CN111692264B - Resonance eliminating device for mainframe based on vibration compensation - Google Patents
Resonance eliminating device for mainframe based on vibration compensation Download PDFInfo
- Publication number
- CN111692264B CN111692264B CN202010379873.3A CN202010379873A CN111692264B CN 111692264 B CN111692264 B CN 111692264B CN 202010379873 A CN202010379873 A CN 202010379873A CN 111692264 B CN111692264 B CN 111692264B
- Authority
- CN
- China
- Prior art keywords
- pipe
- pressure
- signal
- piston
- feedback
- 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
-
- 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
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
- F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
- F16F9/22—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with one or more cylinders each having a single working space closed by a piston or plunger
-
- 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
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/43—Filling or drainage arrangements, e.g. for supply of gas
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2230/00—Purpose; Design features
- F16F2230/06—Fluid filling or discharging
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2230/00—Purpose; Design features
- F16F2230/08—Sensor arrangement
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2230/00—Purpose; Design features
- F16F2230/18—Control arrangements
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The invention discloses a vibration compensation-based resonance elimination device for a large-scale machine, which comprises a base, a plurality of groups of shock absorption pads and a compensation assembly, wherein the shock absorption pads are arranged on the base, and the head parts of the compensation assemblies are embedded into the shock absorption pads. The compensation assembly comprises a first pipe cylinder, a second pipe cylinder, an oil liquid circulation assembly and a feedback correction controller, and a vertical accommodating hole is formed in the surface, away from the base, of the shock absorption pad; the first pipe cylinder comprises a signal pipe, the signal pipe is arranged in the shock absorption pad, a signal piston is arranged in the signal pipe upwards, and a measuring point of the pressure sensor is positioned on the inner side surface or the bottom of the signal pipe; the second pipe cylinder comprises a pressure regulating pipe, a feedback piston, a pressure boosting pipe, a pressure relief pipe and an electromagnetic valve, wherein the feedback piston is arranged upwards in the pressure regulating pipe, the inner side surface or the bottom of the pressure regulating pipe is connected with the oil liquid circulating assembly through the pressure boosting pipe and the pressure relief pipe, and the electromagnetic valve is arranged on the pressure boosting pipe and the pressure relief pipe; the electromagnetic valve and the pressure sensor are both electrically connected with the feedback correction controller.
Description
Technical Field
The invention relates to the field of vibration elimination devices, in particular to a vibration compensation-based resonance elimination device for a large-scale machine.
Background
The machine vibrates during operation, and only the amplitude is different. In the prior art, vibration is generally counteracted by arranging a buffer shock pad between a foot and a base of a machine, but the effect is often not ideal.
The vibration of the machine is mainly divided into two types, one is that the vibration caused by the tolerance of a bearing or a main shaft is low-amplitude high-frequency vibration, the frequency of the vibration is generally multiple of the rotating speed of the machine, and the frequency is higher; another is high amplitude vibration generated by coupling of factors such as operating conditions: for example, the machine vibrates periodically due to periodic pressure fluctuation when the gas pump is conveyed, or a certain disturbing force is accumulated on the main shaft, and is released for a short time after reaching a certain degree and then enters the next accumulation process. The bradyseism pad can only be used for eliminating the vibration of low amplitude, and the difficult vibration of big amplitude is eliminated through the bradyseism pad, because if the bradyseism pad is harder, then its vibration isolation effect is just relatively poor, can lose the vibration elimination effect of its low amplitude, if the bradyseism pad is softer, then it needs great deformation just can offset pressure variation for the footing displacement is great, and then influences machine operating stability. The prior art has no targeted classification and elimination device, and certain vibration which is not eliminated can cause machine resonance to cause serious accidents.
Disclosure of Invention
The invention aims to provide a resonance elimination device for a mainframe based on vibration compensation, which aims to solve the problems in the prior art.
In order to achieve the purpose, the invention provides the following technical scheme:
the utility model provides a resonance remove device for mainframe based on vibration compensation, includes base and a plurality of groups bradyseism pad, compensation assembly, and the bradyseism pad sets up on the base, and compensation assembly's head embedding bradyseism is filled up.
The large machine is provided with a plurality of bottom feet, and a shock absorption pad is arranged between each bottom foot and the base to isolate high-frequency low-amplitude vibration.
Furthermore, the compensation assembly comprises a first pipe cylinder, a second pipe cylinder, an oil liquid circulation assembly and a feedback correction controller, and a vertical accommodating hole is formed in the surface, away from the base, of the shock absorption pad;
the first pipe cylinder comprises a signal pipe, a signal piston and a pressure sensor, the signal pipe is arranged in the shock absorption pad, the bottom of the signal pipe is closed, the signal piston is arranged in the signal pipe upwards, the top end of the signal piston is positioned in the accommodating hole, the top end of the signal piston is lower than the upper surface of the shock absorption pad, the signal piston is hooked by an annular limiting bulge on the inner surface of the signal pipe, so that the signal piston cannot be pushed upwards infinitely due to the pressure in the signal pipe and can only reach the height position of the annular limiting bulge, the signal piston can only be pressed downwards during operation, the top end of the position signal piston is lower than the upper surface of the shock absorption pad at the moment, and a measuring point of the pressure sensor is positioned on the inner side surface or the bottom of the signal pipe;
the second pipe cylinder comprises a pressure regulating pipe, a feedback piston, a pressure boosting pipe, a pressure relief pipe and an electromagnetic valve, wherein the feedback piston is arranged in the pressure regulating pipe upwards, the top of the feedback piston is positioned in the accommodating hole, the top end of the feedback piston is flush with the top end of the signal piston, the feedback piston is also hooked by an annular limiting bulge on the inner wall of the pressure regulating pipe, the feedback piston cannot move upwards infinitely and can only be pressed down, the inner side surface or the bottom of the pressure regulating pipe is connected with an oil liquid circulating assembly through the pressure boosting pipe and the pressure relief pipe, the flowing direction of a fluid in the pressure boosting pipe is from the oil liquid circulating assembly to the pressure regulating pipe, the flowing direction of a fluid in the pressure relief pipe is from the pressure regulating pipe to the oil liquid circulating assembly, and the electromagnetic valves are arranged on the pressure boosting pipe and the pressure relief pipe;
the electromagnetic valve and the pressure sensor are both electrically connected with the feedback correction controller.
The flow principle of the compensation component is as follows: when the footing is pressed down to the signal piston and the feedback piston due to large vibration, the signal piston and the feedback piston are both pressed down, the pressure in the signal pipe rises, the pressure sensor gives a signal to the feedback correction controller, the feedback correction controller obtains the signal to control the electromagnetic valve on the pressure rising pipe to open, then the high-pressure oil in the oil liquid circulating assembly is led into the pressure regulating pipe, the oil pressure in the pressure regulating pipe rises, the force of the feedback piston reversely propping against the footing is larger until the footing is counteracted, the pressing process of the footing due to large vibration is divided into two curves of pressing force increasing and pressing force reducing, the oil pressure in the pressure regulating pipe rises in the pressing force increasing link, the oil pressure in the pressure regulating pipe is discharged through the pressure relief pipe in the pressing force reducing link, if the oil pressure regulation of the pressure regulating pipe is carried out after the vibration, the electromagnetic valve appears to be lagged, so that the electromagnetic valve is allocated through the feedback correction controller, The signal and the switching value of the pressure sensor achieve the purpose of automatic control, the automatic control is a closed-loop control system, and additional expected conditions are as follows: the system allows larger steady-state error, but the overshoot is larger, and the rise time and the adjusting time are shorter.
In addition, because the self-control regulating quantity is arranged in the pressure regulating pipe, the target quantity is arranged in the signal pipe, and the feedback piston is blocked by a limiting bulge, the oil pressure in the pressure regulating pipe can be continuously increased to the maximum oil pressure which can be provided by the oil liquid circulating assembly, and then when the vibration of the bottom foot is resisted, the bottom foot is kicked to an iron plate, and the rigid collision can not play a role of buffering. The priority of the automatic control adjustment between the pressure regulating pipe and the signal pipe is lower than that of the total adjustment process, and the automatic control adjustment of the pressure regulating pipe and the signal pipe is started only when the total adjustment process enters a steady state.
The conduction of oil pressure is rapid, and as the transmission medium of autonomous system, the transmission speed demand can be satisfied to the high-amplitude vibration of low frequency of reply footing.
Further, fluid circulation subassembly includes high-pressure tank, low-pressure jar, booster pump, and high-pressure tank and low-pressure jar carry out the fluid through the booster pump connection and step up, and the booster pipe is connected to the high-pressure tank, and the pressure release pipe is connected to the low-pressure jar.
High-pressure oil and low-pressure oil are respectively stored in the high-pressure tank and the low-pressure tank, and the oil which is led into the pressure regulating pipe or discharged from the pressure regulating pipe is prepared all the time; the booster pump maintains the working pressures of the high-pressure tank and the low-pressure tank.
Furthermore, the first pipe cylinder also comprises a pre-adjusting pipe and a hand valve, one end of the pre-adjusting pipe is connected into the signal pipe, the other end of the pre-adjusting pipe is connected to an external pressure source, and the hand valve is installed on the pre-adjusting pipe. The pilot line and hand valve are used to initially set the pressure in the signal line as desired in the autonomous system.
Preferably, the hand valve is a pressure regulating hand valve with a pressure gauge. When the hand valve is opened, pressure is introduced into the signal pipe, and a pressure gauge is arranged, so that whether a preset value is reached or not can be observed conveniently on site, otherwise, detection or pre-adjustment is needed from the introduction position of the pressure source.
The signal pipe and the pressure regulating pipe are arranged in a sleeved and embedded mode, the signal pipe is arranged at the upper portion in the pressure regulating pipe, the outer wall of the lower portion of the signal pipe is mounted on the inner wall of the pressure regulating pipe through a support, the feedback piston is annular, and a lower sealing ring of the feedback piston is in contact with the outer wall of the signal pipe and the inner wall of the pressure regulating pipe.
The annular feedback piston and the signal piston are concentrically arranged, the force applied by the foot to the annular feedback piston and the signal piston is horizontally uniform, and the self-control precision is not influenced due to the fact that the foot is not deviated from a horizontal plane due to different force applying positions.
As optimization, the second pipe cylinder further comprises a pressure transfer piston, the lower end of the pressure regulating pipe extends into the shock absorption pad which is farthest away from the pressure regulating pipe, the pipe orifice at the lower end of the pressure regulating pipe faces downwards, and the pressure transfer piston is arranged at the lower end of the pressure regulating pipe and is in contact with the base. Unless the transfer function of the feedback correction controller in the compensation assembly is properly designed, the lead adjustment is very well performed, even if most of the vibration is compensated and eliminated, a part of the vibration of the foot which cannot be eliminated by the compensation assembly is loaded on the pressure regulating pipe, and the rotary pressing piston is arranged to guide the part of the force to the farthest base position.
Preferably, the solenoid valve is a high-speed solenoid valve. The response time of the high-speed electromagnetic valve is extremely short, the requirement of an automatic control system is met, and the lengthening of the automatic control adjusting time caused by hardware problems is eliminated as far as possible.
For optimization, the feedback correction controller is a PD or PID controller. The PD controller is a proportional-derivative controller, the lead correction performance of the PD controller is excellent, the system adjusting time is shortened, and the phase stability margin is excellent. The PID controller is a PID controller, which not only has the characteristics of a PD controller, but also has the characteristics of a PI controller that can improve the steady-state performance of the system, although the steady-state error in the steady-state performance is not a factor to be considered in the present invention. The PD or PID controller is a mature controller commonly used in automatic control, and can be set after being bought.
Compared with the prior art, the invention has the beneficial effects that: the low-amplitude high-frequency vibration of the bottom foot is adaptively eliminated by the shock absorption pad, the high-amplitude vibration is compensated by the compensation assembly, the compensation assembly comprises an automatic control system for advanced adjustment, an execution component for collecting system information and performing adjustment, the feedback piston provides a supporting force for the bottom foot to offset the amplitude by the oil pressure in the pressure regulating pipe controlled by the feedback correction controller, and the force is applied by the oil pressure and can be provided without deformation like a cushion pad; the response time of working components such as a high-speed electromagnetic valve, oil pressure transmission and the like and media is short, is shorter than the high-amplitude vibration period of the footing, and is not restricted by self-control regulation due to hardware; the signal piston and the feedback piston which are sleeved on the inner ring layer and the outer ring layer are uniformly stressed and fed back, and the situation that the stress condition deviates from the expectation due to the inclined force application angle cannot occur on the same horizontal plane.
Drawings
In order that the present invention may be more readily and clearly understood, a more particular description of the invention briefly described above will be rendered by reference to specific embodiments that are illustrated in the appended drawings.
FIG. 1 is a schematic view of the overall configuration of the present invention;
FIG. 2 is a cross-sectional view of the shock pad and compensation assembly of the present invention;
FIG. 3 is view A of FIG. 2;
FIG. 4 is view B of FIG. 2;
FIG. 5 is a schematic structural view of the head of the first tube cylinder and the head of the second tube cylinder;
FIG. 6 is a schematic flow chart of the operation of the compensating assembly of the present invention;
FIG. 7 is a graph illustrating vibration curves of machine vibrations;
FIG. 8 is a schematic diagram of a compensation overlay curve of the compensation component;
FIG. 9 is a control block diagram of a compensation assembly feedback adjustment system.
In the figure: 1-shock absorption pad, 11-accommodating hole, 2-compensation component, 21-first pipe cylinder, 211-signal pipe, 212-signal piston, 213-pre-regulation pipe, 214-hand valve, 215-pressure sensor, 22-second pipe cylinder, 221-pressure regulation pipe, 222-feedback piston, 223-pressure boosting pipe, 224-pressure relief pipe, 225-electromagnetic valve, 229-pressure conversion piston, 23-oil circulation component, 231-high pressure tank, 232-low pressure tank, 233-pressure boosting pump, 24-PID controller, 3-base and 9-baseboard.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the 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.
As shown in fig. 1 and 2, a vibration compensation-based resonance elimination apparatus for a mainframe includes a base 3, a plurality of groups of shock absorbing pads 1 and a compensation assembly 2, the shock absorbing pads 1 are disposed on the base 3, and the heads of the compensation assembly 2 are embedded into the shock absorbing pads 1.
The base 3 is the base used for installation of a large-scale machine, the large-scale machine is provided with a plurality of feet 9, the cushioning pad 1 is arranged between each foot 9 and the base 3 to isolate high-frequency low-amplitude vibration, and the compensation assembly 2 is arranged in the cushioning pad 1, so that when the feet 9 press the cushioning pad 1 downwards due to vibration to be larger, the feet 9 are jacked reversely, and the load of the cushioning pad 1 is reduced.
As shown in fig. 3 and 6, the compensation assembly 2 comprises a first pipe cylinder 21, a second pipe cylinder 22, an oil circulation assembly 23 and a feedback correction controller 24, and a vertical receiving hole 11 is formed on the surface of the shock pad 1 departing from the base 3;
the first tube cylinder 21 comprises a signal tube 211, a signal piston 212 and a pressure sensor 215, the signal tube 211 is arranged in the shock absorption pad 1, the bottom of the signal tube 211 is closed, the signal piston 212 is arranged in the signal tube 211 in an upward mode, the top end of the signal piston 212 is positioned in the accommodating hole 11, the top end of the signal piston 212 is lower than the upper surface of the shock absorption pad 1, the signal piston 212 is hooked by an annular limiting bulge on the inner surface of the signal tube 211, so that the signal piston 212 cannot be pushed out upwards infinitely due to the pressure in the signal tube 211 and can only reach the height position in fig. 3, the signal piston can only be pressed downwards during operation, at the moment, the top end of the position signal piston 212 is lower than the upper surface of the shock absorption pad 1, and the measuring point of the pressure sensor 215 is positioned on the inner side surface or the bottom of the signal tube 211;
the second pipe cylinder 22 comprises a pressure regulating pipe 221, a feedback piston 222, a pressure boosting pipe 223, a pressure relief pipe 224 and an electromagnetic valve 225, wherein the feedback piston 222 is arranged in the pressure regulating pipe 221 upwards, the top of the feedback piston 222 is positioned in the accommodating hole 11, the top end of the feedback piston 222 is flush with the top end of the signal piston 212, the feedback piston 222 is also hooked by an annular limiting bulge on the inner wall of the pressure regulating pipe 221, the feedback piston cannot move upwards infinitely and can only be pressed downwards, the inner side surface or the bottom of the pressure regulating pipe 221 is connected with the oil circulation assembly 23 through the pressure boosting pipe 223 and the pressure relief pipe 224, the flow direction of fluid in the pressure boosting pipe 223 is from the oil circulation assembly 23 to the pressure regulating pipe 221, the flow direction of fluid in the pressure relief pipe 224 is from the pressure regulating pipe 221 to the oil circulation assembly 23, and the pipelines of the pressure boosting pipe 223 and the pressure relief pipe 224 are both provided with the electromagnetic valve 225;
the solenoid valve 225 and the pressure sensor 215 are electrically connected to the feedback correction controller 24.
The flow principle of the compensating assembly 2 is shown in fig. 6, when the foot 9 is pressed down to the signal piston 212 and the feedback piston 222 due to the large vibration, the signal piston 212 and the feedback piston 222 are both pressed down, the pressure in the signal pipe 211 is increased, the pressure sensor 215 sends a signal to the feedback correction controller 24, the feedback correction controller 24 obtains a signal to control the electromagnetic valve 225 on the pressure-increasing pipe 223 to open, so as to introduce the high-pressure oil in the oil circulating assembly 23 into the pressure-adjusting pipe 221, the oil pressure in the pressure-adjusting pipe 221 is increased, the force of the feedback piston 222 reversely pushing against the foot 9 is larger until the pressure is counteracted, the pressing process of the foot 9 due to the large vibration is divided into two curves of pressing-down force increase and pressing-down force reduction, the oil pressure in the pressure-adjusting pipe 221 is increased in the pressing-down force increase link, and the oil pressure in the pressure-adjusting pipe 221 is removed through the pressure-releasing pipe 224 in the pressing-down force reduction link, so as to reach the compensating curve in fig. 8, if the oil pressure of the pressure regulating pipe 221 is regulated after the vibration occurs, the oil pressure appears to be delayed, so the feedback correction controller 24 is used for regulating the signals and the switching value of the electromagnetic valve 225 and the pressure sensor 215, thereby achieving the purpose of automatic control, the system block diagram of the automatic control is shown in fig. 9 and is a closed loop control system, the target value is the output quantity Y(s) of G4, G4 corresponds to the signal pipe 211 in the compensation assembly 2, Y(s) corresponds to the output value of the pressure sensor 215, R(s) is the original preset value of the pressure in the signal pipe 211, G1 corresponds to the feedback correction controller 24, the signal Y(s) from the pressure sensor 215 is compared with the preset value R(s) in the feedback correction controller 24 and is converted into the control signal of G2, G2 corresponds to the second pipe cylinder 22, the rise or fall of the oil pressure is controlled by G1, G2 is fed back to G3, G3 corresponds to foot 9, the vibration of the machine is loaded into the automatic control system as a disturbance factor N(s), and a mechanic in the automatic control field sets a specific transfer function parameter value in the feedback correction controller 24 according to the control logic and the block diagram, and the fluctuation of the vibration can be approximately regarded as sinusoidal change, so that the automatic control system is a second-order system, and according to the application occasion of the invention, additional expected conditions are as follows: the system allows larger steady-state error, but the overshoot is larger, and the rise time and the adjusting time are shorter.
In addition, since the self-controlled adjustment amount is in the pressure regulating pipe 221, and the target amount is in the signal pipe 211, the feedback piston 222 is blocked by a limit protrusion, so that the oil pressure in the pressure regulating pipe 221 can be continuously increased to the maximum oil pressure provided by the oil circulation component 23, and then when the vibration of the bottom foot 9 is resisted, the bottom foot 9 is kicked to an iron plate, rigid collision cannot play a role in buffering, therefore, if the oil pressure in the pressure regulator pipe 221 needs to be restored after each adjustment, in order to realize this characteristic, a separate self-control adjustment logic should be provided between G2/G4, after the adjustment of fig. 9 is realized, the pressure in G2/G4 is adjusted to the original ratio, the side of the pressure regulating pipe 221 also needs to be provided with a corresponding pressure sensor to be connected to the feedback correction controller 24, and the feedback correction controller 24 undertakes two-way self-control adjustment hinge. The priority of the automatic control regulation between G2/G4 is lower than that of the total regulation process, and the automatic control regulation of G2/G4 is started only after the total regulation process enters a steady state.
The conduction of oil pressure is rapid, and as a transmission medium of an automatic control system, the transmission speed requirement can be met by responding to the low-frequency high-amplitude vibration of the bottom foot 9.
As shown in fig. 1 and 6, the oil circulation unit 23 includes a high-pressure tank 231, a low-pressure tank 232, and a booster pump 233, the high-pressure tank 231 and the low-pressure tank 232 are connected by the booster pump 233 to boost the pressure of the fluid, the high-pressure tank 231 is connected to a booster pipe 223, and the low-pressure tank 232 is connected to a pressure relief pipe 224.
High-pressure oil and low-pressure oil are respectively stored in the high-pressure tank 231 and the low-pressure tank 232, and the oil which is led into the pressure regulating pipe 221 or is discharged from the pressure regulating pipe 221 is prepared at any time; the booster pump 233 maintains the operating pressures of the high-pressure tank 231 and the low-pressure tank 232.
As shown in fig. 6, the first pipe cylinder 21 further includes a pilot pipe 213 and a hand valve 214, the pilot pipe 213 has one end connected to the signal pipe 211 and the other end connected to an external pressure source, and the hand valve 214 is installed on the pilot pipe 213. The pilot line 213 and the hand valve 214 are used to initially set the pressure in the signal line 211 as a desired value r(s) in the autonomous system.
As shown in fig. 6, the hand valve 214 is a pressure-regulating hand valve with a pressure gauge. The hand valve 214 is opened to introduce pressure into the signal tube 211, and a pressure gauge is provided to facilitate on-site observation of the presence of a predetermined value that would otherwise be detected or preset from the introduction of the pressure source.
As shown in fig. 3 and 5, the signal tube 211 and the pressure regulating tube 221 are nested, the signal tube 211 is disposed at the upper part in the pressure regulating tube 221, the outer wall of the lower part of the signal tube 211 is mounted on the inner wall of the pressure regulating tube 221 through a bracket, the feedback piston 222 is annular, and the lower sealing ring of the feedback piston 222 is in contact with the outer wall of the signal tube 211 and the inner wall of the pressure regulating tube 221.
The annular feedback piston 222 and the signal piston 212 are concentrically arranged, the force applied by the foot 9 to the feedback piston and the signal piston is horizontally uniform, and the self-control precision is not influenced by deviation from the horizontal plane caused by different force applying positions.
As shown in fig. 1, 2, 4 and 6, the second cylinder 22 further includes a pressure-transfer piston 229, the lower end of the pressure-regulating tube 221 extends into the shock-absorbing pad 1 farthest away from the pressure-regulating tube 221, the lower end of the pressure-regulating tube 221 has a nozzle facing downward, and the pressure-transfer piston 229 is disposed at the lower end of the pressure-regulating tube 221 and contacts with the base 3. Unless the transfer function of the feedback correction controller 24 in the compensating block 2 is properly designed, the timing of the lead adjustment is very good, even if most of the vibration has been compensated for, a part of the vibration of the foot 9 that cannot be eliminated by the compensating block 2 is loaded on the pressure regulating tube 221, and the position of the rotary pressing piston 229 is set to guide the part of the force to the farthest position of the base 3, and generally, when one foot is pressed down, the foot 9 that is farthest away from the foot is lifted, and the pressure to the base 3 is small, and the rotary pressing piston 229 is in contact with the position, so that the position can provide a supporting force for the foot that is in high amplitude vibration, and the pressure is uniformly released to the base 3.
The solenoid valve 225 is a high speed solenoid valve. The response time of the high-speed electromagnetic valve is extremely short, the requirement of an automatic control system is met, and the lengthening of the automatic control adjusting time caused by hardware problems is eliminated as far as possible.
The feedback correction controller 24 is a PD or PID controller. The PD controller is a proportional-derivative controller, the lead correction performance of the PD controller is excellent, the system adjusting time is shortened, and the phase stability margin is excellent. The PID controller is a PID controller, which not only has the characteristics of a PD controller, but also has the characteristics of a PI controller that can improve the steady-state performance of the system, although the steady-state error in the steady-state performance is not a factor to be considered in the present invention.
The main using process of the invention is as follows: large-scale machine installs on base 3, set up bradyseism pad 1 and compensating assembly 2 between its footing 9 and the base 3, as shown in FIG. 7, bradyseism pad 1 eliminates low-amplitude high-frequency vibration, as shown in FIG. 8, and high-amplitude low-frequency vibration is crossing bradyseism pad 1 back, load on compensating assembly 2, compensating assembly 2 passes through the automatic control that the feedback was adjusted, provide the holding power of footing 9 with certain feedback curve, offset footing 9's vibration displacement, thereby reach and make machine 9's very big partial vibration eliminated, thereby can't lead to resonance to take place.
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.
Claims (1)
1. A vibration compensation-based resonance elimination device for a mainframe is characterized in that: the resonance elimination device comprises a base (3), a plurality of groups of shock absorption pads (1) and a compensation assembly (2), wherein the shock absorption pads (1) are arranged on the base (3), and the heads of the compensation assembly (2) are embedded into the shock absorption pads (1);
the compensation assembly (2) comprises a first pipe cylinder (21), a second pipe cylinder (22), an oil circulation assembly (23) and a feedback correction controller (24), and a vertical accommodating hole (11) is formed in the surface, deviating from the base (3), of the shock absorption pad (1);
the first pipe cylinder (21) comprises a signal pipe (211), a signal piston (212) and a pressure sensor (215), the signal pipe (211) is arranged in the cushioning pad (1), the bottom of the signal pipe (211) is closed, the signal piston (212) is arranged in the signal pipe (211) in an upward mode, the top end of the signal piston (212) is located in the accommodating hole (11), the top end of the signal piston (212) is lower than the upper surface of the cushioning pad (1), and a measuring point of the pressure sensor (215) is located on the inner side surface or the bottom of the signal pipe (211);
the second pipe cylinder (22) comprises a pressure regulating pipe (221), a feedback piston (222), a pressure boosting pipe (223), a pressure relief pipe (224) and an electromagnetic valve (225), wherein the feedback piston (222) is arranged in the pressure regulating pipe (221) upwards, the top of the feedback piston (222) is positioned in the accommodating hole (11), the top end of the feedback piston (222) is flush with the top end of the signal piston (212), the inner side surface or the bottom of the pressure regulating pipe (221) is connected with the oil circulation assembly (23) through the pressure boosting pipe (223) and the pressure relief pipe (224), the flowing direction of fluid in the pressure boosting pipe (223) is from the oil circulation assembly (23) to the pressure regulating pipe (221), the flowing direction of fluid in the pressure relief pipe (224) is from the pressure regulating pipe (221) to the oil circulation assembly (23), and the electromagnetic valves (225) are arranged on the pressure boosting pipe (223) and the pressure relief pipe (224);
the electromagnetic valve (225) and the pressure sensor (215) are electrically connected with the feedback correction controller (24);
the oil liquid circulation assembly (23) comprises a high-pressure tank (231), a low-pressure tank (232) and a booster pump (233), the high-pressure tank (231) and the low-pressure tank (232) are connected through the booster pump (233) to boost fluid, the high-pressure tank (231) is connected with a booster pipe (223), and the low-pressure tank (232) is connected with a pressure relief pipe (224);
the second pipe cylinder (22) further comprises a pressure transfer piston (229), the lower end of the pressure regulating pipe (221) extends into the shock absorption pad (1) which is farthest away from the pressure regulating pipe, the pipe orifice of the lower end of the pressure regulating pipe (221) faces downwards, and the pressure transfer piston (229) is arranged at the lower end of the pressure regulating pipe (221) and is in contact with the base (3); the solenoid valve (225) is a high-speed solenoid valve; the feedback correction controller (24) is a PD or PID controller.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010379873.3A CN111692264B (en) | 2019-09-20 | 2019-09-20 | Resonance eliminating device for mainframe based on vibration compensation |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910894052.0A CN110566629B (en) | 2019-09-20 | 2019-09-20 | Resonance eliminating device for mainframe based on vibration compensation |
| CN202010379873.3A CN111692264B (en) | 2019-09-20 | 2019-09-20 | Resonance eliminating device for mainframe based on vibration compensation |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910894052.0A Division CN110566629B (en) | 2019-09-20 | 2019-09-20 | Resonance eliminating device for mainframe based on vibration compensation |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111692264A CN111692264A (en) | 2020-09-22 |
| CN111692264B true CN111692264B (en) | 2021-08-03 |
Family
ID=68781531
Family Applications (3)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010379873.3A Active CN111692264B (en) | 2019-09-20 | 2019-09-20 | Resonance eliminating device for mainframe based on vibration compensation |
| CN202010384651.0A Active CN111692265B (en) | 2019-09-20 | 2019-09-20 | Resonance eliminating device for mainframe based on vibration compensation |
| CN201910894052.0A Active CN110566629B (en) | 2019-09-20 | 2019-09-20 | Resonance eliminating device for mainframe based on vibration compensation |
Family Applications After (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010384651.0A Active CN111692265B (en) | 2019-09-20 | 2019-09-20 | Resonance eliminating device for mainframe based on vibration compensation |
| CN201910894052.0A Active CN110566629B (en) | 2019-09-20 | 2019-09-20 | Resonance eliminating device for mainframe based on vibration compensation |
Country Status (1)
| Country | Link |
|---|---|
| CN (3) | CN111692264B (en) |
Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3073879B2 (en) * | 1994-03-25 | 2000-08-07 | キヤノン株式会社 | Anti-vibration device |
| WO2002006700A1 (en) * | 2000-07-13 | 2002-01-24 | Ebara Corporation | Vibration isolating device using magnetic levitating device |
| US20020104950A1 (en) * | 2000-11-27 | 2002-08-08 | Takehiko Mayama | Active vibration suppression apparatus, control method therefor, and exposure apparatus having active vibration suppression apparatus |
| TW535227B (en) * | 2000-02-09 | 2003-06-01 | Canon Kk | Active anti-vibration apparatus and exposure apparatus |
| US20060272910A1 (en) * | 2005-06-02 | 2006-12-07 | Emil Kraner | Systems and methods for active vibration damping |
| CN201013821Y (en) * | 2007-03-06 | 2008-01-30 | 中国船舶重工集团公司第七一一研究所 | Metallic rubber vibration damping bearing plate |
| CN101128694A (en) * | 2003-10-24 | 2008-02-20 | 纽波特公司 | Instrumented platform for vibration-sensitive equipment |
| CN102705431A (en) * | 2012-05-31 | 2012-10-03 | 中国科学院长春光学精密机械与物理研究所 | Angular-displacement-free active and passive combined vibration reduction system and method |
| CN103062285A (en) * | 2012-12-19 | 2013-04-24 | 哈尔滨工业大学 | Coplane air floatation orthogonal decoupling and flexible membrane angle decoupling zero-stiffness vibration isolator |
| CN103398138A (en) * | 2013-07-01 | 2013-11-20 | 西安交通大学 | Damping-rigidness-controllable double-freedom-degree vibration active control platform |
| CN204900659U (en) * | 2015-06-23 | 2015-12-23 | 嘉兴鸿利机械有限公司 | Section of jurisdiction is vibration isolation platform for production line |
| CN105972148A (en) * | 2016-07-15 | 2016-09-28 | 中国地震局地震研究所 | Ultralow-frequency vibration isolation device based on dual-spiral-spring system |
Family Cites Families (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DK116700A (en) * | 1963-07-12 | |||
| CH530573A (en) * | 1971-10-29 | 1972-11-15 | Lenco Ag | Arrangement for the vibration-free suspension of devices, in particular record players |
| FR2600137B1 (en) * | 1986-06-16 | 1990-06-22 | Pechiney Aluminium | PNEUMATIC SUSPENSION OF VIBRATORS USED IN PARTICULAR FOR THE PRODUCTION OF CARBON BLOCKS |
| JPH02278038A (en) * | 1989-04-20 | 1990-11-14 | Fuji Photo Film Co Ltd | Supporting structure of photo beam scanning mechanism |
| DK170999B1 (en) * | 1993-07-09 | 1996-04-15 | Smidth & Co As F L | Vibration compensator to counter vibration |
| CN2303123Y (en) * | 1997-05-22 | 1999-01-06 | 王水木 | Shock-absorbing and spring mat material |
| CN100392279C (en) * | 2004-07-28 | 2008-06-04 | 陈清欣 | Engine suspension soft pad assembly |
| CN2849317Y (en) * | 2005-11-09 | 2006-12-20 | 重庆宗申技术开发研究有限公司 | Shock absorption foot cushion |
| CN2913728Y (en) * | 2006-03-24 | 2007-06-20 | 舒和实业股份有限公司 | Vehicular air cushion with multiple functions |
| CN1963939A (en) * | 2006-12-08 | 2007-05-16 | 北京工业大学 | A quakeproof removable harddisk |
| CN101846150A (en) * | 2009-03-23 | 2010-09-29 | 韩芳 | Nonlinear damping composite rubber vibration attenuation pad |
| CN202023877U (en) * | 2011-05-09 | 2011-11-02 | 浙江正裕工业有限公司 | Compression valve seat in automobile vibration damper |
| CN202132437U (en) * | 2011-06-20 | 2012-02-01 | 隆昌山川精密焊管有限责任公司 | Compression valve of shock absorber for automobiles |
| JP2014009696A (en) * | 2012-06-27 | 2014-01-20 | Shinwa Giken:Kk | Seismic isolation member and seismic isolation device employing the same |
| FR2996892B1 (en) * | 2012-10-16 | 2015-11-06 | Technip France | DAMPING ASSEMBLY FOR AT LEAST PARTLY INSTALLED INSTALLATION IN A WATER EXTEND, ASSOCIATED INSTALLATION AND METHOD |
| CN204024542U (en) * | 2014-09-05 | 2014-12-17 | 王洪臣 | A kind of borehole pump safety valve pressure release flow path device |
| CN204879285U (en) * | 2015-07-11 | 2015-12-16 | 遂宁森帝汽配制造有限责任公司 | Engine mounting cushion device |
| DE102015214877A1 (en) * | 2015-08-04 | 2017-02-09 | Zf Friedrichshafen Ag | Method and device for enclosing damping medium and compensating medium in a vibration damper |
| CN105299127B (en) * | 2015-12-09 | 2017-04-26 | 上海康比利仪表有限公司 | Precise automatic damping-oil injection control device for instrument movements |
| CN206903830U (en) * | 2017-04-11 | 2018-01-19 | 浙江偌美装饰材料有限公司 | A kind of compressor of good damping effect |
| CN207634589U (en) * | 2017-11-21 | 2018-07-20 | 江苏蔚金汽车零部件有限公司 | A kind of lightweight suspension bags seat structure |
-
2019
- 2019-09-20 CN CN202010379873.3A patent/CN111692264B/en active Active
- 2019-09-20 CN CN202010384651.0A patent/CN111692265B/en active Active
- 2019-09-20 CN CN201910894052.0A patent/CN110566629B/en active Active
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3073879B2 (en) * | 1994-03-25 | 2000-08-07 | キヤノン株式会社 | Anti-vibration device |
| TW535227B (en) * | 2000-02-09 | 2003-06-01 | Canon Kk | Active anti-vibration apparatus and exposure apparatus |
| WO2002006700A1 (en) * | 2000-07-13 | 2002-01-24 | Ebara Corporation | Vibration isolating device using magnetic levitating device |
| US20020104950A1 (en) * | 2000-11-27 | 2002-08-08 | Takehiko Mayama | Active vibration suppression apparatus, control method therefor, and exposure apparatus having active vibration suppression apparatus |
| CN101128694A (en) * | 2003-10-24 | 2008-02-20 | 纽波特公司 | Instrumented platform for vibration-sensitive equipment |
| US20060272910A1 (en) * | 2005-06-02 | 2006-12-07 | Emil Kraner | Systems and methods for active vibration damping |
| CN201013821Y (en) * | 2007-03-06 | 2008-01-30 | 中国船舶重工集团公司第七一一研究所 | Metallic rubber vibration damping bearing plate |
| CN102705431A (en) * | 2012-05-31 | 2012-10-03 | 中国科学院长春光学精密机械与物理研究所 | Angular-displacement-free active and passive combined vibration reduction system and method |
| CN103062285A (en) * | 2012-12-19 | 2013-04-24 | 哈尔滨工业大学 | Coplane air floatation orthogonal decoupling and flexible membrane angle decoupling zero-stiffness vibration isolator |
| CN103398138A (en) * | 2013-07-01 | 2013-11-20 | 西安交通大学 | Damping-rigidness-controllable double-freedom-degree vibration active control platform |
| CN204900659U (en) * | 2015-06-23 | 2015-12-23 | 嘉兴鸿利机械有限公司 | Section of jurisdiction is vibration isolation platform for production line |
| CN105972148A (en) * | 2016-07-15 | 2016-09-28 | 中国地震局地震研究所 | Ultralow-frequency vibration isolation device based on dual-spiral-spring system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN110566629B (en) | 2020-06-26 |
| CN111692264A (en) | 2020-09-22 |
| CN111692265A (en) | 2020-09-22 |
| CN111692265B (en) | 2021-09-21 |
| CN110566629A (en) | 2019-12-13 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US20080031991A1 (en) | Injection mold for glass encapsulation | |
| CN101979173B (en) | Hydraulic straightening device | |
| CN102269235B (en) | Magneto-rheological fluid (MRF) damper based pressure fluctuation self-adjusting system and adjusting method | |
| JP6889240B2 (en) | Home appliances | |
| CN111692264B (en) | Resonance eliminating device for mainframe based on vibration compensation | |
| US20190292712A1 (en) | Support for household appliance, and household appliance | |
| CN202388179U (en) | Positioning device for welding | |
| US20200191320A1 (en) | Supporting and leveling device for household appliance, and household appliance | |
| CN211965944U (en) | Main spindle box hydraulic balance structure | |
| CN111485857B (en) | Single-double-cylinder wellhead type automatic reversing hydraulic pumping unit and hydraulic control method | |
| CN104005329B (en) | A kind of vibration source constant-pressure compensation system | |
| CN209425281U (en) | A kind of wedge-caulking device | |
| CN213452107U (en) | Synchronous adjustable sliding pipe carrier | |
| KR20120081818A (en) | Hydraulic shock absorbing tilting disc check valve | |
| CN219809513U (en) | Anti-seismic support structure for building pipeline installation | |
| CN201521511U (en) | Oil cylinder with semi-driving controllable buffer at tail end | |
| CN218261483U (en) | Adjustable elevator main machine vibration reduction combined structure | |
| CN211231115U (en) | Hydraulic cylinder of adjustable buffering dynamics | |
| CN218925991U (en) | Positioning reference device of pipe bending machine | |
| CN204041836U (en) | Bottom valve of shock absorber assembly | |
| CN106949175A (en) | A kind of floating clamp arrestment mechanism of slip | |
| CN219830220U (en) | Valve plate device is examined to helium | |
| CN204222236U (en) | Fluid pressure type rotating press device | |
| CN220435602U (en) | Supporting device for fixing throttle valve | |
| CN218177818U (en) | Buffer device for textile machinery |
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 | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20210716 Address after: Room 1208-15, building 1, No. 199, Shishan Road, high tech Zone, Suzhou, Jiangsu 215000 Applicant after: Suzhou wislem Intelligent Technology Co.,Ltd. Address before: 215000 No. 1, Linglong street, Suzhou Industrial Park, Jiangsu Province Applicant before: Pei Guanghua |
|
| TA01 | Transfer of patent application right | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |