A gas-hydraulic linkage actuator for natural gas transportation pipelines

Abstract

This invention relates to the field of valve actuator technology, specifically a gas-hydraulic linkage actuator for natural gas transportation pipelines. It includes a gas storage tank, an opening gas-hydraulic tank, a closing gas-hydraulic tank, and an actuator cylinder. The gas storage tank, controlled by a gas valve, inputs compressed gas into either the opening or closing gas-hydraulic tank. Under the action of the compressed gas, the opening or closing gas-hydraulic tank generates positive pressure hydraulic oil, which is then input into the actuator cylinder to control its opening and closing action. This invention can store compressed gas in the gas storage tank as a power source, and also possesses the incompressibility of hydraulic oil, enabling the natural gas transportation pipeline to maintain a rigid and stable closed state after shutdown, thus enhancing safety. Furthermore, the output hydraulic oil has a pulse pressurization effect, which is beneficial for breaking up blockages and congestion in the hydraulic pipeline.

Description

Technical Field

[0001] This invention relates to the field of valve actuator technology, specifically a gas-liquid linkage actuator for natural gas transportation pipelines. Background Technology

[0002] After the valves in a natural gas transportation pipeline are closed, they need to remain in a stable locked state to completely prevent gas leakage. Existing natural gas valve actuators are generally divided into pneumatic actuators and hydraulic actuators. Pneumatic actuators, due to the compressible nature of gas, are softer and more elastic when used as a medium, which can easily lead to problems such as valves not closing tightly or being forced open by the pressure of natural gas in the pipeline after closing, posing significant safety hazards. Hydraulic actuators, on the other hand, can achieve a stable and rigid lock-up of the natural gas valve after it is closed by utilizing the incompressible nature of hydraulic oil. However, they require a hydraulic station to maintain the hydraulic pressure, which places high demands on on-site conditions and increases pipeline layout costs. Summary of the Invention

[0003] The purpose of this invention is to provide a pneumatic-hydraulic linkage actuator for natural gas transportation pipelines, so as to solve the limitations of pure pneumatic or pure hydraulic actuators mentioned in the background art.

[0004] To achieve the above objectives, the present invention provides the following technical solution: a gas-hydraulic linkage actuator for natural gas transportation pipelines, comprising a gas storage tank, an opening gas-hydraulic tank, a closing gas-hydraulic tank, and an actuator cylinder. The gas storage tank, controlled by a gas valve, inputs compressed gas into the opening or closing gas-hydraulic tank. Under the action of the compressed gas, the opening or closing gas-hydraulic tank generates positive pressure hydraulic oil, which is then input into the actuator cylinder, controlling its opening and closing action. Both the opening and closing gas-hydraulic tanks are equipped with gas-hydraulic floats for the compressed gas... Located above the gas-liquid floating roof, with hydraulic oil below it; an impact support column is fixedly installed on the upper surface of the gas-liquid floating roof, and a counterweight block is installed above the gas-liquid floating roof. The impact support column passes through the counterweight block, and a block compression spring is installed on the upper part of the counterweight block to apply downward pressure to the counterweight block. An adaptive lifting component is also installed on the upper part of the gas-liquid floating roof. The adaptive lifting component intermittently pushes the counterweight block only when the gas-liquid floating roof moves downward, so that the counterweight block, in conjunction with the block compression spring, generates a downward impact force.

[0005] The adaptive lifting assembly includes a friction roller, a roller shaft that is drivenly connected to the friction roller, and a first bevel tooth coaxially fixed on the roller shaft. The friction roller makes frictional contact with the inner wall surface of the open or closed gas-liquid tank. When the gas-liquid float moves up and down inside the open or closed gas-liquid tank, it can drive the friction roller to rotate in both directions.

[0006] The first bevel tooth is externally meshed with a second bevel tooth, and a worm shaft is coaxially fixedly mounted on the second bevel tooth. The worm shaft is externally meshed with a worm wheel portion, and a split bottom shaft is fixedly mounted at the center of the worm wheel portion. When the first bevel tooth rotates, the split bottom shaft can be driven to rotate through the above transmission. A bottom shaft seat is fixedly mounted on the upper surface of the gas-liquid float, and the split bottom shaft is rotatably mounted in the bottom shaft seat.

[0007] The split bottom shaft is fitted with a one-way rotating cylinder. The split bottom shaft drives the one-way rotating cylinder to rotate in one direction only when the gas-liquid float moves downward. The surface of the one-way rotating cylinder is fixedly provided with a slanted support, and the inside of the counterweight block is fixedly provided with a cooperating support shaft. When the one-way rotating cylinder rotates, the slanted support, through cooperation with the cooperating support shaft, pushes the counterweight block to move upward into position and then falls vertically downward.

[0008] The split bottom shaft has a through groove, a one-way tooth is inserted in the through groove, and a two-way force spring is also provided in the through groove. The two-way force spring applies an outward pushing force to the one-way tooth.

[0009] A ratchet ring is also fixedly installed on the inner wall of the unidirectional rotating cylinder. Under the thrust of the bidirectional force spring, the unidirectional teeth engage with the ratchet ring. Through the cooperation between the unidirectional teeth and the ratchet ring, the split bottom shaft drives the unidirectional rotating cylinder to rotate in one direction.

[0010] An arc-shaped side plate is fixedly provided on the upper surface of the gas-liquid float. A track protrusion is fixedly provided on the surface of the arc-shaped side plate. A counterweight impact ring is slidably provided on the outside of the track protrusion. The track protrusion limits the counterweight impact ring to rotate circumferentially within a certain angle around the axis of the gas-liquid float. A bearing part is fixedly provided at the end of the arc-shaped side plate. A spring piece is provided above the gas-liquid float. The spring piece applies a spring force to the counterweight impact ring, causing the counterweight impact ring to tend to move in the direction of the bearing part.

[0011] The counterweight impact ring has a toothed structure; the impact support column is fitted with a one-way rotating sleeve, and a single-unit pawl is fixedly installed on the one-way rotating sleeve. When the one-way rotating sleeve rotates one revolution, the single-unit pawl can engage with the toothed structure within a certain angle and move the counterweight impact ring once.

[0012] A ratchet assembly is provided between the one-way rotating sleeve and the impact support column. The ratchet assembly limits the one-way rotating sleeve, so that the one-way rotating sleeve can only rotate in one direction.

[0013] An oblique toothed ring is fixedly provided on the unidirectional rotating sleeve, and a mating push tooth is provided below the counterweight block. A downward support part and an upward elastic part are fixedly provided on the mating push tooth. The mating push tooth is fixedly connected to the lower surface of the counterweight block through the upward elastic part. When the counterweight block moves down, the downward support part supports the lower surface of the counterweight block, so that the mating push tooth squeezes and drives the oblique toothed ring, causing the unidirectional rotating sleeve to rotate at a certain angle.

[0014] Compared with the prior art, the beneficial effects of the present invention are as follows: 1. The gas-hydraulic linkage actuator of the present invention adopts a gas-hydraulic combination method, which can store compressed gas in the gas storage tank as a power source, and also has the incompressibility of hydraulic oil, so that the natural gas transportation pipeline can maintain a rigid and stable closed state after being closed, which is safer; and through the cooperation of the gas-hydraulic float, the counterweight block and the adaptive lifting component, the counterweight block can apply a downward impact force to the gas-hydraulic float during the process of the gas-hydraulic float moving down to output hydraulic oil, so that the output hydraulic oil has a pulse pressurization effect, which is beneficial to break the blockage and congestion in the hydraulic pipeline and maintain the action speed of the actuator for a long time.

[0015] 2. This invention, through the combination of a counterweight impact ring, a one-way rotating sleeve, and a counterweight block, can control the counterweight impact ring by utilizing each downward impact of the counterweight block. This allows the counterweight impact ring to periodically strike the impact-bearing part, generating rotational force on the gas-liquid float. This periodic rotation at a certain angle prevents excessive wear on the inner wall of the open or closed valve gas-liquid tank by the friction rollers in the same vertical position. By evenly distributing wear, the probability of leakage between the gas-liquid float and the open or closed valve gas-liquid tank is reduced. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of the overall structure of the present invention.

[0017] Figure 2 This is a three-dimensional half-section diagram of the valve-opening gas-liquid tank.

[0018] Figure 3 This is a three-dimensional semi-sectional schematic diagram of the gas-liquid float section at the valve-opening gas-liquid tank.

[0019] Figure 4 This is a schematic diagram of the three-dimensional semi-section plunger unit at the valve-opening gas-liquid tank.

[0020] Figure 5 This is a three-dimensional half-section diagram of the horizontal angle at the actuator.

[0021] Figure 6 This is a partial three-dimensional cross-section diagram of the horizontal angle at the actuator.

[0022] Figure 7 This is a schematic diagram of the structure of the gas-liquid floating disk.

[0023] Figure 8 This is a schematic diagram of the structure at the gas-liquid floating disk in an explosion.

[0024] Figure 9 This is a top view of the structure at the gas-liquid floating disk.

[0025] Figure 10 This is a side view of the structure at the gas-liquid floating disk.

[0026] Figure 11 This is a partial side view of the structure at the gas-liquid floating disk.

[0027] Figure 12 This is a three-dimensional half-section diagram of the gas-liquid floating plate.

[0028] Figure 13 This is a partial three-dimensional cross-sectional view of the gas-liquid floating plate.

[0029] Figure 14 This is a three-dimensional half-section diagram of the gas-liquid floating plate from another angle.

[0030] Figure 15 This is a schematic diagram of the bottom structure of the counterweight block.

[0031] In the diagram: 1. Gas storage tank; 2. Opening gas-liquid tank; 3. Closing gas-liquid tank; 4. Gas-liquid float; 5. Impact support column; 6. Counterweight block; 7. Block compression spring; 8. Arc-shaped side plate; 9. Actuating cylinder; 401. Friction roller; 402. Roller shaft; 403. First bevel gear; 404. Second bevel gear; 405. Worm shaft; 406. Worm wheel section; 407. Split bottom shaft; 408. Bottom shaft seat; 409. One-way rotating cylinder; 410. Inclined support section; 411. Matching support shaft; 412. Through groove; 413. One-way shifting tooth; 414. Two-way force-applying spring; 415. Ratchet ring; 801. Track protrusion; 802. Counterweight impact ring; 803. 804. Impact bearing part; 805. Spring piece; 806. Tooth structure; 807. One-way rotating sleeve; 808. Single-unit prying tooth; 809. Ratchet assembly; 810. Angled gear ring; 811. Matching push tooth; 812. Lowering support part; 813. Upper lifting elastic part; 201. Control air inlet pipe; 202. Plunger unit; 203. Hydraulic flow channel; 204. Sedimentation tank; 205. Sewage discharge channel; 206. Sealing bolt; 501. Horizontal frame plate; 502. Matching top shaft; 901. Valve unit; 902. Natural gas pipeline; 903. Actuating inner cylinder; 904. Drive blade; 905. Separator seat; 906. Valve closing liquid hole; 907. Valve opening liquid hole. Detailed Implementation

[0032] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0033] Please see Figures 1 to 15 This invention provides a technical solution: a gas-liquid linkage actuator for natural gas transportation pipelines, comprising a gas storage tank 1, an opening gas-liquid tank 2, a closing gas-liquid tank 3, and an actuator cylinder 9. The gas storage tank 1 controls the input of compressed gas into the opening gas-liquid tank 2 or the closing gas-liquid tank 3 via a gas valve. Figure 1 As shown, control inlet pipes 201 are respectively connected to the upper ends of the open-valve gas-liquid tank 2 and the closed-valve gas-liquid tank 3. The gas storage tank 1 is individually connected to the control inlet pipe 201 via a gas valve. The gas valve allows the compressed gas in the gas storage tank 1 to selectively enter the open-valve gas-liquid tank 2 or the closed-valve gas-liquid tank 3. The gas valve mentioned above is a valve combination unit in the prior art, which can realize the on-off control of gas. It is omitted in the accompanying drawings of this invention. The gas storage tank 1 is connected to the compressed gas source. By setting a one-way valve, the gas in the compressed gas source flows unidirectionally into the gas storage tank 1. Therefore, in the event of power failure, pipeline rupture, or other conditions, after the compressed gas source is lost, the compressed gas stored in the gas storage tank 1 can still complete the emergency drive of the open-valve gas-liquid tank 2 and the closed-valve gas-liquid tank 3 within a certain number of times.

[0034] The valve-opening gas-liquid tank 2 or the valve-closing gas-liquid tank 3 generates positive pressure hydraulic oil under the action of compressed gas and inputs it into the actuator 9, controlling the opening and closing action of the actuator 9, such as... Figure 1 As shown, a valve unit 901 is provided at the lower part of the actuator 9. The valve unit 901 can be opened and closed by rotating 90 degrees. The valve unit 901 is installed on the natural gas pipeline 902. Natural gas is output from the natural gas pipeline 902. By rotating the actuator 9, the valve unit 901 can be closed or opened, thereby controlling the natural gas in the natural gas pipeline 902.

[0035] like Figure 4 As shown, both the bottom of the open-valve gas-liquid tank 2 and the closed-valve gas-liquid tank 3 are respectively equipped with plunger units 202. This invention... Figure 4 The example shown is the valve-opening gas-liquid tank 2. The plunger unit 202 is in sealed contact with the valve-opening gas-liquid tank 2.

[0036] The plunger unit 202 has a hydraulic flow channel 203, such as Figure 4As shown, the upper end of the hydraulic flow channel 203 is higher than the bottom of the valve-opening gas-liquid tank 2 by a certain height and then communicates with the inner cavity of the valve-opening gas-liquid tank 2. The other end of the hydraulic flow channel 203 is connected to the actuator cylinder 9 to drive the actuator cylinder 9. The plunger unit 202 is also provided with a sedimentation drain 204 and a sewage discharge channel 205 that are interconnected. The sediment generated by the hydraulic oil in the valve-opening gas-liquid tank 2 can be discharged to the outside through the sedimentation drain 204 and the sewage discharge channel 205. The bottom of the sewage discharge channel 205 is spirally installed with a sealing bolt 206, which seals the sewage discharge channel 205. When it is necessary to discharge the sediment, the sealing bolt 206 can be removed, which is convenient for maintenance.

[0037] Both the open-valve gas-liquid tank 2 and the closed-valve gas-liquid tank 3 are equipped with gas-liquid floats 4. The gas-liquid floats 4 are in sealed contact with the inner wall surfaces of the open-valve gas-liquid tank 2 and the closed-valve gas-liquid tank 3 through rubber rings. The compressed gas is located above the gas-liquid floats 4, and the hydraulic oil is located below the gas-liquid floats 4. Thus, when the compressed gas acts on the gas-liquid floats 4, the gas-liquid floats 4 can push the hydraulic oil below to output.

[0038] An impact support column 5 is welded and fixed to the upper surface of the gas-liquid float 4, such as... Figure 14 As shown, the impact support column 5 is integrally formed by two cylinders with different diameters, the lower cylinder having a larger diameter than the upper cylinder. A counterweight block 6 is provided above the gas-liquid float 4, and the impact support column 5 passes through the counterweight block 6. A block compression spring 7 is provided on the upper part of the counterweight block 6 to apply downward pressure to the counterweight block 6. An adaptive lifting component is also provided on the upper part of the gas-liquid float 4. The adaptive lifting component intermittently pushes the counterweight block 6 only when the gas-liquid float 4 moves downward, so that the counterweight block 6, in conjunction with the block compression spring 7, generates a downward impact force.

[0039] like Figure 9 As shown, the adaptive lifting assembly includes a friction roller 401, a roller shaft 402 that is drivenly connected to the friction roller 401, and a first bevel tooth 403 that is coaxially fixed on the roller shaft 402. The friction roller 401 is in frictional contact with the inner wall surface of the open valve gas-liquid tank 2 or the closed valve gas-liquid tank 3. When the gas-liquid float 4 moves up and down inside the open valve gas-liquid tank 2 or the closed valve gas-liquid tank 3, it can drive the friction roller 401 to rotate in both directions.

[0040] A second bevel tooth 404 is externally meshed with the first bevel tooth 403. A worm shaft 405 is coaxially fixedly mounted on the second bevel tooth 404. A support structure is welded and fixedly mounted on the upper surface of the gas-liquid float 4. The support structure supports and limits the roller shaft 402 and the worm shaft 405. A worm wheel portion 406 is externally meshed with the worm shaft 405. A split bottom shaft 407 is fixedly mounted at the center of the worm wheel portion 406. When the first bevel tooth 403 rotates, the split bottom shaft 407 can be driven to rotate through the above transmission.

[0041] like Figure 12 As shown, a bottom shaft seat 408 is fixedly installed on the upper surface of the gas-liquid floating disk 4, and a split bottom shaft 407 is rotatably installed in the bottom shaft seat 408.

[0042] A one-way rotating cylinder 409 is sleeved on the outside of the split bottom shaft 407. The split bottom shaft 407 drives the one-way rotating cylinder 409 to rotate in one direction only when the gas-liquid float 4 moves downward; for example Figure 14 As shown, the upper end of the impact support column 5 is detachably fixed with a crossbeam plate 501 by screws. The bottom of the crossbeam plate 501 is welded and fixed with a mating top shaft 502. The lower end of the mating top shaft 502 presses against the one-way rotating cylinder 409 to limit the one-way rotating cylinder 409.

[0043] like Figure 8 As shown, a beveled support 410 is fixedly provided on the surface of the unidirectional rotating cylinder 409, such as... Figure 14 As shown, the counterweight block 6 is fixedly provided with a matching support shaft 411. When the unidirectional rotating cylinder 409 rotates, the inclined support 410, through its cooperation with the matching support shaft 411, pushes the counterweight block 6 upward to its position and then falls vertically downward.

[0044] like Figure 13 As shown, a through groove 412 is provided inside the split bottom shaft 407, and a one-way pawl 413 is inserted into the through groove 412. A two-way force-applying spring 414 is also provided in the through groove 412, and the two-way force-applying spring 414 applies an outward pushing force to the one-way pawl 413. A ratchet ring 415 is also fixedly provided on the inner wall of the one-way rotating cylinder 409. Under the pushing force of the two-way force-applying spring 414, the one-way pawl 413 contacts and engages with the ratchet ring 415. Through the cooperation of the one-way pawl 413 and the ratchet ring 415, the split bottom shaft 407 drives the one-way rotating cylinder 409 to rotate in one direction.

[0045] An arc-shaped side plate 8 is fixedly provided on the upper surface of the gas-liquid float 4. A track protrusion 801 is fixedly provided on the surface of the arc-shaped side plate 8. A counterweight impact ring 802 is slidably provided on the outside of the track protrusion 801. The counterweight impact ring 802 can rotate circumferentially within a certain angle around the axis of the gas-liquid float 4 by the limiting of the track protrusion 801. A bearing part 803 is fixedly provided at the end of the arc-shaped side plate 8. A spring piece 804 is provided above the gas-liquid float 4. The spring piece 804 applies a spring force to the counterweight impact ring 802, so that the counterweight impact ring 802 has a tendency to move in the direction of the bearing part 803.

[0046] The counterweight impact ring 802 has a toothed structure 805; the impact support column 5 is fitted with a one-way rotating sleeve 806, and a single-unit prying tooth 807 is fixedly installed on the one-way rotating sleeve 806. When the one-way rotating sleeve 806 rotates one revolution, the single-unit prying tooth 807 can mesh with the toothed structure 805 within a certain angle and pry the counterweight impact ring 802 once.

[0047] A ratchet assembly 808 is provided between the one-way rotating sleeve 806 and the impact support column 5. The ratchet assembly 808 limits the one-way rotating sleeve 806, so that the one-way rotating sleeve 806 can only rotate in one direction.

[0048] like Figure 11 As shown, a unidirectional rotating sleeve 806 is fixedly provided with an oblique gear ring 809, and a mating push tooth 810 is provided below the counterweight block 6. The mating push tooth 810 is fixedly provided with a downward pressure support part 811 and an upward lifting elastic part 812. The mating push tooth 810 is fixedly connected to the lower surface of the counterweight block 6 through the upward lifting elastic part 812. When the counterweight block 6 moves down, the downward pressure support part 811 supports the lower surface of the counterweight block 6, so that the mating push tooth 810 squeezes and drives the oblique gear ring 809, causing the unidirectional rotating sleeve 806 to rotate at a certain angle.

[0049] like Figure 6 As shown, the actuator cylinder 9 has an inner actuator cylinder 903 inside. The rotation of the inner actuator cylinder 903 controls the opening and closing of the valve unit 901. A drive blade 904 is fixedly mounted on the inner actuator cylinder 903, and the drive blade 904 is in sealed contact with the inner wall surface of the actuator cylinder 9. A separator seat 905 is also fixedly mounted inside the actuator cylinder 9, and the separator seat 905 is in sealed contact with the inner actuator cylinder 903. A valve-closing fluid hole 906 and a valve-opening fluid hole 907 are formed through the inner wall of the actuator cylinder 9. The hydraulic flow channel 203 corresponding to the valve-opening gas-liquid tank 2 is connected to the valve-opening fluid hole 907, and the hydraulic flow channel 203 corresponding to the valve-closing gas-liquid tank 3 is connected to the valve-closing fluid hole 906. Hydraulic oil is input through the valve-closing fluid hole 906 or the valve-opening fluid hole 907, and the pressure acts on the surface of the drive blade 904, enabling forward and reverse drive control of the inner actuator cylinder 903.

[0050] Furthermore, a hydraulic valve is also arranged on the hydraulic pipeline that connects the hydraulic flow channel 203 to the valve closing port 906 or the valve opening port 907. When the hydraulic valve is closed, it can lock the hydraulic oil in the pipeline. By utilizing the incompressible property of the hydraulic oil, the position of the drive plate 904 is completely locked and fixed.

[0051] When the compressed gas from the gas storage tank 1 enters the interior of the valve-opening gas-liquid tank 2 or the valve-closing gas-liquid tank 3, the gas pressure of the compressed gas acts on the upper part of the gas-liquid float 4, pushing the gas-liquid float 4 downward, so that the hydraulic oil below the gas-liquid float 4 is input into the valve-closing liquid hole 906 or the valve-opening liquid hole 907 through the hydraulic flow channel 203, thereby performing forward and reverse drive control on the inner cylinder 903.

[0052] like Figure 3 and Figure 9 As shown, when the gas-liquid float 4 moves downward, the friction roller 401 rotates by frictional contact with the inner wall surface of the open valve gas-liquid tank 2 or the closed valve gas-liquid tank 3. The roller shaft 402 and the first bevel gear 403 rotate synchronously. The first bevel gear 403 drives the second bevel gear 404 to rotate through meshing, which in turn drives the worm shaft 405 to rotate.

[0053] like Figure 13 and Figure 14 As shown, the worm shaft 405 drives the worm wheel 406 and the split bottom shaft 407 to rotate through meshing. The split bottom shaft 407 drives the ratchet ring 415 to rotate the one-way rotating cylinder 409 through the one-way shifting tooth 413.

[0054] like Figure 8 As shown, the surface of the one-way rotating cylinder 409 is provided with a sloping support 410. One side of the sloping support 410 is an inclined plane and the other side is a vertical plane. During the rotation of the one-way rotating cylinder 409, the sloping support 410 lifts the counterweight block 6 by moving the mating support shaft 411 through the inclined plane, causing the block compression spring 7 to be elastically compressed. When the mating support shaft 411 moves to the vertical plane of the sloping support 410, the mating support shaft 411 and the counterweight block 6 fall vertically under the restoring force of the block compression spring 7, causing the counterweight block 6 to impact and strike the base of the impact support column 5, applying a downward impact force to the gas-liquid float 4. Through the cyclic action during the rotation of the one-way rotating cylinder 409, the hydraulic oil output from the hydraulic flow channel 203 has a pulse pressurization effect, which is beneficial for breaking up the blockages in the hydraulic pipeline.

[0055] When the gas-liquid float 4 moves upward, the friction roller 401, worm shaft 405 and split bottom shaft 407 rotate in opposite directions, and the power is transmitted to the ratchet ring 415. Through the one-way ratchet structure between the one-way gear 413 and the ratchet ring 415, the one-way rotating cylinder 409 will not be driven, and the one-way rotating cylinder 409 will be in a stopped state.

[0056] During the above process, each time the counterweight block 6 moves down to its position, such as Figure 11 and Figure 15 As shown, the counterweight block 6, in conjunction with the pusher tooth 810, compresses the oblique gear ring 809, causing the oblique gear ring 809 to drive the one-way rotating sleeve 806 to rotate clockwise by a certain angle when viewed from above. Figure 11As shown, when the mating pusher 810 presses downward, the downward support part 811 supports the lower surface of the counterweight block 6, preventing the mating pusher 810 from bending upward. When the counterweight block 6 moves upward, because the upper part of the teeth of the inclined gear ring 809 is tilted to the left, part of it presses on the mating pusher 810. During the upward movement of the mating pusher 810, the upward elastic part 812 avoids this by elastic bending, allowing the mating pusher 810 to move smoothly out of the inclined gear ring 809.

[0057] The ratchet assembly 808 ensures that the unidirectional rotating sleeve 806 can only rotate in one direction. Figure 11 As shown, the one-way adapter 806 is in Figure 11 From a top-down perspective, it can only rotate clockwise.

[0058] The above-mentioned structural arrangement ensures that each time the counterweight block 6 moves down to its position, it will cumulatively drive the unidirectional rotating sleeve 806 to rotate at a certain angle.

[0059] like Figure 7 and Figure 8 As shown, a single-unit prying tooth 807 is fixedly provided on the surface of the one-way rotating sleeve 806. During the rotation of the one-way rotating sleeve 806, the single-unit prying tooth 807, through cooperation with the tooth structure 805, can pry the counterweight impact ring 802 a certain distance and release it, so that the counterweight impact ring 802, under the elastic force of the spring piece 804, impacts the impact bearing part 803, thereby causing the gas-liquid float 4 to generate a rotational impact force.

[0060] like Figure 3 As shown, during the up-and-down movement of the gas-liquid float 4, the friction roller 401 is always in frictional contact with the inner wall of the valve-opening gas-liquid tank 2 at the same vertical position. In long-term operation, after the friction roller 401 wears down the corresponding position of the inner wall of the valve-opening gas-liquid tank 2, resulting in a vertical indentation, leakage is likely to occur between the vertical indentation and the gas-liquid float 4. The present invention generates a rotational impact force by having the counterweight impact ring 802 strike the impact bearing part 803, so that the gas-liquid float 4 can rotate at a certain small angle periodically. This can disperse the wear of the friction roller 401 on the inner wall of the valve-opening gas-liquid tank 2 in the circumferential direction, thereby reducing the probability of sealing leakage between the gas-liquid float 4 and the inner wall of the valve-opening gas-liquid tank 2.

[0061] Although embodiments of the invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the appended claims and their equivalents.

Claims

1. A gas-liquid linkage actuator for a natural gas transportation pipeline, comprising a gas storage tank, a valve-opening gas-liquid tank, a valve-closing gas-liquid tank, and an actuator cylinder, characterized in that: The gas storage tank is controlled by a gas valve to input compressed gas into the open valve gas-liquid tank or the closed valve gas-liquid tank. Under the action of the compressed gas, the open valve gas-liquid tank or the closed valve gas-liquid tank generates positive pressure hydraulic oil and inputs it into the actuator cylinder to control the opening and closing action of the actuator cylinder. Both the opening and closing gas-liquid tanks are equipped with gas-liquid floats, with compressed gas located above the gas-liquid floats and hydraulic oil located below the gas-liquid floats. An impact support column is fixedly installed on the upper surface of the gas-liquid floating disk. A counterweight block is installed above the gas-liquid floating disk. The impact support column passes through the counterweight block. A block compression spring is installed on the upper part of the counterweight block to apply downward pressure to the counterweight block. An adaptive lifting component is also installed on the upper part of the gas-liquid floating disk. The adaptive lifting component intermittently pushes the counterweight block only when the gas-liquid floating disk moves downward, so that the counterweight block and the block compression spring generate a downward impact force.

2. The gas-hydraulic linkage actuator for natural gas transportation pipelines according to claim 1, characterized in that: The adaptive lifting assembly includes a friction roller, a roller shaft that is drivenly connected to the friction roller, and a first bevel tooth that is coaxially fixed on the roller shaft. The friction rollers make frictional contact with the inner wall surface of the open or closed gas-liquid tank. When the gas-liquid float moves up and down inside the open or closed gas-liquid tank, it can drive the friction rollers to rotate in both directions.

3. The gas-hydraulic linkage actuator for natural gas transportation pipelines according to claim 2, characterized in that: The first bevel tooth is externally meshed with a second bevel tooth, and a worm shaft is coaxially fixedly mounted on the second bevel tooth. The worm shaft is externally meshed with a worm wheel portion, and a split bottom shaft is fixedly mounted at the center of the worm wheel portion. When the first bevel tooth rotates, the split bottom shaft can be driven to rotate through the above transmission. A bottom shaft seat is fixedly installed on the upper surface of the gas-liquid floating disk, and the split bottom shaft is rotatably installed in the bottom shaft seat.

4. The gas-hydraulic linkage actuator for natural gas transportation pipelines according to claim 3, characterized in that: The split bottom shaft is fitted with a one-way rotating cylinder. The split bottom shaft drives the one-way rotating cylinder to rotate in one direction. The split bottom shaft can drive the one-way rotating cylinder to rotate only when the gas-liquid float moves down. The surface of the unidirectional rotating cylinder is fixedly provided with a slanted support, and the interior of the counterweight block is fixedly provided with a cooperating support shaft. When the unidirectional rotating cylinder rotates, the slanted support, in cooperation with the cooperating support shaft, pushes the counterweight block upward to its position and then falls vertically downward.

5. The gas-hydraulic linkage actuator for natural gas transportation pipelines according to claim 4, characterized in that: The split bottom shaft has a through groove, a one-way tooth is inserted in the through groove, and a two-way force spring is also provided in the through groove. The two-way force spring applies an outward pushing force to the one-way tooth.

6. The gas-hydraulic linkage actuator for natural gas transportation pipelines according to claim 5, characterized in that: A ratchet ring is also fixedly installed on the inner wall of the unidirectional rotating cylinder. Under the thrust of the bidirectional force spring, the unidirectional teeth engage with the ratchet ring. Through the cooperation between the unidirectional teeth and the ratchet ring, the split bottom shaft drives the unidirectional rotating cylinder to rotate in one direction.

7. The gas-hydraulic linkage actuator for natural gas transportation pipelines according to claim 1, characterized in that: An arc-shaped side plate is fixedly provided on the upper surface of the gas-liquid floating disk, and a track protrusion is fixedly provided on the surface of the arc-shaped side plate. A counterweight impact ring is slidably provided on the outside of the track protrusion. The counterweight impact ring can rotate circumferentially within a certain angle around the axis of the gas-liquid floating disk by limiting the track protrusion. The end of the arc-shaped side plate is fixedly provided with a bearing part, and a spring piece is provided above the gas-liquid float. The spring piece applies a spring force to the counterweight impact ring, so that the counterweight impact ring tends to move in the direction of the bearing part.

8. The gas-hydraulic linkage actuator for natural gas transportation pipelines according to claim 7, characterized in that: The counterweight ring is provided with a toothed structure; The impact support column is fitted with a one-way rotating sleeve, and a single-unit pawl is fixedly installed on the one-way rotating sleeve. When the one-way rotating sleeve rotates one revolution, the single-unit pawl can engage with the tooth structure within a certain angle and move the counterweight impact ring once.

9. The gas-hydraulic linkage actuator for natural gas transportation pipelines according to claim 8, characterized in that: A ratchet assembly is provided between the one-way rotating sleeve and the impact support column. The ratchet assembly limits the one-way rotating sleeve, so that the one-way rotating sleeve can only rotate in one direction.

10. The gas-hydraulic linkage actuator for natural gas transportation pipelines according to claim 8, characterized in that: An oblique toothed ring is fixedly provided on the unidirectional rotating sleeve, and a mating push tooth is provided below the counterweight block. A downward support part and an upward elastic part are fixedly provided on the mating push tooth. The mating pusher is fixedly connected to the lower surface of the counterweight block through the upward elastic part. When the counterweight block moves down, the downward support part supports the lower surface of the counterweight block, so that the mating pusher squeezes and drives the oblique gear ring, causing the unidirectional rotating sleeve to rotate.

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