
s1212, calculating the variation of the axial tension of the single damper in a detection period delta t according to the calculated axial tension of the single damper and 4 large directions of all dampers installed on the duct piece, wherein the 4 large directions of each damper installed on the duct piece are respectively an annular left side, an annular right side, an axial front end and an axial rear end; the circular left sides are respectively a first circular left side (3L 1) and a second circular left side (3L 2); the annular right sides are respectively a first annular right side (7R 1) and a second annular right side (7R 2); the axial front ends are respectively a first axial front end (10F 1), a second axial front end (10F 2) and a third axial front end (10F 3); the axial rear ends are respectively a first axial rear end (5B 1), a second axial rear end (5B 2) and a third axial rear end (5B 3), and the variation of the axial tension of the single damper in the detection period delta t is calculated;
s1213, the process goes to step S13 according to the single damper axial tension variation amount to determine.
3. The shield tunnel segment vibration and impact prediction control method according to claim 1 or 2, wherein the step S122 comprises the steps of:
s1221, when the duct piece is impacted by an external load, obtaining relative speed through changes of distances between impact loads and the duct piece in a detection period delta t of a first radar sensor (11F), a second radar sensor (11B), a third radar sensor (11L) and a fourth radar sensor (11R) which are uniformly distributed in four directions of the duct piece;
s1222, calculating the acceleration of the impact load in the detection period delta t according to the speed obtained in the step S1221;
after S1223, the velocity and acceleration obtained in steps S1221 and S1222, and the distance obtained in step S11, the time to collision between the impact load and the segment and the initial velocity at the time of collision are calculated according to newton' S second law.
4. The shield tunnel segment vibration and impact prediction control method according to claim 1 or 2, characterized in that in step S11, relative changes Δ S11F, Δ S11B, Δ S11L, Δ S11R of relative distances measured by respective radar sensors within Δ t are calculated and compared in magnitude;
when max { delta S11B, delta S11R } < min { delta S11F, delta S11L }, the impact acting force area is in an area I;
when max { Δ S11F, Δ S11R } is less than or equal to min { Δ S11B, Δ S11L }, the impact acting force area is in the area II;
when max { Δ S11F, Δ S11L }. Is less than or equal to min { Δ S11B, Δ S11R }, the impact acting force area is in a zone III;
when max (delta S11B, delta S11L) is less than or equal to min (delta S11F, delta S11R), the impact acting force area is in an IV area;
the area I, the area II, the area III and the area IV divide the inner wall of the pipe piece into four areas which are opposite in pairs;
wherein the zone I is located between the first axial front end (10F 1) and the second axial front end (10F 2); the zone II is located between the first axial rear end (5B 1) and the second axial rear end (5B 2); zone III is located between the second rearward end (5B 2) and the third rearward end (5B 3); the IV zone is located between the second axial front end (10F 2) and the third axial front end (10F 3).
5. The shield tunnel segment vibration and impact prediction control method according to claim 4, wherein the step S3 comprises the following steps:
s31, according to the distance change values delta S11F, delta S11B, delta S11L and delta S11R measured in the step S11 and the axial tension change value measured in the step S121, when the distance change value is larger than a preset safety value, judging that impact external load occurs; when the change value of the axial tension is larger than a preset safety value, judging that vibration occurs;
and S32, estimating the damping adjustment required position and presetting the initial current of the magnet exciting coil of the magnetic control damping device according to the judgment result of the step S31.
6. The shield tunnel segment vibration and impact estimation control method according to claim 5, wherein the step S32 includes the steps of:
s321, when an impact external load occurs, determining a damping adjustment demand direction according to the impact force acting area in the step S11, and predicting a damping adjustment sequence;
meanwhile, according to the load characteristic parameters estimated in the step S2, an impact dynamics model and a required magnetic control damping device ideal damping force model are constructed;
wherein the ideal damping force model is obtained by:
in the formula (2), F Need to For desired damping force, v First stage The initial velocity at which the impact occurs, L MR Is the compression stroke m of a disc spring in a magnetic control damping device 0 Mass as impact load;
presetting initial current of a damping regulator in the magnetic control damping device through an impact dynamics model and an ideal damping force model;
s322, when a vibration load occurs, determining a damping adjustment demand direction according to the impact force acting area in the step S11, and predicting a damping adjustment sequence; and (5) constructing an impact dynamics model and a required magnetic control damping device ideal damping force model through the load characteristic parameters estimated in the step (S2).
