A pneumatically-based piston-type controllable high-speed vortex ring generator

Abstract

The present invention discloses a pneumatic-based piston-type controllable high-speed vortex ring generator, which relates to the technical field of fluid mechanics. The present invention provides a high-speed and precisely controllable vortex ring generator for experimental research on high-speed vortex rings, and solves the problem that the existing controllable piston-type vortex ring generator has a small speed and cannot meet the requirements of high-speed vortex ring experimental research. The high-speed vortex ring generator of the present invention includes a compressor, a gas storage tank, various valves, pipelines, a speed reduction mechanism, a piston, an angular velocity sensor, and a single-chip microcomputer. The present invention is used for experimental research on high-speed vortex rings.

Description

Technical Field

[0001] The present invention relates to a pneumatic piston - type controllable high - speed vortex ring generator, belonging to the technical field of fluid mechanics. Background Art

[0002] Existing vortex ring generating devices: 1. In CN 104149956A, "A piston oscillator turbulent - flow - type bionic vortex ring generator", the vortex ring is mainly generated by a motor directly driving a mechanical device to energize the air flow in the cavity. Since it generates bionic vortex rings, the generated vortex rings have a very low speed.

[0003] 2. In CN 106423698 B, "An atomizing jet method and device based on a vortex ring structure", a vortex ring is generated by a compressed gas driving a piston. Since this device is a fixed - stroke and fixed - pressure vortex ring generator, it cannot control the speed of the piston, can only give the piston a fixed initial speed and the corresponding speed curve is single and cannot be changed, and the generated vortex ring speed is also relatively slow.

[0004] 3. In CN 112081798 A, "A vortex ring generator based on centrifugal force and electromagnetic ejection", a piston is driven by electromagnetic ejection to energize the air flow in the pipeline to generate a vortex ring. Due to structural limitations, this device cannot generate high - speed vortex rings.

[0005] The above three vortex ring generators are all used to generate low - speed vortex rings and are mainly applied in low - speed environments, so they cannot be used to generate high - speed vortex rings. Moreover, the above devices cannot accurately control the speed of the piston, can only give the vortex ring an initial speed and acceleration, and the subsequent speed cannot be adjusted, which obviously cannot meet the research requirements of vortex ring experiments. Finally, the pistons in the above three devices all move in a reciprocating motion, which is not allowed in experiments because the reciprocating motion will interfere with the generation of vortex rings and thus affect the experiment. Summary of the Invention

[0006] The technical problems to be solved by the present invention are: 1. How to provide sufficient kinetic energy for the piston. 2. How to accurately control the speed of the piston. 3. How to provide resistance to the moving piston without causing the piston to move reciprocally or suck back.

[0007] In view of the above - mentioned technical problems, the present invention provides a pneumatic piston - type high - speed vortex ring generator, which can be applied to the generation of high - speed vortex rings, and to a certain extent solves the problem that pneumatic devices are difficult to control, can accurately control the piston speed, and provides a reliable experimental device for the experimental research of high - speed vortex rings.

[0008] The technical solution adopted by the present invention to solve the above technical problems: A pneumatic piston-type controllable high-speed vortex ring generator, characterized in that it includes a nozzle pipe, a piston, a deceleration mechanism, a transition pipe, a three-way connecting pipe, a quick pressure relief valve, a quick switch valve, a pressure reducing valve, a main valve, an air storage tank, a compressor, and a control cabinet composed of a single-chip microcomputer; all the above valves and pipelines are connected by flange plates and bolts; the nozzle pipe includes installation positioning holes; the deceleration mechanism includes a deceleration mechanism housing and a deceleration device; the deceleration mechanism housing includes holes, a motor installation hole, and a data line outlet hole; the deceleration device is composed of a torque motor group, a transmission gear group, a resistance clamping structure group, a steering connection group, a stepping motor group, and a rotary transmission group; the holes are symmetrically present on the inner wall of the nozzle and the deceleration mechanism housing, where the hole is a single-step hole and the holes are all double-step holes; the torque motor group includes a torque motor and a gear, the bottom of the torque motor is fixed on the inner wall of the deceleration mechanism housing by means of screw connection, and the rotating shaft of the torque motor is fixed to the gear.

[0009] The stepping motor group includes a stepping motor and a sprocket, the bottom of the stepping motor is fixed on the inner wall of the deceleration mechanism housing by means of screw connection, and the rotating shaft of the stepping motor is fixed to the single-row sprocket.

[0010] The torque motor group, the transmission gear group, and the resistance clamping structure group are driven by gear cooperation, and the steering connection group, the rotary transmission group, and the stepping motor are all driven by chain and sprocket cooperation.

[0011] The cooperation of the parts in the transmission gear group and the resistance clamping structure group is symmetrical.

[0012] The quick pressure relief valve, the quick switch valve, the torque motor group, and the stepping motor group are all controlled by the single-chip microcomputer.

[0013] The transmission gear group includes a transmission shaft, two gears, two sleeves, two bearings, and two bearing washers; the bearing washers and the bearings are fixed at the holes on the inner wall of the deceleration mechanism housing by interference fit, and the bearing washers are located between the bearings and the holes; thus, the outer ring of the bearing is fixed and the inner ring can rotate around the shaft; the inner ring of the bearing is fitted with the first step of the transmission shaft; the sleeves and the second step of the transmission shaft fix the gears and can rotate with the inner ring of the bearing.

[0014] The resistance clamping structure group includes two bearing shims, two bearings, two transmission gear sleeves, two transmission intermediate sleeves, two friction sleeves, two lubricating bushings, a double-row sprocket, a sprocket shaft, and a sprocket bearing; the sprocket shaft is fixed at the bottom of the inner wall hole of the nozzle by interference fit; one end of the lubricating bushing abuts against the step of the middle hole of the nozzle, and the other end abuts against the inner ring of the sprocket bearing. After the lubricating bushing is sleeved on the sprocket shaft, it needs to be welded so that the bushing and the shaft are fixed as one body. Another lubricating bushing fixes the inner ring of the sprocket bearing by symmetric cooperation in the same way; both the bearing shims and the bearings are fixed at the step of the inner wall hole of the nozzle by interference fit. The bearing shims are located between the sprocket shaft and the hole step, which makes the outer ring of the bearing fixed while the inner ring can rotate around the sprocket shaft; the concave part of the double-row sprocket cooperates with the convex part on the sprocket bearing to fix the outer ring of the sprocket bearing to the double-row sprocket, enabling the double-row sprocket to rotate around the axis; the convex part of the lubricating bushing cooperates with the concave part of the transmission gear sleeve, allowing the transmission gear sleeve to make an axial linear movement on the lubricating bushing; the internal thread of the transmission gear sleeve rotates and mates with the external thread of the transmission intermediate sleeve; the convex side of the transmission gear sleeve abuts against the inner ring of the sprocket bearing, enabling the transmission gear sleeve to rotate around the shaft together with the inner ring of the sprocket bearing.

[0015] The steering connection group includes a sleeve, a wire reel, a connecting bearing, a single-row sprocket, and a transmission shaft; the second step of the transmission shaft and the sleeve sleeved on the connecting shaft fix the inner ring of the connecting bearing by clamping on both sides, and the outer ring can still rotate around the shaft; the wire reel cooperates with the concave part of the single-row sprocket and the convex part of the connecting bearing, and both the wire reel and the single-row sprocket can rotate around the axis; both ends of the transmission shaft are fixed at the bottom of the inner wall hole of the nozzle, and the other end of the sleeve abuts against the step of the hole, making the transmission shaft unable to rotate around the shaft; the wire is wound around the wire reel, and the single-row sprocket can rotate at the same speed as the wire reel.

[0016] The rotary transmission group includes a long bushing, two short bushings, an infrared speed sensor, a double-row sprocket, a connecting bearing, and a rotary transmission shaft; both ends of the rotary transmission shaft abut against the bottom and are fixed. The long bushing and the two short bushings are all sleeved on the rotary transmission shaft to abut against the inner ring of the connecting bearing and fix the inner ring. The concave part of the double-row sprocket is nested and matched with the convex part of the connecting bearing, and the double-row sprocket can rotate around the shaft together with the outer ring of the connecting bearing; at the same time, the two short bushings cooperate to fix the angular velocity sensor located between the two bushings.

[0017] An experimental method for the pneumatic piston type controllable high-speed vortex ring generator according to the above, this method includes the following three steps (the control principle schematic diagram is attached Figure 15 ):

[0018] 1. In the experimental preparation stage, the main valve, the quick-opening valve, and the quick-pressure-relief valve are all closed. The piston speed curve required for the experiment is input into the single-chip microcomputer. Calculate the required gas pressure and the pulling force that the deceleration mechanism needs to provide for the piston according to the piston speed curve. Then adjust the pressure-reducing valve so that the discharged gas pressure can make the piston speed reach the required standard. Finally, input the speed function curve into the control program, and perform corresponding control of the valves and the motor according to the input of the corresponding speed function curve;

[0019] 2. In the experimental stage, the control system and the deceleration device cooperate with each other to achieve real-time control of the piston speed. First, open the main valve and start the control program. First, the piston is in the acceleration stage. The quick-opening valve opens when it receives the opening signal sent by the program. The compressed air flow passes through the quick-opening valve and enters the nozzle, giving the piston kinetic energy to accelerate it according to the acceleration in the predetermined speed curve. If the angular velocity sensor measures that the speed is greater than the set value in this stage, feedback to adjust the torque motor group of the deceleration mechanism to change the clamping force of the two friction sleeves on the double-row sprocket, so as to reduce the piston speed; then, through this control method, make the piston move according to the preset speed curve. When entering the uniform motion stage of the piston, the single-chip microcomputer controls the torque motor group to increase the output power, and the deceleration mechanism starts to give the piston a greater pulling force. However, when the piston speed is less than the speed at the corresponding time point of the preset curve, reduce the output power of the torque motor group so that the piston motion enters the uniform motion stage; after the uniform motion stage ends, the quick-opening valve receives the closing signal and closes, and the pressure-relief valve receives the opening signal and opens to release the pressure inside the pipeline. At the same time, the torque motor group increases the power, and the deceleration mechanism increases the pulling force given to the piston. The piston enters the deceleration stage and decelerates according to the predetermined deceleration function until it stops, and the deceleration mechanism is powered off;

[0020] 3. In the experimental end stage, manually close the main valve and start the reset program. This program will start the stepping motor group to rotate, make the steering connection group rotate, and retract the steel wire into the steel wire reel until the piston is pulled back to its original position. The stepping motor group stops, and the quick-pressure-relief valve receives the closing signal and closes, and the experiment ends. Description of the Drawings

[0021] Figure 1 is the overall sectional view of the pneumatic piston-type controllable rapid vortex ring generator in the embodiment of the present invention;

[0022] Figure 2 is the three-dimensional structure schematic diagram of the pneumatic piston-type controllable rapid vortex ring generator in the embodiment of the present invention;

[0023] Figure 3 is the sectional view of the deceleration mechanism (3) in the pneumatic piston-type controllable rapid vortex ring generator in the embodiment of the present invention;

[0024] Figure 4 It is a schematic cross-sectional view of the deceleration mechanism housing (3-1) in the deceleration mechanism (3) of the pneumatic piston-type controllable rapid vortex ring generator in an embodiment of the present invention;

[0025] Figure 5 It is a three-dimensional cross-sectional schematic view of the rear end of the nozzle tube (1) in the pneumatic piston-type controllable rapid vortex ring generator in an embodiment of the present invention;

[0026] Figure 6 It is a three-dimensional schematic view of the deceleration device (3-2) in the deceleration mechanism (3) of the pneumatic piston-type controllable rapid vortex ring generator in an embodiment of the present invention;

[0027] Figure 7 It is an exploded schematic view of the transmission gear set (3-2-2) in the deceleration device (3-2) of the deceleration mechanism (3) of the pneumatic piston-type controllable rapid vortex ring generator in an embodiment of the present invention;

[0028] Figure 8 It is a cross-sectional schematic view of the transmission gear set (3-2-2) of the transmission gear set in the deceleration device (3-2) of the deceleration mechanism (3) of the pneumatic piston-type controllable rapid vortex ring generator in an embodiment of the present invention;

[0029] Figure 9 It is an exploded schematic view of the resistance clamping structure group (3-2-3) in the deceleration device (3-2) of the deceleration mechanism (3) of the pneumatic piston-type controllable rapid vortex ring generator in an embodiment of the present invention;

[0030] Figure 10 It is a cross-sectional schematic view of the resistance clamping structure group (3-2-3) in the deceleration device (3-2) of the deceleration mechanism (3) of the pneumatic piston-type controllable rapid vortex ring generator in an embodiment of the present invention;

[0031] Figure 11 It is an exploded schematic view of the steering connection group (3-2-4) in the deceleration device (3-2) of the deceleration mechanism (3) of the pneumatic piston-type controllable rapid vortex ring generator in an embodiment of the present invention;

[0032] Figure 12 It is a cross-sectional schematic view of the steering connection group (3-2-4) in the deceleration device (3-2) of the deceleration mechanism (3) of the pneumatic piston-type controllable rapid vortex ring generator in an embodiment of the present invention;

[0033] Figure 13 It is an exploded schematic view of the rotary transmission group (3-2-6) in the deceleration device (3-2) of the deceleration mechanism (3) of the pneumatic piston-type controllable rapid vortex ring generator in an embodiment of the present invention;

[0034] Figure 14It is a schematic cross-sectional view of the rotary drive group (3-2-6) in the deceleration device (3-2) of the deceleration mechanism (3) in the pneumatic piston-type controllable rapid vortex ring generator in the embodiment of the present invention;

[0035] Figure 15 It is a schematic diagram of the control principle of the control system based on a single-chip microcomputer in the pneumatic piston-type controllable rapid vortex ring generator in the embodiment of the present invention; Specific embodiments

[0036] The present invention will be described in detail below with reference to the drawings and embodiments.

[0037] Refer to Figures 1 to 14 As shown, a pneumatic piston-type controllable rapid vortex ring generator in an example provided by the present invention.

[0038] The vortex ring generator includes a nozzle (1), a piston (2), a deceleration mechanism (3), a transition pipe (4), a three-head connecting pipe (5), a quick pressure relief valve (6), a quick switch valve (7), a pressure reducing valve (8), a main valve (9), an air storage tank (10), a compressor, and a single-chip microcomputer (11);

[0039] First, regarding the power problem of the piston. The piston is arranged in the nozzle. When the main valve (9) and the quick switch valve (7) are opened and the quick pressure relief valve (6) is closed, the high-pressure gas in the air storage tank (10) enters the nozzle pipe through the valve and the pipeline to push the piston, so that the piston starts to move at high speed along the pipeline of the nozzle (1), realizing the conversion of the pressure of the high-pressure gas into the kinetic energy of the piston;

[0040] Secondly, regarding the problem of how to decelerate the piston without causing the piston to have a rebound movement in the final stage. The basic principle of realization is to use friction to provide resistance to decelerate the piston, so that the piston will not have a rebound movement in the final stage of deceleration. The specific structure is realized as follows. The piston is connected to the deceleration mechanism (3) through a steel wire. The deceleration mechanism (3) provides the required resistance for the piston to reduce the speed of the moving piston and this resistance will not cause the piston to have a rebound movement;

[0041] According to the above technical solution, the deceleration mechanism (3) includes a deceleration mechanism housing (3-1) and a deceleration device (3-2), as shown in the appendix Figure 3 ;

[0042] According to the above technical solution, the deceleration mechanism housing (3-1) includes a hole (3-1-1), motor mounting positioning holes (3-1-2) and (3-1-3), and a data line outlet hole (3-1-4). During the experimental stage, the gap between the wire and the hole is blocked with 704 glue. The specific distribution positions are as shown in the appendix Figure 4 ;

[0043] According to the above technical solution, the deceleration device (3-2) includes a torque motor group (3-2-1), a transmission gear group (3-2-2), a resistance clamping structure group (3-2-3), a steering connection group (3-2-4), a rotary transmission group (3-2-6) and a stepping motor group (3-2-5). The axial mounting positions and distances of the torque motor group (3-2-1), the transmission gear group (3-2-2) and the stepping motor group (3-2-6) are determined by the motor mounting positioning holes (3-1-2) and (3-1-3) and are on the same horizontal line. The axial mounting positions of the transmission gear group (3-2-2), the resistance clamping structure group (3-2-3) and the steering connection group (3-2-4) are on the same vertical line. The axial mounting positions of the rotary transmission group (3-2-6) and the stepping motor group (3-2-5) are on the same vertical line. The relevant positions and distances are determined by the mounting positioning holes (1-1)(1-2)(1-3), as shown in the appendix Figure 5 as shown;

[0044] According to the above technical solution, the torque motor group (3-2-1) drives the transmission gear group (3-2-2) to rotate, and then through gear transmission, the transmission gear sleeve (3-2-3-3) in the resistance clamping structure group (3-2-3) starts to rotate around the axis;

[0045] According to the above technical solution, the frictional resistance is generated by the resistance clamping structure group (3-2-3). The specific structure and principle are as follows: The resistance clamping structure group (3-2-3) forms a quasi-ball screw structure through the transmission gear sleeve (3-2-3-3) and the transmission transition sleeve (3-2-3-4), converts the rotation of the transmission gear sleeve (3-2-3-3) around the axis into the axial linear movement of the transmission transition sleeve (3-2-3-4), and then axially linearly pushes out the friction sleeve (3-2-3-5). Through the combined action of the two friction sleeves (3-2-3-5), the double-row sprocket (3-2-3-7) in rapid movement is clamped, as shown in the appendix Figure 9 , 10 as shown. The frictional force formed by the clamping will form a corresponding resistance torque and then be transmitted to the steering connection group (3-2-4) through the sprocket chain to hinder the rotation of the wire disk around the axis, so that the wire forms a pulling force on the piston in the opposite direction to the movement direction. The specific connection method of the steering connection group (3-2-4) is as shown in the appendix Figure 11 and 12 . Also, because the resistance is generated by the mutual friction between the sprocket and the friction sleeve, when the piston stops moving, the resistance also disappears, and the piston will not have a return movement at the last moment of deceleration, affecting the experimental results;

[0046] According to the above technical solution, the clamping force of the two friction sleeves (3-2-3-5) on the double-row sprocket (3-2-3-7) can be changed by adjusting the output power of the torque motor, and the frictional torque is also changed accordingly. At the same time, the tension of the steel wire on the piston is also changed;

[0047] Finally, for the control problem of the piston speed, its control principle is that the angular velocity sensor (3-2-6-7), the reduction device (3-2), and the single-chip microcomputer jointly form a closed-loop control system. Among them, the angular velocity sensor first measures the rotational speed of the sprocket in the rotary transmission group (3-2-6). Since the sprocket is driven by the forward movement of the piston, multiplying the angular velocity of the sprocket (3-2-6-2) by the radius of the sprocket (3-2-6-2) and then dividing by the radius of the wire reel (3-2-4-2) can obtain the real-time speed of the piston. The specific formula is Formula 1: V piston = ω chain *R chain / R coil (V piston represents the piston speed, ω chain represents the angular velocity of the sprocket (3-2-6-2), R chain represents the radius of the sprocket (3-2-6-2), R coil represents the radius of the wire reel (3-2-4-2)), and the installation position of the angular velocity sensor (3-2-6-7) is as shown in the appendix Figure 13 and 14 ;

[0048] The specific control principle is as follows (the attached drawing is Figure 15 ): First, according to the experiment requirements, give the single-chip microcomputer the curve of the piston's movement speed with respect to time; then, the angular velocity sensor (3-2-6-7) transmits the measured angular velocity signal back to the single-chip microcomputer through the communication function. The single-chip microcomputer converts the angular velocity into the piston's movement speed through calculation. When the measured piston speed is greater than the predetermined speed, the torque motor group (3-2-1) in the reduction device (3-2) increases the power under the control of the single-chip microcomputer, thereby increasing the resistance torque; when the piston speed is less than the predetermined speed, the torque motor group (3-2-1) reduces the power under the control of the single-chip microcomputer, thereby reducing the resistance torque; finally, the piston speed forms a dynamically balanced speed closed-loop control under the control of the above-mentioned closed-loop control system;

[0049] One end of the three-way connecting pipe (5) is connected to the quick pressure relief valve (6). When pressure relief is required, the quick pressure relief valve (6) is opened, and the high-pressure air flow is discharged from the quick pressure relief valve, so that the movement of the piston is no longer affected by the pressure of the high-pressure air flow in the subsequent stage;

[0050] According to the above technical solution, after the experiment, the stepping motor group (3-2-5) drives the steering connection group (3-2-4) to reverse through the rotary transmission group (3-2-6) to retract the steel wire, so that the piston returns to the origin.

[0051] When the pneumatic piston type controllable high-speed vortex ring generator of this embodiment is applied, the operation steps are divided into three stages in total:

[0052] In the experimental preparation stage, the main valve (9), the quick switch valve (7) and the quick pressure relief valve (6) are all closed, and the piston speed curve required for the experiment is input into the single-chip microcomputer. Regarding the power problem of the piston, it is also necessary to calculate the required pressure of the compressed gas and the pulling force that the deceleration mechanism needs to provide for the piston according to the piston speed curve, and then adjust the pressure reducing valve (8) so that the discharged gas pressure can make the piston speed reach the required standard. Finally, the speed function curve is input into the control program, and the program will perform corresponding control of the valves and motors according to the input of the corresponding speed function curve, which will be specifically shown in the next two stages.

[0053] In the experimental progress stage, the most crucial thing is the mutual cooperation between the control system and the deceleration device to achieve real-time control of the piston speed. The specific principle is as shown in the appendix Figure 15 . The specific operation steps are as follows: First, open the main valve (9) and start the control program. First, the piston is in the acceleration stage. The quick switch valve (7) opens when it receives the opening signal sent by the program. The compressed air flow passes through the quick switch valve (7) and enters the nozzle (1), giving kinetic energy to the piston to accelerate it according to the acceleration in the predetermined speed curve. If the angular velocity sensor (3-2-6-7) measures that the speed is greater than the set value in this stage, the torque motor group (3-2-1) of the deceleration mechanism (3) is feedback-adjusted to change the clamping force of the two friction sleeves (3-2-3-5) on the double-row sprocket (3-2-3-7), as shown in the appendix Figure 8 . Thus, the piston speed is reduced; then, the piston is made to move according to the preset speed curve through this control method. When entering the uniform motion stage of the piston, the single-chip microcomputer controls the torque motor group (3-2-1) to increase the output power, and the deceleration mechanism (3) starts to give the piston a greater pulling force. However, when the piston speed is less than the speed at the corresponding time point of the preset curve, the output power of the torque motor group (3-2-1) is reduced, so that the piston motion enters the uniform motion stage; after the uniform motion stage ends, the quick switch valve (7) receives the closing signal from the program and closes, and the pressure relief valve (6) receives the opening signal and opens to release the pressure inside the pipeline. At the same time, the torque motor group (3-2-1) increases the power, and the deceleration mechanism (3) increases the pulling force given to the piston. The piston enters the deceleration stage and decelerates according to the predetermined deceleration function until it stops, and the deceleration mechanism (3) is powered off;

[0054] At the end of the experiment, the main valve (9) is manually closed and the reset program is started. This program will start the rotation of the stepping motor group (3-2-5), causing the steering connection group (3-2-4) to rotate, retracting the steel wire into the wire reel (3-2-4-3) until the piston is pulled back to its original position. Then the stepping motor group (3-2-5) stops, and the quick pressure relief valve (7) receives a closing signal and closes, ending the experiment.

[0055] The above content is only a preferred embodiment of the present invention and is not used to limit the implementation of the present invention. Those of ordinary skill in the art can easily make corresponding adaptations or modifications according to the main concept and spirit of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope required by the claims.

Claims

1. A pneumatic-based piston-type controllable high-speed vortex ring generator, characterized in that It includes a nozzle (1), a piston (2), a speed reduction mechanism (3), an adapter pipe (4), a three - head connecting pipe (5), a quick pressure relief valve (6), a quick - acting switch valve (7), a pressure reducing valve (8), a main valve (9), an air storage tank (10), a compressor, and a single - chip microcomputer (11); all the above valves and pipes are connected by flange plates and bolts; the nozzle (1) includes mounting and positioning holes (1 - 1), (1 - 2), and (1 - 3); the speed reduction mechanism (3) includes a speed reduction mechanism housing (3 - 1) and a speed reduction device (3 - 2); the speed reduction mechanism housing (3 - 1) includes a hole (3 - 1 - 1), motor mounting holes (3 - 1 - 2) and (3 - 1 - 3), and a data line outlet hole (3 - 1 - 4); the speed reduction device (3 - 2) is composed of a torque motor group (3 - 2 - 1), a transmission gear group (3 - 2 - 2), a resistance clamping structure group (3 - 2 - 3), a steering connection group (3 - 2 - 4), a stepping motor group (3 - 2 - 5), and a rotary transmission group (3 - 2 - 6); the mounting and positioning holes (1 - 1), (1 - 2), (1 - 3) and the hole (3 - 1 - 1) are symmetrically present on the inner walls of the nozzle (1) and the speed reduction mechanism housing (3 - 1), where the hole (3 - 1 - 1) is a single - step hole, and the mounting and positioning holes (1 - 1), (1 - 2), (1 - 3) are all double - step holes; the torque motor group (3 - 2 - 1) includes a torque motor and a gear, the bottom of the torque motor is fixed on the inner wall of the speed reduction mechanism housing (3 - 1) by screw connection, and the rotating shaft of the torque motor is fixed to the gear.

2. The piston-type controllable high-speed vortex ring generator based on pneumatics according to claim 1, characterized in that, The stepping motor group (3 - 2 - 5) includes a stepping motor and a sprocket, the bottom of the stepping motor is fixed on the inner wall of the speed reduction mechanism housing (3 - 1) by screw connection, and the rotating shaft of the stepping motor is fixed to the single - row sprocket.

3. The piston-type controllable high-speed vortex ring generator based on pneumatics according to claim 1, wherein The torque motor group (3 - 2 - 1), the transmission gear group (3 - 2 - 2), and the resistance clamping structure group (3 - 2 - 3) are driven by gear meshing, and the steering connection group (3 - 2 - 4), the rotary transmission group (3 - 2 - 6), and the stepping motor (3 - 2 - 5) are all driven by chain - sprocket meshing.

4. A pneumatic piston-type controllable high-speed vortex ring generator according to claim 1, characterized in that, The matching of the parts in the transmission gear group (3 - 2 - 2) and the resistance clamping structure group (3 - 2 - 3) is symmetric.

5. A pneumatic-based piston-type controllable high-speed vortex ring generator according to claim 1, characterized in that The quick pressure relief valve (6), the quick - acting switch valve (7), the torque motor group (3 - 2 - 1), and the stepping motor group (3 - 2 - 5) are all controlled by the single - chip microcomputer.

6. The piston-type controllable high-speed vortex ring generator based on pneumatics according to claim 5, wherein The transmission gear set (3-2-2) includes a transmission shaft (3-2-2-1), two gears (3-2-2-2), two sleeves (3-2-2-3), two bearings (3-2-2-4) and two bearing shims (3-2-2-5); the bearing shims (3-2-2-5) and the bearings (3-2-2-4) are fixed at the hole (3-1-1) on the inner wall of the reduction mechanism housing (3-1) by an interference fit, and the bearing shims (3-2-2-5) are located between the bearings (3-2-2-4) and the hole (3-1-1); thereby, the outer ring of the bearing (3-2-2-4) is fixed while the inner ring can rotate around the shaft; the inner ring of the bearing (3-2-2-4) is fitted with the first step of the transmission shaft (3-2-2-1); the sleeve (3-2-2-3) and the second step of the transmission shaft (3-2-2-1) fix the gear (3-2-2-2) and the gear can rotate with the inner ring of the bearing (3-2-2-4).

7. The piston-type controllable high-speed vortex ring generator based on pneumatics according to claim 6, characterized in that, The resistance clamping structure group (3-2-3) includes two bearing shims (3-2-3-1), two bearings (3-2-3-2), two transmission gear sleeves (3-2-3-3), two transmission transition sleeves (3-2-3-4), two friction sleeves (3-2-3-5), two lubricating bushings (3-2-3-6), a double-row sprocket (3-2-3-7), a sprocket shaft (3-2-3-8) and a sprocket bearing (3-2-3-9); the sprocket shaft (3-2-3-8) is fixed at the bottom of the nozzle installation positioning hole (1-1) by interference fit; one end of the lubricating bushing (3-2-3-6) abuts against the step of the nozzle installation positioning hole (1-1) in the middle, and the other end abuts against the inner ring of the sprocket bearing (3-2-3-9). After the lubricating bushing (3-2-3-6) is sleeved on the sprocket shaft (3-2-3-8), it needs to be welded to fix the bushing and the shaft as a whole. Another lubricating bushing (3-2-3-6) fixes the inner ring of the sprocket bearing (3-2-3-9) by symmetric cooperation in the same way; both the bearing shim (3-2-3-1) and the bearing (3-2-3-2) are fixed at the step of the nozzle (1) installation positioning hole (1-1) by interference fit. The bearing shim (3-2-3-1) is located between the sprocket shaft (3-2-3-8) and the step of the installation positioning hole (1-1), which makes the outer ring of the bearing (3-2-3-2) fixed and the inner ring can rotate around the sprocket shaft (3-2-3-8); the concave part in the double-row sprocket (3-2-3-7) cooperates with the convex part on the sprocket bearing (3-2-3-2) to fix the outer ring of the sprocket bearing (3-2-3-2) and the double-row sprocket (3-2-3-7), so that the double-row sprocket (3-2-3-7) can rotate around the axis; the convex part of the lubricating bushing (3-2-3-6) cooperates with the concave part of the transmission gear sleeve (3-2-3-3), so that the transmission gear sleeve (3-2-3-3) can make a linear movement along the axial direction on the lubricating bushing (3-2-3-6); the internal thread of the transmission gear sleeve (3-2-3-3) is rotationally matched with the external thread of the transmission transition sleeve (3-2-3-4); the convex side of the transmission gear sleeve (3-2-3-3) abuts against the inner ring of the sprocket bearing (3-2-3-2), so that the transmission gear sleeve (3-2-3-3) can rotate around the axis together with the inner ring of the sprocket bearing (3-2-3-2).

8. A pneumatic-based piston-type controllable high-speed vortex ring generator according to claim 7, characterized in that, The steering connection group (3-2-4) includes a sleeve (3-2-4-1), a wire disk (3-2-4-2), a connecting bearing (3-2-4-3), a single-row sprocket (3-2-4-4) and a transmission shaft (3-2-4-5); the two-step of the transmission shaft (3-2-4-5) and the sleeve (3-2-4-1) sleeved on the connecting shaft fix the inner ring of the connecting bearing (3-2-4-3) by means of clamping on both sides, and the outer ring can still rotate around the shaft; the wire disk (3-2-4-2) cooperates with the concave part of the single-row sprocket (3-2-4-4) and the convex part of the connecting bearing (3-2-4-3), and both the wire disk (3-2-4-2) and the single-row sprocket (3-2-4-4) can rotate around the axis; both ends of the transmission shaft (3-2-4-5) are fixed at the bottom of the nozzle installation positioning hole (1-2), and the other end of the sleeve (3-2-4-1) abuts against the step of the installation positioning hole (1-2), so that the transmission shaft (3-2-4-5) cannot rotate around the shaft; the wire is wound on the wire disk (3-2-4-2), and the single-row sprocket (3-2-4-4) can rotate at the same speed as the wire disk (3-2-4-2).

9. The piston-type controllable high-speed vortex ring generator based on pneumatics according to claim 8, wherein, The slewing drive group (3-2-6) includes a long shaft sleeve (3-2-6-1), two short shaft sleeves (3-2-6-5) (3-2-6-6), an infrared speed sensor (3-2-6-7), a double-row sprocket (3-2-6-2), a connecting bearing (3-2-6-3) and a slewing transmission shaft (3-2-6-4); both ends of the slewing transmission shaft (3-2-6-4) abut against the bottom of the installation positioning hole (1-3) and are fixed. The long shaft sleeve (3-2-6-1) and the two short shaft sleeves (3-2-6-5) (3-2-6-6) are all sleeved on the slewing transmission shaft (3-2-6-4) to abut against the inner ring of the connecting bearing (3-2-6-3) and fix the inner ring. The concave part of the double-row sprocket (3-2-6-2) is nested and matched with the convex part of the connecting bearing (3-2-6-3), and the double-row sprocket (3-2-6-2) can rotate around the shaft together with the outer ring of the connecting bearing (3-2-6-3); at the same time, the two short shaft sleeves (3-2-6-5) (3-2-6-6) cooperate to fix the angular velocity sensor (3-2-6-7) located between the two shaft sleeves.

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