CN210599669U - Ultrahigh-speed synchronous gas-liquid driving system - Google Patents
Ultrahigh-speed synchronous gas-liquid driving system Download PDFInfo
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- CN210599669U CN210599669U CN201921298322.3U CN201921298322U CN210599669U CN 210599669 U CN210599669 U CN 210599669U CN 201921298322 U CN201921298322 U CN 201921298322U CN 210599669 U CN210599669 U CN 210599669U
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Abstract
The utility model provides an ultra-high speed and ultra-high synchronous gas-liquid driving system, which comprises at least one same telescopic gas-liquid mixing cylinder, at least one mass block, a high-pressure gas source, an inflation valve and a controller; the same telescopic gas-liquid mixing cylinders are used for driving the mass blocks to move, and the number of the same telescopic gas-liquid mixing cylinders is the same as that of the mass blocks; the high-pressure gas source is connected with the telescopic gas-liquid mixing cylinder through a first gas path, and the inflation valve is arranged on the first gas path; the controller is connected with the inflation valve to control the inflation valve to act. The utility model discloses a spare part of easily designing and processing is built, can realize 60 ms's drive speed, can provide powerful support for internal explosion simulation work.
Description
Technical Field
The utility model belongs to the technical field of pneumatic drive and hydraulic drive, concretely relates to synchronous gas-liquid actuating system of hypervelocity superelevation.
Background
With the development of technology, fluid transmission technologies represented by pneumatic systems and hydraulic systems have become mature. The hydraulic system has the main advantages of high control precision, large energy density ratio and high response speed; the pneumatic system has the main advantages of cleanness, no pollution, small elastic modulus, good force output flexibility and difficult damage to a driving object. Therefore, the pneumatic-hydraulic driving system is widely applied to various scenes in which objects need to be driven at an ultra-high speed, for example, in an automobile crash test and a simulated explosion test.
Extreme loads from an explosion can have devastating consequences for the building, and if the damage to the support structure from the explosive load can result in the continued collapse of the entire building, more serious life and property damage will result. Therefore, from the aspects of experimental tests, analysis strategies, threat assessment tools and the like, it is very necessary to develop research work for predicting the damage mode and damage of the building supporting component under the action of explosive load. Engineers apply these strategies to new and existing structures, and also require digital tools and guidelines to assist in design. The field live-action test is the most reliable method of demonstrating the effectiveness or inadequacy of structural components in the event of an explosion. However, these types of tests are expensive and time consuming. Meanwhile, the control conditions required by explosive explosion are harsh, the environmental pollution is serious, the fireball generated instantaneously in explosion is not beneficial to data acquisition and interpretation, and high-quality data cannot be generated frequently due to the severe environment of an instrument and the variability of specified load, so that the method for acquiring research data in field tests has certain limitations.
How to simulate the extreme load generated by explosive explosion by using the prior art means becomes an important research subject. Aiming at the problem, the work of driving a load to impact a measured object by using an ultrahigh-speed and ultrahigh-synchronous driving system to simulate an explosion effect is carried out abroad. Wherein, the university of san Diego in America establishes a world first ultrahigh-speed ultrahigh-synchronous driving system. The system includes four high speed drives of identical construction. As shown in fig. 1, each high speed drive includes an integrated hydraulic valve, two accumulators, a displacement sensor, and a cylinder. When the system works, the hydraulic valve is opened quickly, and the energy accumulator injects a large amount of hydraulic oil into the accelerating cavity in a short time, so that the load is accelerated to a high speed in a short time. And nitrogen is remained in the speed reducing cavity, and when the piston rod moves leftwards, the speed reducing cavity is compressed, and the nitrogen is pressurized to buffer the movement. Four high-speed drivers can be used simultaneously in the system, each high-speed driver drives one mass block 2, and the four mass blocks 2 simultaneously impact the measured object. The maximum speed can reach 40m/s, the four high-speed drivers push the mass block 2 to pass through the same displacement, and the time difference of impacting the measured object does not exceed +/-1 ms. However, the conventional super-high speed and super-high speed synchronous driving system cannot increase the driving speed to more than 40m/s due to the restriction of the performance of the hydraulic valve, the accumulator and the oil cylinder. In addition, the oil cylinder is a single-stage oil cylinder, and after the relative speed of the cylinder barrel 11 and the piston is too high, the sealing element cannot bear, so that the further improvement of the driving speed is limited to a certain extent.
Disclosure of Invention
In order to overcome the problems in the related art at least to a certain extent, the utility model provides a superspeed ultrahigh-speed synchronous gas-liquid driving system.
According to an embodiment of the present invention, the present invention provides an ultra-high speed and ultra-high synchronous gas-liquid driving system, which comprises at least one homogeneous telescopic gas-liquid mixing cylinder, at least one mass block, a high pressure gas source, an inflation valve and a controller;
the same-telescopic gas-liquid mixing cylinders are used for driving the mass blocks to move so as to push the measured object, and the number of the same-telescopic gas-liquid mixing cylinders is the same as that of the mass blocks;
the high-pressure gas source is connected with the same telescopic gas-liquid mixing cylinder through a first gas path, and the inflation valve is arranged on the first gas path;
the controller is connected with the inflation valve to control the inflation valve to act.
The ultrahigh-speed ultrahigh-synchronous gas-liquid driving system further comprises a gas discharging cylinder and a gas discharging valve, wherein the gas discharging cylinder is connected with the gas-liquid mixing cylinder which is telescopic through a second gas path, and the gas discharging valve is arranged on the second gas path; the air release valve is connected with a controller, and the controller controls the air release valve to act.
In the ultrahigh-speed synchronous gas-liquid driving system, the gas-liquid mixing cylinder with the same expansion and contraction comprises a cylinder barrel, a first-stage cylinder body and a second-stage cylinder body; the first-stage cylinder body is vertically arranged in the cylinder barrel, and the top end of the first-stage cylinder body is positioned on the outer side of the cylinder barrel; the second-stage cylinder body is vertically arranged in the first-stage cylinder body, and the top end of the second-stage cylinder body is positioned on the outer side of the first-stage cylinder body;
the first-stage cylinder body comprises a cylinder bottom and a cylinder wall, and a space formed by the cylinder bottom and the lower part of the cylinder barrel is a first-stage positive cavity; the space formed by the cylinder bottom, the cylinder wall and the upper part of the cylinder barrel is a first-stage reverse cavity; hydraulic oil is pre-injected into the first-stage reverse cavity;
the first-stage cylinder body is in sealing contact with the cylinder barrel, and the second-stage cylinder body is in sealing contact with the first-stage cylinder body;
the second-stage cylinder body is of a structure with an inverted T-shaped longitudinal section, and a space formed by the bottom end of the second-stage cylinder body, the cylinder bottom and the lower part of the cylinder wall is a second-stage positive cavity; the space formed by the bottom end of the cylinder and the upper part of the cylinder wall is a second-stage reverse cavity; the second-stage reverse cavity is pre-filled with gas;
and an oil passing hole is formed in the position, close to the cylinder bottom, on the cylinder wall.
Furthermore, the side wall of the upper part of the cylinder barrel is also provided with an adjusting hole; the hydraulic oil source is connected with the adjusting hole through an oil way, and a hydraulic adjusting valve is arranged on the oil way.
Furthermore, a first sealing piece is arranged at the contact part of the cylinder barrel and the cylinder wall, and a second sealing piece is arranged at the contact part of the cylinder bottom and the inner wall of the cylinder barrel.
Furthermore, a third sealing element is arranged at the top end of the first-stage cylinder body and at the contact part of the upper parts of the first-stage cylinder body and the second-stage cylinder body; and a fourth sealing element is arranged at the contact part of the bottom end of the second-stage cylinder body and the cylinder wall.
Furthermore, an air charging and discharging port is arranged at the top of the first-stage cylinder body, and air is pre-charged into the second-stage reverse cavity through the air charging and discharging port.
The ultrahigh-speed ultrahigh-synchronous gas-liquid driving system further comprises a slow stopping device, wherein the slow stopping device comprises a pulley, a guide rail, a buffer oil cylinder and a one-way movement mechanism; the mass block is connected with the pulley, the pulley is arranged on the guide rail in a sliding mode, the buffer oil cylinder is arranged on the outer side of the guide rail, and a one-way movement mechanism is arranged at the joint of the pulley and the buffer oil cylinder.
The ultrahigh-speed ultrahigh-synchronization gas-liquid driving system further comprises a position sensor and a speed sensor, wherein the position sensor and the speed sensor are arranged inside the same-telescopic gas-liquid mixing cylinder and are respectively used for detecting the position and the speed of the same-telescopic gas-liquid mixing cylinder.
According to the above embodiments of the present invention, at least the following advantages are obtained: the utility model discloses through setting up inflation valve and high pressurized air source among the synchronous gas-liquid actuating system of hypervelocity superelevation, utilize high-pressure gas as drive medium, can show improvement drive speed. The utility model discloses the synchronous gas-liquid actuating system of hypervelocity superelevation adopts the spare part of easily designing and processing to build, can realize 60 ms's drive speed, can provide powerful support for internal explosion simulation work.
It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the invention, as claimed.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of the specification of the invention, illustrate embodiments of the invention and together with the description, serve to explain the principles of the invention.
Fig. 1 is a schematic diagram of a super high speed and super high synchronous drive system established at the university of san diego, usa in the prior art.
Fig. 2 is a schematic structural diagram of an ultrahigh-speed and ultrahigh-speed synchronous gas-liquid driving system according to an embodiment of the present invention.
Fig. 3 is a schematic structural diagram of a buffer device in an ultrahigh-speed and ultrahigh-synchronization gas-liquid driving system according to an embodiment of the present invention.
Fig. 4 is a schematic structural diagram of a one-way driving mechanism in the buffering device provided in fig. 3.
Fig. 5 is a schematic structural diagram of a simulation model of an ultrahigh-speed and ultrahigh-synchronization gas-liquid driving system according to an embodiment of the present invention.
Fig. 6 is a schematic structural diagram of a simulation model of a single co-telescopic gas-liquid mixing cylinder in the simulation model of the ultra-high-speed and ultra-high-speed synchronous gas-liquid driving system provided in fig. 5.
Fig. 7 is a simulation result diagram of the driving speed of the ultra-high speed and ultra-high synchronous gas-liquid driving system according to the embodiment of the present invention; wherein the abscissa represents time in units of s; the ordinate represents the speed in m/s.
Fig. 8 is a diagram showing a result of displacement simulation of a mass block in the ultra-high-speed and ultra-high-speed synchronous gas-liquid driving system according to the embodiment of the present invention; wherein the abscissa represents time in units of s; the ordinate represents the displacement in m.
Fig. 9 is a simulation result diagram of the driving speed when the length of a pipeline at one end of the same telescopic gas-liquid mixing cylinder in the ultra-high-speed and ultra-high-synchronization gas-liquid driving system provided by the embodiment of the present invention is biased; wherein the abscissa represents time in units of s; the ordinate represents the speed in m/s; a simulation curve of the driving speed when the length of the pipeline at one end of the same telescopic gas-liquid mixing cylinder is deviated is shown,
and represents the simulation curves of the driving speed when the lengths of the other three pipelines of the same telescopic gas-liquid mixing cylinder are not deviated.
Fig. 10 is a diagram showing a simulation result of displacement of a mass block when a length of a pipeline at one end of a same telescopic gas-liquid mixing cylinder in an ultra-high-speed and ultra-high-synchronization gas-liquid driving system according to an embodiment of the present invention is biased; wherein the abscissa represents time in units of s; the ordinate represents the displacement in m;
the simulation curve of the driving speed when the length of the pipeline at one end of the same telescopic gas-liquid mixing cylinder is deviated is shown, and the simulation curves of the driving speed when the lengths of the pipelines of the other three same telescopic gas-liquid mixing cylinders are not deviated are shown.
Fig. 11 is a simulation result diagram of the driving speed when the friction force and the pipeline length are biased together in the ultra-high-speed and ultra-high-synchronization gas-liquid driving system according to the embodiment of the present invention; wherein the abscissa represents time in units of s; the ordinate represents the speed in m/s; the simulation curve of the driving speed when the length of the pipeline at one end of the same telescopic gas-liquid mixing cylinder is deviated is shown, and the simulation curves of the driving speed when the lengths of the pipelines of the other three same telescopic gas-liquid mixing cylinders are not deviated are shown.
Fig. 12 is a graph showing a simulation result of the displacement of the mass block when the friction force and the length of the pipeline are biased together in the ultra-high-speed and ultra-high-synchronization gas-liquid driving system according to the embodiment of the present invention; wherein the abscissa represents time in units of s; the ordinate represents the displacement in m; the simulation curve of the driving speed when the length of the pipeline at one end of the same telescopic gas-liquid mixing cylinder is deviated is shown, and the simulation curves of the driving speed when the lengths of the pipelines of the other three same telescopic gas-liquid mixing cylinders are not deviated are shown.
Fig. 13 is a simulation result diagram of the driving speed when the friction force is pulled again in the ultra-high speed and ultra-high synchronous gas-liquid driving system according to the embodiment of the present invention; wherein the abscissa represents time in units of s; the ordinate represents the speed in m/s; a simulation curve showing the driving speed when the length of the pipeline at one end of the same telescopic gas-liquid mixing cylinder is deviated, and
-. represents the simulation curve of the driving speed when the lengths of the other three pipelines of the same telescopic gas-liquid mixing cylinder are not deviated.
Fig. 14 is a diagram showing a simulation result of the displacement of the mass block when the friction force is pulled again in the ultra-high-speed and ultra-high-synchronization gas-liquid driving system according to the embodiment of the present invention; wherein the abscissa represents time in units of s; the ordinate represents the displacement in m; a simulation curve showing the driving speed when the length of the pipeline at one end of the same telescopic gas-liquid mixing cylinder is deviated, and
-. represents the simulation curve of the driving speed when the lengths of the other three pipelines of the same telescopic gas-liquid mixing cylinder are not deviated.
Fig. 15 is a graph showing the simulation result of the displacement when a certain together telescopic gas-liquid mixing cylinder moves integrally in the ultra-high-speed and ultra-high-synchronization gas-liquid driving system according to the embodiment of the present invention; wherein the abscissa represents time in units of s; the ordinate represents the displacement in m; -represents a driving speed simulation curve when the length of a pipeline at one end of the same telescopic gas-liquid mixing cylinder is deviated, and,
The simulation curves of the driving speed when the lengths of the pipelines of the other three same telescopic gas-liquid mixing cylinders are not deviated are shown
Fig. 16 is a simulation result diagram of the driving speed during the pre-pressurization adjustment in the ultra-high speed and ultra-high synchronous gas-liquid driving system according to the embodiment of the present invention; wherein the abscissa represents time in units of s; the ordinate represents the speed in m/s; a simulation curve showing the driving speed when the length of the pipeline at one end of the same telescopic gas-liquid mixing cylinder is deviated, and
-. represents the simulation curve of the driving speed when the lengths of the other three pipelines of the same telescopic gas-liquid mixing cylinder are not deviated
Fig. 17 is a diagram showing a simulation result of displacement during pre-pressurization adjustment in the ultra-high speed and ultra-high synchronous gas-liquid driving system according to the embodiment of the present invention; wherein the abscissa represents time in units of s; the ordinate represents the displacement in m; the simulation curve of the driving speed when the length of the pipeline at one end of the same telescopic gas-liquid mixing cylinder is deviated is shown, and the simulation curves of the driving speed when the lengths of the pipelines of the other three same telescopic gas-liquid mixing cylinders are not deviated are shown.
Description of reference numerals:
1. a gas-liquid mixing cylinder which is telescopic;
11. a cylinder barrel; 111. an adjustment hole;
12. a first stage cylinder; 121. a cylinder bottom; 122. a cylinder wall; 123. a first stage positive cavity; 124. a first stage reverse cavity; 125. an air discharge port; 126. an oil passing hole;
13. a second stage cylinder; 131. a second-stage positive cavity; 132. a second stage reverse cavity;
2. a mass block;
3. a high pressure gas source; 31. a first gas path;
4. an inflation valve;
5. a gas discharge cylinder; 51. a second gas path;
6. a deflation valve;
7. a source of hydraulic oil; 71. an oil path;
8. a hydraulic pressure regulating valve;
9. a slow stop device; 91. a pulley; 92. a guide rail; 93. a buffer oil cylinder; 94. a unidirectional movement mechanism; 941. a pin; 942. a spring; 943. a handle; 944. and (4) limiting the step.
Detailed Description
To make the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the spirit of the present invention will be described in detail with reference to the accompanying drawings, and any person skilled in the art can change or modify the techniques taught by the present invention without departing from the spirit and scope of the present invention after understanding the embodiments of the present invention.
The exemplary embodiments and descriptions of the present invention are provided to explain the present invention, but not to limit the present invention. Additionally, the same or similar numbered elements/components used in the drawings and the embodiments are used to represent the same or similar parts.
As used herein, the terms "first," "second," …, etc. do not denote any order or sequential importance, nor are they used to limit the invention, but rather are used to distinguish one element from another or from another element or operation described in the same technical language.
With respect to directional terminology used herein, for example: up, down, left, right, front or rear, etc., are simply directions with reference to the drawings. Accordingly, the directional terminology used is intended to be illustrative and is not intended to be limiting of the present teachings.
As used herein, the terms "comprising," "including," "having," "containing," and the like are open-ended terms that mean including, but not limited to.
As used herein, "and/or" includes any and all combinations of the described items.
References to "plurality" herein include "two" and "more than two"; reference to "multiple sets" herein includes "two sets" and "more than two sets".
Certain words used to describe the invention are discussed below or elsewhere in this specification to provide additional guidance to those skilled in the art in describing the invention.
Fig. 2 is a schematic structural diagram of an ultrahigh-speed and ultrahigh-speed synchronous gas-liquid drive system provided by an embodiment of the present invention. As shown in fig. 2, the ultra-high speed and ultra-high speed synchronous gas-liquid driving system comprises at least one co-telescopic gas-liquid mixing cylinder 1, at least one mass block 2, a high-pressure gas source 3, an inflation valve 4, a deflation gas cylinder 5, a deflation valve 6 and a controller (not shown in the figure).
And the telescopic gas-liquid mixing cylinder 1 is used for driving the mass block 2 to move. The number of the same telescopic gas-liquid mixing cylinders 1 is the same as that of the mass blocks 2.
The high-pressure air source 3 is connected with the telescopic air-liquid mixing cylinder 1 through a first air path 31, and the inflation valve 4 is arranged on the first air path 31.
The deflation gas bottle 5 is connected with the telescopic gas-liquid mixing cylinder 1 through a second gas path 51, and the deflation valve 6 is arranged on the second gas path 51.
The controller is connected with the inflation valve 4 and the deflation valve 6 to control the inflation valve 4 and the deflation valve 6 to act.
In the explosion simulation working condition, one same-telescopic gas-liquid mixing cylinder 1 or a plurality of same-telescopic gas-liquid mixing cylinders 1 can be selected and used according to the volume of the measured object. In the automobile collision working condition, the requirement can be met by selectively using one same telescopic gas-liquid mixing cylinder 1.
Specifically, the co-telescopic gas-liquid mixing cylinder 1 includes a cylinder tube 11, a first-stage cylinder body 12, and a second-stage cylinder body 13. The first-stage cylinder 12 is vertically disposed in the cylinder 11, and the top end of the first-stage cylinder 12 is located outside the cylinder 11. The second-stage cylinder 13 is vertically disposed in the first-stage cylinder 12, and the top end of the second-stage cylinder 13 is located outside the first-stage cylinder 12.
The first-stage cylinder body 12 comprises a cylinder bottom 121 and a cylinder wall 122, and a space formed by the cylinder bottom 121 and the lower part of the cylinder barrel 11 is a first-stage positive cavity 123; the space formed by the cylinder bottom 121, the cylinder wall 122 and the upper part of the cylinder tube 11 is a first-stage reverse cavity 124. The first-stage reverse chamber 124 is pre-filled with hydraulic oil.
The first sealing member is arranged at the contact part of the cylinder tube 11 and the cylinder wall 122 at the top end of the cylinder tube 11. A second sealing member is provided at a contact portion of the cylinder bottom 121 and the inner wall of the cylinder tube 11.
The second-stage cylinder body 13 adopts a structure with an inverted T-shaped longitudinal section, and a space formed by the bottom end of the second-stage cylinder body, the cylinder bottom 121 and the lower part of the cylinder wall 122 is a second-stage positive cavity 131; the space formed by the bottom end and the upper portion of the cylinder wall 122 is the second-stage reverse chamber 132.
An air discharge port 125 is provided at the top of the first-stage cylinder 12, and the second-stage reverse chamber 132 can be preliminarily charged with air through the air discharge port 125. When the telescopic gas-liquid mixing cylinder 1 is operated, the air inlet/outlet port 125 is closed.
An oil passing hole 126 is formed in the cylinder wall 122 near the cylinder bottom 121. The oil passing hole 126 is arranged to facilitate the hydraulic oil in the first-stage reverse cavity 124 to enter the second-stage positive cavity 131 after being squeezed.
A third seal is provided at the top end of the first-stage cylinder 12, at the upper contact portion between the first-stage cylinder 12 and the second-stage cylinder 13. The contact part of the bottom end of the second-stage cylinder body 13 and the cylinder wall 122 is provided with a fourth sealing member.
The upper side wall of the cylinder 11 is also provided with an adjusting hole 111. The hydraulic oil source 7 is connected to the adjustment hole 111 through an oil passage 71, and the oil passage 71 is provided with a hydraulic pressure adjustment valve 8.
The utility model discloses synchronous gas-liquid actuating system work of hypervelocity superelevation is when no-load motion operating mode, and its working process is:
the controller controls the inflation valve 4 to be opened, the high-pressure air source 3 inflates air into the first-stage positive cavity 123 through the inflation valve 4, the first-stage positive cavity 123 is rapidly pressurized, and the first-stage cylinder body 12 and the second-stage cylinder body 13 synchronously and rapidly extend out.
After the preset time is reached, the controller controls the air release valve 6 to be opened, the first-stage positive cavity 123 releases air and releases pressure, and released air is collected through the air release air bottle 5.
The first-stage cylinder 12 and the second-stage cylinder 13 continue to extend under the inertia effect, and as the volume of the second-stage reverse chamber 132 becomes smaller, the pressure of the second-stage reverse chamber 132 becomes higher and lower, and the pressure of the first-stage positive chamber 123 becomes lower and higher.
After the first-stage cylinder 12 and the second-stage cylinder 13 are gradually decelerated to stop, the first-stage cylinder 12 and the second-stage cylinder 13 start moving in opposite directions, that is, in a direction toward the bottom of the cylinder 11.
The utility model discloses when hypervelocity superelevation synchronous gas-liquid actuating system promoted the load, its working process was:
and injecting a preset amount of hydraulic oil into the first-stage reverse cavity 124, presetting corresponding pressure for the second-stage reverse cavity 132, setting the action time sequence of the inflation valve 4 and the deflation valve 6, and setting the distance between the mass block 2 at the top end of the second-stage cylinder body 13 and the measured object.
The controller controls the inflation valve 4 to be opened, the high-pressure air source 3 inflates air into the first-stage positive cavity 123 through the inflation valve 4, and the first-stage cylinder body 12 and the second-stage cylinder body 13 synchronously and quickly extend out.
When the first-stage cylinder block 12 moves in a direction away from the bottom of the cylinder tube 11, the hydraulic oil in the first-stage reverse chamber 124 is compressed and is pressed into the second-stage positive chamber 131 through the oil passage hole 126 to drive the second-stage cylinder block 13 to move.
After the preset time is reached, the controller controls the air release valve 6 to be opened, and the first-stage positive cavity 123 releases air and releases pressure.
The gas in the second-stage reverse chamber 132 is compressed and the pressure in the second-stage reverse chamber 132 increases.
After the first-stage positive cavity 123 is vented, the pressure in the first-stage positive cavity 123 decreases. After the pressure of the second-stage reverse chamber 132 is equal to the pressure of the first-stage positive chamber 123, the first-stage cylinder 12 and the second-stage cylinder 13 start decelerating until the speed in the direction away from the bottom of the cylinder 11 decreases to 0, and then the first-stage cylinder 12 and the second-stage cylinder 13 start moving in the direction toward the bottom of the cylinder 11.
In order to avoid damage caused by the collision of the first-stage cylinder 12 and the second-stage cylinder 13, which recover at high speed, against the cylinder 11 or the collision between the first-stage cylinder 12 and the second-stage cylinder 13, a slow stop device 9 is provided for the second-stage cylinder 13 and the mass 2, which recover at high speed.
The slow stop device 9 can take various forms according to the actual space, speed and number of the same telescopic gas-liquid mixing cylinders 1. In the present embodiment, as shown in fig. 3, the slow stop device 9 includes a trolley 91, a guide rail 92, a cushion cylinder 93, and a one-way movement mechanism 94. The mass block 2 is connected with a pulley 91, the pulley 91 is slidably disposed on a guide rail 92, a buffer cylinder 93 is disposed outside the guide rail 92, and a one-way movement mechanism 94 is disposed at a connection position of the pulley 91 and the buffer cylinder 93.
As shown in fig. 4, the unidirectional movement mechanism 94 includes a housing (not shown), a pin 941, a spring 942, and a handle 943. The trolley 91 is fixedly connected with the housing. When the second stage cylinder 13 extends outward, the housing drives the pin 941 in a direction away from the bottom end of the cylinder 11; when the pin 941 is extended by the spring 942 when it passes over the stop 944, the carriage 91 can still move away from the bottom end of the cylinder 11. When the pulley 91 moves towards the direction close to the bottom of the cylinder 11 and moves to the stopping step 944, the extended pin 941 pushes the piston rod of the buffer cylinder 93 to retract, and the mass block 2 is gradually stopped under the action of the oil pressure of the positive cavity of the buffer cylinder 93.
In the above embodiment, the utility model discloses still include position sensor and speedtransmitter among the super high speed super high-speed synchronous gas-liquid actuating system, wherein, position sensor and speedtransmitter all set up in the inside with flexible gas-liquid mixing jar 1, are used for detecting position and speed with flexible gas-liquid mixing jar 1 respectively.
When the ultrahigh-speed ultrahigh-synchronization gas-liquid driving system comprises more than two same telescopic gas-liquid mixing cylinders 1 and the more than two same telescopic gas-liquid mixing cylinders 1 move simultaneously, if the positions of the same telescopic gas-liquid mixing cylinders 1 detected by the position sensors are greatly inconsistent, the hydraulic regulating valve 8 can be opened, and the hydraulic oil source 7 injects hydraulic oil into the first-stage reverse cavity 124 or discharges the hydraulic oil from the first-stage reverse cavity 124 through the hydraulic regulating valve 8 to regulate the relative speed or the initial position of the second-stage cylinder body 13, so that the absolute speed of the second-stage cylinder body 13 is regulated, and the purpose of synchronizing the same telescopic gas-liquid mixing cylinders 1 is ensured.
In addition, the synchronization of the telescopic gas-liquid mixing cylinders 1 can be ensured by adjusting the preset pressure of the second-stage reverse cavity 132.
The top end of the second stage cylinder 13 can be connected to different loads in a variety of ways to achieve drive as required by the load. The synchronous driving of a plurality of loads can be realized, and the high-speed driving of a single load can also be realized. The load pushed by the top end of the second-stage cylinder body 13 in the telescopic gas-liquid mixing cylinder 1 can be connected with the second-stage cylinder body 13 all the time, and can also be separated from the second-stage cylinder body 13 after reaching a certain speed. Different connecting modes are set corresponding to different working conditions, and different supporting modes can be selected for the load.
In the above embodiments, the controller is a commercially available high performance controller, which has the functions of driving the valve, collecting signals, and storing a control program. The controller is connected with the inflation valve 4, the deflation valve 6, the pressure sensor, the position sensor and the like through cables, is responsible for sending opening or closing signals to the inflation valve 4 and the deflation valve 6 and collecting signals of pressure, position, speed and the like in the system so as to be used for system state detection and data analysis.
The driving medium of the ultra-high speed and ultra-high speed synchronous gas-liquid driving system in the prior art shown in fig. 1 is hydraulic oil, and when the hydraulic oil flows through the hydraulic valve, huge hydraulic power is generated, which limits the opening speed of the hydraulic valve. The limited opening speed of the hydraulic valve can cause that hydraulic oil can not enter the accelerating cavity in as short time as possible, and the oil cylinder can not reach the required driving speed in limited formation. The maximum opening speed of the hydraulic valve which can meet the flow requirement at present is more than 20ms, and the opening speed of the hydraulic valve is required to reach 10ms when the speed of a load is required to reach 60m/s, which is difficult to realize by utilizing the prior art.
The utility model discloses synchronous gas-liquid actuating system of hypervelocity superelevation is through setting up inflation valve 4 and high pressurized air source 3, and the drive medium is high pressure gas, and there is not similar hydrodynamic force in the opening process of inflation valve 4 simultaneously, and drive air valve case motion can be thought to be at drive inertial load, and the opening speed of pneumatic valve accomplishes 10ms very easily and opens entirely.
The oil cylinder in the ultra-high speed and ultra-high speed synchronous gas-liquid driving system in the prior art shown in fig. 1 is a single-stage cylinder, if the speed of the load reaches 60m/s, the friction speed borne by the sealing element is 60m/s, while the maximum speed that the existing sealing element can bear is 15m/s, and the bearing capacity of the sealing element also limits the further improvement of the driving speed of the prior ultra-high speed and ultra-high speed synchronous gas-liquid driving system.
The power source of the ultra-high speed and ultra-high synchronous gas-liquid driving system in the prior art shown in fig. 1 is high-pressure gas in an accumulator. When the air valve is opened, the high-pressure gas pushes the piston to move, and the piston extrudes the hydraulic oil to quickly flow to the accelerating cavity of the cylinder. The gas chamber of the accumulator is filled slowly and for a long time, i.e. before the accumulator actually works, it is required that the sealing is very good, otherwise the gas in the gas chamber is liable to leak into the liquid chamber through the sealing. However, when the high pressure gas drives the piston to move rapidly, the piston is required to move flexibly, and the resistance caused by the sealing element is required to be as small as possible. The sealing element has to be well sealed and flexible to move, which are conflicting requirements and difficult to realize. And meanwhile, the moving speed of the piston is far beyond 15m/s, and a proper dynamic sealing element is difficult to find.
And in the utility model discloses among the synchronous gas-liquid actuating system of hypervelocity superelevation, the power supply is gas cylinder, and it is the steel structure, does not have the dynamic seal, realizes very easily.
To sum up, adopt the utility model discloses synchronous gas-liquid actuating system of hypervelocity superelevation can show and improve the drive speed.
Based on the synchronous gas-liquid actuating system of hypervelocity superelevation more than, the utility model also provides a synchronous gas-liquid actuating method of hypervelocity superelevation, it includes following step:
and constructing and operating a simulation model of the ultrahigh-speed ultrahigh-synchronous gas-liquid driving system to obtain a simulation result meeting the requirement.
And setting parameters of each component in the ultrahigh-speed ultrahigh-synchronous gas-liquid driving system according to the parameters of each component model in the simulation model corresponding to the simulation result.
According to the simulation result, a preset amount of hydraulic oil is injected into the first-stage reverse cavity 124, corresponding pressure is preset for the second-stage reverse cavity 132, the action time sequence of the inflation valve 4 and the deflation valve 6 is set, and the distance between the mass block 2 at the top end of the second-stage cylinder body 13 and the object to be measured is set.
The controller controls the inflation valve 4 to be opened, the high-pressure air source 3 inflates air into the first-stage positive cavity 123 through the inflation valve 4, the first-stage cylinder body 12 and the second-stage cylinder body 13 synchronously extend out in the direction far away from the bottom of the cylinder barrel 11, and the second-stage cylinder body 13 pushes a measured object through the mass block 2.
After the preset time is reached, the controller controls the air release valve 6 to be opened, the first-stage positive cavity 123 releases air and releases pressure, and the first-stage cylinder body 12 and the second-stage cylinder body 13 move towards the direction close to the bottom of the cylinder barrel 11 until the movement is stopped. Of course, according to different speed requirements, the air release valve can be kept not to be opened all the time by setting the pressure and the volume of the high-pressure air source.
The following describes the ultra-high speed and ultra-high synchronous gas-liquid driving method according to the present invention in detail by using specific embodiments.
As shown in fig. 5 and 6, a simulation model of the ultra-high-speed and ultra-high-speed synchronous gas-liquid driving system is constructed, wherein the ultra-high-speed and ultra-high-speed synchronous gas-liquid driving system comprises four co-telescopic gas-liquid mixing cylinders 1. The four same-telescopic gas-liquid mixing cylinders 1 share the same inflation valve 4, high-pressure gas source 3, air release valve 6 and air release cylinder 5.
In this simulation model, the high-pressure gas source 3 was set to 30L at 25 MPa. The pre-charging pressure of the second-stage reverse cavity 132 in the same telescopic gas-liquid mixing cylinder 1 is 10 MPa.
The inflation valve 4 starts to actuate at time zero and opens fully within 10 ms. The purge valve 6 is actuated at 15ms and fully opened within 10 ms.
And operating the simulation model of the ultra-high-speed and ultra-high-synchronization gas-liquid driving system constructed as described above to obtain a driving speed simulation result diagram shown in fig. 7 and a mass block 2 displacement simulation result diagram shown in fig. 8. As shown in FIG. 7, the driving speed curves of the four telescopic gas-liquid mixing cylinders 1 completely coincide with each other, and at 0.023s, the driving speeds of the four telescopic gas-liquid mixing cylinders can reach 60 m/s. As shown in fig. 8, the displacement curves of the four masses 2 connected to the telescopic gas-liquid mixing cylinder 1 are also completely overlapped, and at 0.037s, the positions of the four masses 2 are all at 1.370m, so that the synchronicity of the masses 2 is very good, and the masses start to move in reverse within a designed stroke of 1.6 m.
The length of a section of pipeline of the same telescopic gas-liquid mixing cylinder 1 is increased from 1m to 3m, the length of a section of pipeline of the other same telescopic gas-liquid mixing cylinder 1 is kept unchanged at 1m, and simulation results are shown in fig. 9 and 10, so that the influence of the change of the length of the pipeline on the simulation result of the ultrahigh-speed ultrahigh-synchronous gas-liquid driving system is small. After moving in the opposite direction to the first-stage cylinder body 12 and the second-stage cylinder body 13 in the telescopic gas-liquid mixing cylinder 1, the speed and position deviation starts to become slightly larger. However, when the first-stage cylinder 12 and the second-stage cylinder 13 move in opposite directions, the pushing of the object to be measured is completed, and therefore, there is no influence.
The coefficient of kinetic friction of the first-stage cylinder body 12 of the telescopic gas-liquid mixing cylinder 1 with the increased length of one pipeline is increased from 50N/(m/s) to 500N/(m/s). As shown in fig. 11 and 12, significant inconsistencies occurred in both velocity and displacement, with a maximum velocity of about 58m/s and a maximum velocity difference of about 2.4 m/s. The difference in displacement is about 28mm when the displacement reaches a maximum. As can be seen from fig. 11 and 12, the time at which the velocity reaches the maximum value is 0.023s, and the time at which the displacement reaches the maximum value is 0.037 s. The displacement difference of the four same telescopic gas-liquid mixing cylinders 1 at the time of 0.023s is obviously smaller than 28mm, the speed is about 58m/s at the time, the speed makes up the unique difference of 28mm, only 0.48ms is needed, and therefore, under the condition of the deviation, the synchronism of the multiple same telescopic gas-liquid mixing cylinders 1 is still very good.
On the basis of the simulations shown in fig. 11 and 12, the coefficient of kinetic friction of the second-stage cylinder block 13 of the telescopic gas-liquid mixing cylinder 1, in which the length of one pipe is increased, is also increased from 50N/(m/s) to 500N/(m/s). As shown in fig. 13 and 14, there is a clear difference in both velocity and displacement curves. The speed maxima differ by about 6 m/s. The displacement maxima differ by approximately 80 ms. When the speed reaches the maximum value, the displacement difference is about 50mm, the speed of the slower same telescopic gas-liquid mixing cylinder 1 is 53m/s, and the time for the same telescopic gas-liquid mixing cylinder 1 to compensate the 50mm displacement difference is 0.94ms, which is close to 1 ms.
On the basis of the simulation of fig. 13 and 14, the length of one section of pipeline is increased, and the length of the same telescopic gas-liquid mixing cylinder 1 is moved forward by 53mm integrally, and as can be seen from fig. 15, the four same telescopic gas-liquid mixing cylinders 1 can be ensured to reach the same position at 0.023s, namely 0.771 m-0.775 m simultaneously.
On the basis of the simulation arrangement of fig. 15, the pre-charging pressure of the second-stage reverse cavity 132 of the same telescopic gas-liquid mixing cylinder 1 with the length of one section of pipeline increased is reduced from 10MPa to 8MPa, and the pre-charging pressure of the second-stage reverse cavities 132 of the other three same telescopic gas-liquid mixing cylinders 1 is still kept at 10 MPa. As shown in fig. 16 and 17, when the speed reaches the maximum, the displacement difference between the four pieces of the telescopic gas-liquid mixing cylinder 1 is very small and is within 10 mm.
Therefore, no matter the integral movement is the same as the telescopic gas-liquid mixing cylinder 1, or the pre-stamping of the second-stage reverse cavity 132 is adjusted, the position difference of the four same telescopic gas-liquid mixing cylinders 1 when the speed is maximum can be effectively adjusted.
The utility model discloses hypervelocity super high-speed synchronous gas-liquid actuating system adopts the spare part of easily designing and processing to build, can realize 60 ms's driving speed, has surpassed the highest level on the present international, can provide powerful support for internal explosion simulation work.
The foregoing is only an illustrative embodiment of the present invention, and any equivalent changes and modifications made by those skilled in the art without departing from the spirit and principles of the present invention should fall within the protection scope of the present invention.
Claims (9)
1. The ultrahigh-speed synchronous gas-liquid driving system is characterized by comprising at least one co-telescopic gas-liquid mixing cylinder, at least one mass block, a high-pressure gas source, an inflation valve and a controller;
the same-telescopic gas-liquid mixing cylinders are used for driving the mass blocks to move so as to push the measured object, and the number of the same-telescopic gas-liquid mixing cylinders is the same as that of the mass blocks;
the high-pressure gas source is connected with the same telescopic gas-liquid mixing cylinder through a first gas path, and the inflation valve is arranged on the first gas path;
the controller is connected with the inflation valve to control the inflation valve to act.
2. The ultra-high-speed and ultra-high-speed synchronous gas-liquid driving system according to claim 1, further comprising a gas discharge cylinder and a gas discharge valve, wherein the gas discharge cylinder is connected with the gas-liquid mixing cylinder through a second gas path, and the gas discharge valve is arranged on the second gas path; the air release valve is connected with a controller, and the controller controls the air release valve to act.
3. The ultra-high speed and ultra-high speed synchronous gas-liquid driving system according to claim 1, wherein the co-telescopic gas-liquid mixing cylinder comprises a cylinder barrel, a first-stage cylinder body and a second-stage cylinder body; the first-stage cylinder body is vertically arranged in the cylinder barrel, and the top end of the first-stage cylinder body is positioned on the outer side of the cylinder barrel; the second-stage cylinder body is vertically arranged in the first-stage cylinder body, and the top end of the second-stage cylinder body is positioned on the outer side of the first-stage cylinder body;
the first-stage cylinder body comprises a cylinder bottom and a cylinder wall, and a space formed by the cylinder bottom and the lower part of the cylinder barrel is a first-stage positive cavity; the space formed by the cylinder bottom, the cylinder wall and the upper part of the cylinder barrel is a first-stage reverse cavity; hydraulic oil is pre-injected into the first-stage reverse cavity;
the first-stage cylinder body is in sealing contact with the cylinder barrel, and the second-stage cylinder body is in sealing contact with the first-stage cylinder body;
the second-stage cylinder body is of a structure with an inverted T-shaped longitudinal section, and a space formed by the bottom end of the second-stage cylinder body, the cylinder bottom and the lower part of the cylinder wall is a second-stage positive cavity; the space formed by the bottom end of the cylinder and the upper part of the cylinder wall is a second-stage reverse cavity; the second-stage reverse cavity is pre-filled with gas;
and an oil passing hole is formed in the position, close to the cylinder bottom, on the cylinder wall.
4. The ultra-high speed and ultra-high speed synchronous gas-liquid driving system as claimed in claim 3, wherein the upper side wall of the cylinder barrel is further provided with an adjusting hole; the hydraulic oil source is connected with the adjusting hole through an oil way, and a hydraulic adjusting valve is arranged on the oil way.
5. The ultra-high speed and ultra-high speed synchronous gas-liquid driving system as claimed in claim 3, wherein a first sealing member is arranged at the contact part of the cylinder barrel and the cylinder wall, and a second sealing member is arranged at the contact part of the cylinder bottom and the inner wall of the cylinder barrel.
6. The ultra-high-speed and ultra-high-speed synchronous gas-liquid driving system as claimed in claim 3, wherein a third sealing member is arranged at the top end of the first-stage cylinder body and at the contact part of the upper parts of the first-stage cylinder body and the second-stage cylinder body; and a fourth sealing element is arranged at the contact part of the bottom end of the second-stage cylinder body and the cylinder wall.
7. The ultra-high speed and ultra-high speed synchronous gas-liquid driving system according to claim 3, wherein an air charging and discharging port is arranged at the top of the first-stage cylinder body, and gas is pre-charged into the second-stage reverse cavity through the air charging and discharging port.
8. The ultra-high-speed and ultra-high-speed synchronous gas-liquid driving system according to any one of claims 1 to 7, further comprising a slow stop device, wherein the slow stop device comprises a pulley, a guide rail, a buffer oil cylinder and a one-way movement mechanism; the mass block is connected with the pulley, the pulley is arranged on the guide rail in a sliding mode, the buffer oil cylinder is arranged on the outer side of the guide rail, and a one-way movement mechanism is arranged at the joint of the pulley and the buffer oil cylinder.
9. The ultra-high speed and ultra-high speed synchronous gas-liquid driving system according to any one of claims 1 to 7, further comprising a position sensor and a speed sensor, wherein the position sensor and the speed sensor are both arranged inside the co-telescopic gas-liquid mixing cylinder and are respectively used for detecting the position and the speed of the co-telescopic gas-liquid mixing cylinder.
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110439880A (en) * | 2019-08-12 | 2019-11-12 | 北京坤飞航天科技有限公司 | The synchronous gas-liquid driving system of ultrahigh speed superelevation and gas-liquid driving method |
| CN112285113A (en) * | 2020-09-28 | 2021-01-29 | 维信诺科技股份有限公司 | Macroscopic defect inspection machine |
| CN116658491A (en) * | 2023-07-27 | 2023-08-29 | 湖南协力液压有限公司 | Low-impact hydraulic cylinder dynamic control method and system based on fluid resistance optimization |
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2019
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110439880A (en) * | 2019-08-12 | 2019-11-12 | 北京坤飞航天科技有限公司 | The synchronous gas-liquid driving system of ultrahigh speed superelevation and gas-liquid driving method |
| CN112285113A (en) * | 2020-09-28 | 2021-01-29 | 维信诺科技股份有限公司 | Macroscopic defect inspection machine |
| CN116658491A (en) * | 2023-07-27 | 2023-08-29 | 湖南协力液压有限公司 | Low-impact hydraulic cylinder dynamic control method and system based on fluid resistance optimization |
| CN116658491B (en) * | 2023-07-27 | 2023-09-22 | 湖南协力液压有限公司 | Low-impact hydraulic cylinder dynamic control method and system based on fluid resistance optimization |
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