7. The utility model provides a shield tunnel section of jurisdiction vibration and impact predict control system which characterized in that: comprises a detection system and a magnetic control damping device; the detection system comprises a sensing unit and a signal conditioning module (14) and is used for detecting the variation of the stress of the duct piece (1); the magnetic control damping device comprises a program control power supply (12) and damping regulators, the damping regulators are respectively a first damping regulator (3), a second damping regulator (5), a third damping regulator (7) and a fourth damping regulator (10), and each damping regulator is connected with a controller (13) through the program control power supply (12);
the damping regulator changes the magnetic control cement and the magnetorheological elastomer in the damping regulator to generate damping force by changing applied current, and after the magnetorheological cement is injected into the oil storage cylinder of the impact damper, the magnetic field of the coil changes the flow characteristic of the magnetorheological cement, so that the motion of the piston of the impact damper can be controlled to be blocked, and impact buffering is realized; the magnetorheological elastomer is arranged in series connection to resist impact to form the vibration isolator, and is changed by the damping force of the magnetic field of the coil, so that the vibration is controllably isolated.
8. The shield tunnel segment vibration and impact prediction control system according to claim 7, wherein the controller (13) comprises a load determination unit, a parameter prediction unit and a current control unit; the load judging unit is used for judging and judging the variation of the stress of the duct piece (1), the preset safe variation and the variation among load types, the input end of the load judging unit is connected with the output end of the signal conditioning module (14), and the output end of the load judging unit is connected with the input end of the parameter estimating unit; the parameter pre-estimating unit is used for pre-estimating the load grade, the damping adjusting direction, the damping force and the initial current of the damping adjuster; the current control unit is used for controlling the programmable power supply (12) to change output current to the damping regulator, the input end of the current control unit is connected with the output end of the parameter estimation unit, and the output end of the current control unit is connected with the input end of the programmable power supply (12);
the signal conditioning module (14) comprises a signal amplifier, a filter and an A/D converter, wherein the input end of the amplifier is connected with the output end of the pressure sensor, the output end of the amplifier is connected with the input end of the filter, the output end of the filter is connected with the input end of the A/D converter, and the output end of the A/D converter is connected with the input end of the controller (13).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110733614.0A CN113447187B (en) | 2021-06-30 | 2021-06-30 | Shield tunnel segment vibration and impact pre-estimation control method and control system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110733614.0A CN113447187B (en) | 2021-06-30 | 2021-06-30 | Shield tunnel segment vibration and impact pre-estimation control method and control system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113447187A CN113447187A (en) | 2021-09-28 |
| CN113447187B true CN113447187B (en) | 2022-10-04 |
Family
ID=77814344
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110733614.0A Active CN113447187B (en) | 2021-06-30 | 2021-06-30 | Shield tunnel segment vibration and impact pre-estimation control method and control system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113447187B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114200444A (en) * | 2021-11-12 | 2022-03-18 | 广州地铁设计研究院股份有限公司 | Shield construction quality detection equipment and method |
| CN114738053B (en) * | 2022-04-26 | 2023-03-21 | 中铁隧道局集团路桥工程有限公司 | Shield tunnel construction is with closing on pipeline safety pressure detection device |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103195858A (en) * | 2013-04-15 | 2013-07-10 | 沈阳航空航天大学 | Magnetorheological buffering unit structure based on impact load and control method thereof |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3926696C3 (en) * | 1989-08-12 | 1998-02-26 | Freudenberg Carl Fa | Rubber bearing with hydraulic damping |
| JP2009174208A (en) * | 2008-01-25 | 2009-08-06 | Jfe Engineering Corp | Tunnel segment |
| CN104179118B (en) * | 2014-08-20 | 2016-01-20 | 重庆邮电大学 | The method for designing of the magnetorheological bearing-damper of anti-impact vibration isolation type bridge pier and device |
| CN104228741B (en) * | 2014-09-03 | 2016-08-17 | 重庆大学 | Car crass Prediction Control method and system based on magnetic control clay buffer unit |
| CN104677587B (en) * | 2015-03-25 | 2017-03-22 | 重庆邮电大学 | Pier buffering and vibration isolating type multifunctional test platform based on intelligent magnetic rubber supporting seat |
| CN105715735B (en) * | 2016-03-02 | 2018-01-16 | 江苏大学 | The controllable vibrating isolation system of a kind of stiffness and damping and inertia force and its control method |
| CN206035499U (en) * | 2016-06-24 | 2017-03-22 | 中国电建集团华东勘测设计研究院有限公司 | Adaptable shield tunnel structure of damping shock insulation |
| CN111173932B (en) * | 2020-02-15 | 2022-06-21 | 重庆工商大学 | Pressure self-adaptation sealing device based on magnetic fluid |
| CN112031806A (en) * | 2020-08-11 | 2020-12-04 | 大连理工大学 | Design method for vibration reduction of TBM support shell |
-
2021
- 2021-06-30 CN CN202110733614.0A patent/CN113447187B/en active Active
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103195858A (en) * | 2013-04-15 | 2013-07-10 | 沈阳航空航天大学 | Magnetorheological buffering unit structure based on impact load and control method thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| CN113447187A (en) | 2021-09-28 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN113447187B (en) | Shield tunnel segment vibration and impact pre-estimation control method and control system | |
| CN107627804B (en) | Damper device of active suspension system and control method of damper device | |
| US8793052B2 (en) | Electromagnetic suspension system | |
| US20210339594A1 (en) | Hybrid-electromagnetic suspension capable of self-powering and control method thereof | |
| CN100404293C (en) | Electronically-controlled suspension apparatus and damping force control method | |
| CN101213436B (en) | Interface module of an electric motor for calculating the service life of a bearing | |
| US8276466B2 (en) | Two or three-axis shear load cell | |
| JP2011500402A (en) | Intelligent continuous monitoring system for application in shock absorbers | |
| CN103061425B (en) | A kind of series and parallel multistage valve viscous damping method and damper | |
| US5686672A (en) | Stress and load variation detector | |
| CN101269618A (en) | Control method for damping value of electronic control air spring damping apparatus with three-gear | |
| TW201408901A (en) | Shock absorber for a bicycle | |
| Carratù et al. | Semi-active suspension system for motorcycles: From the idea to the industrial product | |
| CN104864026A (en) | Compound electromagnetic friction damper | |
| EP1105298A2 (en) | Vehicle/bridge vibration mitigation assembly | |
| CN206974347U (en) | A kind of measurement apparatus for being used for leaf spring earhole perpendicularity and the depth of parallelism | |
| GB2502038A (en) | A system for indicating the state of loading of a compression coil spring of a vehcile suspension | |
| Liu et al. | A validation study of ACS-SSI for online condition monitoring of vehicle suspension systems | |
| KR20180014599A (en) | Damper speed estimation method for the electronically controlled suspension system | |
| CN112857543A (en) | Dynamic weighing system for detecting wide-speed full-driving behavior under off-site law enforcement | |
| CN115789161B (en) | Viscous hydraulic damper with online monitoring function and monitoring method | |
| CN113137446B (en) | Segment bolt self-adaptive damping device | |
| US11635075B1 (en) | Gerotor pump with bearing | |
| JP2024056544A (en) | Damping force control device and damping force control method | |
| CN218027157U (en) | Composite energy-consuming damper for cable bearing bridge |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |