A self-pressure-driven self-sealing valve

Abstract

The present invention discloses a self-pressure-driven self-sealing valve, which includes a valve body and an actuator. A valve stem and a valve plate are rotatably arranged inside the valve body. The output end of the actuator is power-connected to the valve stem, and a bushing is arranged at the position where the valve stem is in rotational contact with the valve body. The actuator includes a driving mechanism with a crank-link structure, a speed reduction mechanism for reducing the output shaft of the driving mechanism, and an adjustment mechanism for driving the bushing to rotate. The driving mechanism includes a central shaft and an eccentric wheel fixed to the central shaft, and five or seven groups of piston crank-link mechanisms for driving the eccentric wheel to rotate are arranged in a circular array outside the central shaft. This self-pressure-driven self-sealing valve is driven by the pressure in the pipeline, reducing the input of additional power, lowering the overall energy consumption, effectively reducing the local wear of the valve stem, and improving the sealing performance of the sealing surface.

Description

Technical Field

[0001] The present invention relates to the technical field of valves, and particularly to a self-pressure-driven self-sealing valve. Background Art

[0002] In large-diameter application scenarios, such as the bottom discharge pipeline of chemical storage tanks and the bottom drainage pipeline of hydropower stations, large-diameter valves are required. When they work, the single pressure is relatively large, and the driving force required for opening is relatively large. In the prior art, external hydraulic or electric motors are mostly used for driving, and a speed reduction mechanism is used to reduce the speed and increase the torque to drive the rotation of the valve stem of the valve. Since the opening frequency of the valve in such scenarios is not high, and the driving force required at the moment of opening is relatively large, the instantaneous energy consumption is huge. There are major difficulties in the laying and load-bearing capacity of the power grid and the safety acceptance of the working conditions. For example, high-voltage points are prohibited from being laid in chemical storage areas, and the space occupied by external hydraulic equipment is relatively large, and the construction difficulty is relatively large. Moreover, since the actual rotation angle of the valve opening and closing is 90°, there is a serious local wear on the force contact surface between the valve stem and the valve body. When used for a long time, the runout of the rotation axis of the valve stem increases, resulting in a decrease in the sealing performance of the sealing surface of the valve and a risk of leakage. Therefore, a valve with low energy consumption, convenient infrastructure construction, reduced local wear, and guaranteed sealing performance should be developed. Summary of the Invention

[0003] The technical problem to be solved by the present invention is to overcome the existing defects, and provide a self-pressure-driven self-sealing valve, which uses the pressure in the pipeline for driving, reduces the input of additional power, reduces the overall energy consumption, effectively reduces the local wear of the valve stem, and improves the sealing performance of the sealing surface, and can effectively solve the problems in the background art.

[0004] To achieve the above object, the present invention provides the following technical solution: A self-pressure-driven self-sealing valve, including a valve body and an actuator. A valve stem and a valve plate are rotatably arranged inside the valve body. The output end of the actuator is in power connection with the valve stem. A bushing is arranged at the position where the valve stem is in rotational contact with the valve body.

[0005] The actuator includes a driving mechanism of a crank and connecting rod structure, a speed reduction mechanism for reducing the output shaft of the driving mechanism, and an adjustment mechanism for driving the bushing to rotate.

[0006] The driving mechanism includes a central shaft and an eccentric wheel fixed to the central shaft. Five or seven piston crank and connecting rod mechanisms for driving the eccentric wheel to rotate are arranged in a circular array outside the central shaft.

[0007] It further includes a regulation mechanism for changing the movement of the pistons in different piston crank and connecting rod mechanisms. The high-pressure medium inlet of the regulation mechanism is communicated with the high-pressure port of the valve body through a high-pressure pipe. A stop valve is arranged at the low-pressure medium outlet of the regulation mechanism.

[0008] The speed reduction mechanism includes a sun gear, planet gears, a planet gear carrier, and an internal gear ring arranged in a planetary speed reduction structure. The sun gear is coaxially and fixedly connected to the central shaft, and the output shaft of the planet gear carrier is coaxially connected to the valve stem.

[0009] It further includes an adjustment mechanism for driving the bushing to rotate, including an external gear disc driven to rotate unidirectionally by the planet gear carrier. The bushing is power-connected to the external gear disc through a worm and worm gear speed reduction mechanism.

[0010] As a preferred technical solution of the present invention, the piston crank connecting rod mechanism includes a reciprocating piston and a connecting rod hinged to the piston. All the ends of the connecting rods are jointly hinged to a driving sleeve, and the driving sleeve is rotatably installed with an eccentric wheel.

[0011] As a preferred technical solution of the present invention, the control mechanism includes an oil pressure chamber. The circumferential surface of the oil pressure chamber is uniformly provided with high-pressure oil pipes respectively communicating with each piston cylinder where each piston is located. A distribution oil shaft and a driving motor for driving the distribution oil shaft to rotate are rotatably arranged in the oil pressure chamber. When the distribution oil shaft rotates, the same high-pressure oil pipe alternately communicates with the high-pressure chamber and the low-pressure chamber in the oil pressure chamber.

[0012] As a preferred technical solution of the present invention, the distribution oil shaft includes a shaft body rotatably and sealingly installed with the oil pressure chamber, and a partition for dividing the oil pressure chamber into a high-pressure chamber and a low-pressure chamber; the shaft body is fixedly connected to the partition, two groups of annular grooves are provided on the circumferential surface of the shaft body, and each group of annular grooves is separately communicated with one side of the partition, and high-pressure pipes corresponding to the two groups of annular grooves are provided on the side wall of the oil pressure chamber.

[0013] As a preferred technical solution of the present invention, the external gear disc is rotatably installed relative to the central shaft. A check tooth connected by an elastic member and capable of floating up and down is provided on the upper end surface of the external gear disc. When the planet gear carrier rotates forward, it can engage with the check tooth to drive the external gear disc to rotate. When the planet gear carrier rotates backward, the check tooth floats downward, and the external gear disc does not rotate with the planet gear carrier; a worm is arranged outside the external gear disc through gear pair transmission, and a worm gear ring is coaxially arranged outside the bushing, and the worm gear ring is meshingly installed with the worm.

[0014] As a preferred technical solution of the present invention, a relay gear is meshingly installed outside the external gear disc, and the lower end of the relay gear is power-connected to the worm through a bevel gear pair.

[0015] Compared with the prior art, the beneficial effects of the present invention are as follows: The self-pressurized driving self-sealing valve uses a high-pressure pipeline to divert the pressure in the high-pressure area of the valve to the driving mechanism of the crank-link structure to obtain a low-speed and high-torque power output. The energy consumption source is the pressure in the pipeline, and no external driving power input is required. Moreover, the rotation direction of the driving mechanism can be changed by changing the regulating mechanism, and the regulating mechanism only needs a small force to drive, effectively reducing the construction difficulty. At the same time, an adjustment mechanism is added inside to apply a rotational torque to the bushing, that is, every time the valve opens and closes, a driving amount of one-way rotation is applied to the bushing, driving the bushing to rotate a small angle. Since the hardness and wear resistance of the bushing are lower than those of the valve stem, when the two rub against each other, the bushing is preferentially worn, and through the rotation of the bushing, local excessive wear is avoided, thus effectively ensuring the sealing performance at the sealing surface of the valve plate. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 is a schematic structural diagram of the present invention;

[0017] Figure 2 is a schematic oil circuit diagram of the driving mechanism and the regulating mechanism of the present invention;

[0018] Figure 3 is a sectional view of the execution part of the present invention;

[0019] Figure 4 is a schematic diagram of the execution part of the present invention;

[0020] Figure 5 is a schematic diagram of the driving part of the present invention;

[0021] Figure 6 is a schematic diagram of the deceleration part of the present invention;

[0022] Figure 7 is a schematic diagram of the adjustment mechanism of the present invention;

[0023] Figure 8 is another angle schematic diagram of the adjustment mechanism of the present invention;

[0024] Figure 9 is a schematic diagram of the regulating mechanism of the present invention.

[0025] In the figure: 1. Valve body; 101. Valve stem; 2. Deceleration mechanism; 201. Internal gear ring; 202. Planet gear; 203. Planet gear carrier; 204. Sun gear; 3. Driving mechanism; 301. Eccentric wheel; 302. Driving sleeve; 303. Piston; 304. Connecting rod; 305. Central shaft; 306. Piston cylinder; 4. Adjustment mechanism; 401. Check tooth; 402. Worm gear ring; 403. Relay gear; 404. Worm; 405. External tooth disc; 5. Bushing; 6. Regulating mechanism; 601. Oil pressure chamber; 602. Oil distribution shaft; 603. Driving motor. DETAILED DESCRIPTION OF THE INVENTION

[0026] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts belong to the scope of protection of the present invention.

[0027] Please refer to Figures 1 - 4 , the present invention provides a technical solution: a self-pressurized drive self-sealing valve, including a valve body 1 and an actuator. A valve stem 101 and a valve plate are rotatably arranged inside the valve body 1. The output end of the actuator is power-connected to the valve stem 101. A bushing 5 is arranged at the position where the valve stem 101 is in rotational contact with the valve body 1;

[0028] The actuator includes a drive mechanism 3 of a crank-link structure, a reduction mechanism 2 for reducing the speed of the output shaft of the drive mechanism 3, and an adjustment mechanism 4 for driving the bushing 5 to rotate;

[0029] The drive mechanism 3 includes a central shaft 305 and an eccentric wheel 301 fixed to the central shaft 305. Five or seven groups of piston crank-link mechanisms for driving the eccentric wheel 301 to rotate are arranged in a circular array outside the central shaft 305;

[0030] It further includes a regulation mechanism 6 for changing the movement of the pistons in different groups of piston crank-link mechanisms. The high-pressure medium inlet of the regulation mechanism 6 is communicated with the high-pressure port of the valve body 1 through a high-pressure pipe. A stop valve is arranged at the low-pressure medium outlet of the regulation mechanism 6;

[0031] Refer to Figure 6 , the reduction mechanism 2 includes a sun gear 204, a planet gear 202, a planet gear carrier 203, and an internal gear ring 201 arranged in a planetary reduction structure. The sun gear 204 is coaxially and fixedly connected to the central shaft 305. The output shaft of the planet gear carrier 203 is coaxially connected to the valve stem 101;

[0032] It further includes an adjustment mechanism 4 for driving the bushing 5 to rotate, including an external gear disk 405 driven to rotate unidirectionally by the planet gear carrier 203. The bushing 5 is power-connected to the external gear disk 405 through a worm and gear reduction mechanism.

[0033] Refer to Figure 5 , the piston crank-link mechanism includes a reciprocating piston 303 and a connecting rod 304 hinged to the piston 303. The ends of all the connecting rods 304 are jointly hinged to a drive sleeve 302, and the drive sleeve 302 is rotatably installed on the eccentric wheel 301.

[0034] Refer to Figure 2, the regulating mechanism 6 includes an oil pressure chamber 601. The circumferential surface of the oil pressure chamber 601 is uniformly provided with high-pressure oil pipes that are respectively communicated with each piston cylinder 306 where each piston 303 is located. An oil distribution shaft 602 and a driving motor 603 for driving the oil distribution shaft 602 to rotate are rotatably arranged in the oil pressure chamber 601. When the oil distribution shaft 602 rotates, the same high-pressure oil pipe is alternately communicated with the high-pressure chamber and the low-pressure chamber in the oil pressure chamber 601.

[0035] Refer to Figure 9 , the oil distribution shaft 602 includes a shaft body rotatably and sealingly installed in the oil pressure chamber 601, and a partition plate for dividing the oil pressure chamber 601 into a high-pressure chamber and a low-pressure chamber; the shaft body is fixedly connected to the partition plate. Two groups of annular grooves are arranged on the circumferential surface of the shaft body, and each group of annular grooves is separately communicated with one side of the partition plate, and high-pressure pipes corresponding to the two groups of annular grooves are arranged on the side wall of the oil pressure chamber 601.

[0036] Refer to Figure 7 and Figure 8 , the outer gear disk 405 is rotatably installed relative to the middle shaft 305. A check tooth 401 that is connected by an elastic member and can float up and down is arranged on the upper end surface of the outer gear disk 405. When the planet gear carrier 203 rotates forward, it can engage with the check tooth 401 to drive the outer gear disk 405 to rotate. When the planet gear carrier 203 rotates reversely, the check tooth 401 floats downward, and the outer gear disk 405 does not rotate with the planet gear carrier 203; a worm 404 is arranged outside the outer gear disk 405 through gear pair transmission. A worm gear ring 402 is coaxially arranged outside the bushing 5, and the worm gear ring 402 is meshed and installed with the worm 404.

[0037] A relay gear 403 is meshed and installed outside the outer gear disk 405, and the lower end of the relay gear 403 is power-connected to the worm 404 through a bevel gear pair.

[0038] During use: When designing a valve body with a large diameter, it is necessary to consider the force on the valve plate and the rigidity of the valve stem in the closed state to avoid problems such as the rearward movement of the sealing surface of the valve plate caused by the force on the valve plate or wear of the valve stem, resulting in gaps at the sealing surface; and for the chemical industry, the stored media often have problems of inflammability and explosiveness, and the on-site safety requirement level is relatively high. Therefore, when using electric drive for such high-torque valves, strict protection is required to avoid the electric sparks generated during the starting process of the motor. Its protection level is relatively high and the cost is relatively large; for the scenarios used in hydropower stations, the infrastructure space is limited, and there are relatively large limitations for the construction of high-voltage power grids and transformers;

[0039] Therefore, the present invention uses the pressure of the cold fluid in the high-pressure cavity of the valve to drive the valve actuator. The driving part is composed of a piston 303, a connecting rod 304, an eccentric wheel 301 and a regulating mechanism 6 to form a hydraulic motor with a crank connecting rod structure, which has the characteristics of low speed and large torque, and is assisted by a reduction mechanism 2 with a planetary structure to reduce the speed, so as to obtain an ultra-large torque to meet the opening torque requirement of the valve.

[0040] A stop valve is provided at the low-pressure medium outlet of the regulating mechanism 6. When the stop valve is closed, the pressures in the high-pressure area and the low-pressure area in the regulating mechanism 6 are nearly equal. At this time, the oil distribution shaft 602 in the regulating mechanism 6 stops rotating at the same time, and the rotation of the driving mechanism 3 is inhibited by its own oil pressure, that is, reverse braking, to control the rotation of the valve stem 101, so as to realize arbitrary control and hovering of the opening amount of the valve plate, and improve the flexibility of valve control.

[0041] During operation, a driving motor 603 is used to drive the oil distribution shaft 602 to rotate. At this time, the medium in the high-pressure cavity of the valve enters the high-pressure area of the oil pressure cavity 601, and then enters the piston cylinder 306 communicated with the high-pressure area, pushing the corresponding piston 303 to move. As the oil distribution shaft 602 rotates, the position of the high-pressure area changes, and at the same time, the piston cylinder 306 communicated with the high-pressure area changes, pushing the piston 303 at the corresponding position to move, while the previously communicated piston cylinder 306 is communicated with the low-pressure area, and the piston 303 at this place is reset. During the reciprocating movement of the piston 303, through the power transmission of the connecting rod 304, the driving sleeve 302 and the eccentric wheel 301 are driven to rotate, and the speed is reduced and the torque is increased through the reduction mechanism 2 with a planetary structure to further expand the output torque, solve the driving problem when the pressure is low at the high-pressure cavity of the valve. At the same time, when the planet carrier 203 of the reduction mechanism 2 rotates, it engages with the check teeth 401 on the end face of the lower external gear disc 405, driving the external gear disc 405 to rotate unidirectionally. The external gear disc 405 meshes with the relay gear 403, driving the relay gear 403 to rotate unidirectionally. The relay gear 403 is coaxially provided with a bevel gear, which meshes with the bevel gear at the end of the worm 404, driving the worm 404 to rotate. The worm 404 meshes with the worm gear ring 402, driving the worm gear ring 402 to rotate unidirectionally, driving the bushing 5 to rotate unidirectionally relative to the valve body 1, and through the secondary reduction of the worm and worm gear reduction mechanism, the output torque is further increased. And when the valve is opened once, the rotation amount of the bushing 5 is extremely small, and the wear between the bushing 5 and the valve body 1 itself can be ignored, while the wear position between the valve stem 101 and the bushing 5 changes. At the same time, in combination with the material selection between the valve stem 101 and the bushing 5, the worn bushing is preferably selected to reduce the loss of the valve stem 101. Through the rotation of the bushing 5, the inner diameter surface of the bushing 5 is evenly worn, avoiding the problem of the sealing performance of the valve plate sealing surface decreasing due to serious local wear, and effectively improving the service life of the valve.

[0042] At the same time, the actuator of the present application can be applied not only to butterfly valves, but also to valves that are opened and closed by rotation, such as ball valves and semi-spherical valves.

[0043] Although embodiments of the present invention have been shown and described, it will be understood by those of ordinary skill in the art that various changes, modifications, substitutions and variations can be made to these embodiments without departing from the principles and spirit of the present invention, and the scope of the present invention is defined by the appended claims and their equivalents.

Claims

1. A self-pressure-driven self-sealing valve, comprising a valve body (1) and an actuator. A valve stem (101) and a valve plate are rotatably arranged inside the valve body (1). The output end of the actuator is power-connected to the valve stem (101). A bushing (5) is arranged at the position where the valve stem (101) is in rotational contact with the valve body (1). It is characterized in that: The actuator includes a driving mechanism (3) of a crank and connecting rod structure, a speed reduction mechanism (2) for reducing the speed of the output shaft of the driving mechanism (3), and an adjusting mechanism (4) for driving the bushing (5) to rotate; The driving mechanism (3) includes a central shaft (305) and an eccentric wheel (301) fixed to the central shaft (305). Five or seven groups of piston crank and connecting rod mechanisms for driving the eccentric wheel (301) to rotate are arranged in a circular array outside the central shaft (305). It further includes a control mechanism (6) for changing the movement of the pistons in different groups of piston crank and connecting rod mechanisms. The high-pressure medium inlet of the control mechanism (6) is communicated with the high-pressure port of the valve body (1) through a high-pressure pipe. A stop valve is arranged at the low-pressure medium outlet of the control mechanism (6); The speed reduction mechanism (2) includes a sun gear (204), planet gears (202), a planet gear carrier (203), and an internal gear ring (201) arranged in a planetary reduction structure. The sun gear (204) is coaxially and fixedly connected to the central shaft (305). The output shaft of the planet gear carrier (203) is coaxially connected to the valve stem (101); It further includes an adjusting mechanism (4) for driving the bushing (5) to rotate, including an external gear disk (405) driven to rotate unidirectionally by the planet gear carrier (203). The bushing (5) is power-connected to the external gear disk (405) through a worm and worm gear reduction mechanism.

2. The self-pressure-driven self-sealing valve according to claim 1, It is characterized in that: The piston crank and connecting rod mechanism includes a reciprocating piston (303) and a connecting rod (304) hinged to the piston (303). The ends of all the connecting rods (304) are jointly hinged to a driving sleeve (302). The driving sleeve (302) is rotatably installed on the eccentric wheel (301).

3. The self-pressure-driven self-sealing valve according to claim 2, It is characterized in that: The control mechanism (6) includes an oil pressure chamber (601). High-pressure oil pipes communicating with the respective piston cylinders (306) where the pistons (303) are located are uniformly arranged on the circumferential surface of the oil pressure chamber (601). A distribution shaft (602) and a driving motor (603) for driving the distribution shaft (602) to rotate are rotatably arranged in the oil pressure chamber (601). When the distribution shaft (602) rotates, the same high-pressure oil pipe communicates with the high-pressure chamber and the low-pressure chamber in the oil pressure chamber (601) alternately.

4. The self-pressure-driven self-sealing valve according to claim 3, It is characterized in that: The oil distribution shaft (602) includes a shaft body rotatably and sealingly installed in the oil pressure chamber (601), and a partition plate for dividing the oil pressure chamber (601) into a high-pressure chamber and a low-pressure chamber; the shaft body is fixedly connected to the partition plate, two groups of annular grooves are provided on the circumferential surface of the shaft body, and each group of annular grooves is separately communicated with one side of the partition plate, and high-pressure pipes respectively corresponding to and communicated with the two groups of annular grooves are provided on the side wall of the oil pressure chamber (601).

5. The self-pressure-driven self-sealing valve according to claim 1, characterized in that: The outer tooth disc (405) is rotatably installed relative to the middle shaft (305), a check tooth (401) connected by an elastic member and capable of floating up and down is arranged on the upper end surface of the outer tooth disc (405), when the planet gear carrier (203) rotates forward, it can be combined with the check tooth (401) to drive the outer tooth disc (405) to rotate, when the planet gear carrier (203) rotates reversely, the check tooth (401) floats downward, and the outer tooth disc (405) does not rotate with the planet gear carrier (203); a worm (404) is arranged outside the outer tooth disc (405) through gear pair transmission, a worm gear ring (402) is coaxially arranged outside the bushing (5), and the worm gear ring (402) is meshingly installed with the worm (404).

6. The self-pressure-driven self-sealing valve according to claim 5, characterized in that: A relay gear (403) is meshingly installed outside the outer tooth disc (405), and the lower end of the relay gear (403) is power-connected to the worm (404) through a bevel gear pair.

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