Multi-rotation type valve gear box and using method thereof

Abstract

The invention provides a multi-rotation type valve gear box and a using method thereof, and belongs to the technical field of gear boxes, the gear box comprises a box body, a transmission shaft and a driving shaft, a driven bevel gear is arranged on the transmission shaft, a driving bevel gear is arranged at one end of the driving shaft, an oil storage cavity is formed in the end of the driving bevel gear, and a fixing shaft is arranged in the box body; one end of the fixing shaft extends into the oil storage cavity, an oil channel communicated with the oil storage cavity is formed in the fixing shaft, a plurality of first channels are formed in the driving bevel gear in the circumferential direction in a penetrating mode, the outlet ends of the first channels are located at the tooth root portions of adjacent teeth on the driving bevel gear, and a first oil way communicated with an inner cavity of the box body and a second oil way communicated with the oil channel are arranged on the box body. And the first oil way and the second oil way are respectively connected in series with an opening control valve. According to the invention, it can be ensured that the lubricating oil more effectively and uniformly covers the tooth surface needing to be lubricated, especially when the gear rotates at a high speed or bears a high load, a stable lubricating oil film can be formed, and gear wear is significantly reduced.

Description

Technical Field

[0001] This invention relates to the field of gearbox technology, specifically to a multi-turn valve gearbox and its usage method. Background Technology

[0002] Multi-turn gearboxes, as a key reduction mechanism widely used in multi-turn valves such as gate valves, globe valves, sluice gates, and sluice gates, play an important role in power, oil and gas, water treatment, and conventional industrial process control. Their main function is to achieve precise opening and closing control of valves through manual or electric operation, according to on-site requirements.

[0003] The applicant's earlier application, publication number CN220354612U, disclosed an economical multi-turn valve gearbox. This gearbox only inputs lubricating oil through an oil inlet located at the top of the housing corresponding to the position of the driving bevel gear, lubricating the meshing surfaces of the driving and driven bevel gears. This single and passive lubrication method results in the lubricating oil failing to effectively and evenly cover all the tooth surfaces requiring lubrication. Especially when the gears are operating at high speeds or under high loads, the lubricating oil film is prone to rupture, thus accelerating gear wear and reducing the gearbox's service life and operating efficiency. Summary of the Invention

[0004] The purpose of this invention is to overcome the shortcomings and deficiencies of the existing technology and to provide a multi-turn valve gearbox and its usage method.

[0005] The technical solution adopted by the present invention is as follows: In a first aspect, this application provides a multi-turn valve gearbox, including a housing, a transmission shaft rotatably disposed laterally on the housing, and a drive shaft rotatably disposed longitudinally on the housing. A driven bevel gear is disposed on the transmission shaft for connection with an actuator. One end of the drive shaft is provided with a driving bevel gear meshing with the driven bevel gear for connection with a valve stem. An oil storage chamber is opened at the end of the driving bevel gear. A fixed shaft is disposed inside the housing, one end of which extends into the oil storage chamber and has an oil passage communicating with the oil storage chamber. A plurality of first channels are provided circumferentially on the driving bevel gear. The outlet end of the first channel is located at the root of the adjacent tooth on the driving bevel gear. A first oil passage communicating with the inner cavity of the housing and a second oil passage communicating with the oil passage are provided on the housing. The first oil passage and the second oil passage are connected in series with an opening control valve.

[0006] In some embodiments, a linkage disc is coaxially arranged on the fixed shaft and the oil storage cavity. The linkage disc includes a circumferential linkage surface, on which a plurality of grooves are evenly arranged. A movable block is slidably arranged in the first channel. The movable block slides in contact with the circumferential linkage surface. Springs are arranged between its two ends and the inner wall of the first channel. A first oil groove is opened on its two side walls. A second oil groove is opened on the two side walls of the first channel and communicates with the inner cavity of the housing. The movable block has a first position abutting against the groove and a second position sliding out of the groove. When it is in the first position, the first oil groove and the oil storage cavity are connected and the second oil groove is isolated. When it is in the second position, the first oil groove and the oil storage cavity are isolated and the second oil groove is connected. When the valve is opened and closed by the actuator, the transmission shaft drives the active bevel gear to rotate relative to the linkage disc, so that the movable block switches between the first position and the second position, and delivers the lubricating oil in the oil storage cavity to the tooth surface of the active bevel gear.

[0007] In some embodiments, the linkage disk is located in the middle of the moving block and includes at least two linkage plates spaced apart. The circumferential linkage surface is the outer contour surface of the linkage plate. The number of grooves is the same as that of the moving block and they are evenly distributed on the outer contour surface. One of the grooves is located at the lowest part of the outer contour surface in the vertical direction.

[0008] In some embodiments, when the moving block is in the first position, the outer end face of the moving block is lower than the outer tooth surface of the driving bevel gear; when the moving block is in the second position, the outer end face of the moving block does not exceed the outer tooth surface of the driving bevel gear.

[0009] In some embodiments, the side wall of the first oil tank near the second oil tank is configured as an oil guiding slope, and the side of the oil guiding slope near the linkage plate is inclined toward the second oil tank.

[0010] In some embodiments, an annular baffle is provided on one side of the oil storage cavity near its opening end, the outer ring of the annular baffle is in close contact with the inner wall of the oil storage cavity, and the diameter of its inner ring is larger than the outer diameter of the fixed shaft.

[0011] In some embodiments, the open end of the oil storage chamber is rotatably mounted on the inner wall of the housing via a rotary bearing, the rotary bearing being located on the side of the annular baffle away from the linkage disc.

[0012] In some embodiments, a lubricating oil circulation system is also included. The bottom of the tank is provided with an oil drain port. The lubricating oil circulation system includes a lubricating oil storage device, an oil inlet circuit and an oil outlet circuit. The oil inlet circuit is connected to the oil filling port, and the oil outlet circuit is connected to the oil drain port. A recovery control valve and a discharge pump are provided on the oil outlet circuit. An input pump is provided on the oil inlet circuit.

[0013] Secondly, this application provides a method of using the aforementioned multi-turn valve gearbox, comprising the following steps: The real-time torque value T of the drive shaft is collected by a torque sensor. When T ≤ rated torque, the opening of the first oil circuit is dynamically adjusted to follow the change of T, while the second oil circuit maintains the basic opening. When T > rated torque, the first oil circuit is controlled to open to the maximum opening, and the opening of the second oil circuit is dynamically adjusted according to the change of T. The lubricating oil level in the internal cavity of the tank is monitored in real time by a liquid level sensor, and the lubricating oil level is controlled within a preset range by the oil input and discharge circuits.

[0014] In some embodiments, long-term shutdown start-up control is also included, comprising the following steps: The duration of a single shutdown of the gearbox is obtained. If the duration of a single shutdown exceeds a preset threshold, it is determined that the gearbox has not been started for a long time. When the gearbox actuator receives the opening and closing command, it first controls the opening of the second oil circuit to supply oil continuously at the maximum opening for a preset time, and simultaneously opens the first oil circuit to supply oil at the basic opening until the oil supply of the second oil circuit reaches the preset amount. The actuator is started and the starting torque value is monitored in real time by the torque sensor. A mapping model of shutdown time, starting torque value and preset amount is established. The preset amount is optimized and adjusted in real time based on the starting torque value so that the subsequent preset amount directly matches the output value of the model.

[0015] The beneficial effects of this invention are as follows: Compared with the single and passive oil injection method in the prior art, this invention can ensure that the lubricating oil covers the tooth surface that needs lubrication more effectively and evenly. Especially when the gears are running at high speed or under high load, a stable lubricating oil film can be formed, significantly reducing gear wear. By connecting the opening control valves in series with the first and second oil circuits, the supply amount and supply path of the lubricating oil can be flexibly adjusted according to the actual working conditions, further optimizing the lubrication effect. Attached Figure Description

[0016] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, obtaining other drawings based on these drawings without creative effort still falls within the scope of the present invention.

[0017] Figure 1 This is a schematic diagram of a multi-turn valve gearbox according to the present invention; Figure 2 for Figure 1 Enlarged view of point A in the middle; Figure 3 This is a partial schematic diagram of a multi-turn valve gearbox according to the present invention. Figure 1 ; Figure 4 This is a partial schematic diagram of a multi-turn valve gearbox according to the present invention. Figure 2 ; Figure 5 This is a cross-sectional view of the driving bevel gear in this invention.

[0018] Icon labels: 1-Box body, 2-Drive shaft, 3-Drive shaft, 4-Driven bevel gear, 5-Driven bevel gear, 6-Fixed shaft, 7-First oil passage, 8-Second oil passage, 9-Opening control valve, 10-Moving block, 11-Spring, 12-First oil groove, 13-Second oil groove, 14-Annular baffle, 15-Rotary bearing, 16-Oil outlet, 17-Lubricating oil storage device, 18-Input oil passage, 19-Output oil passage, 20-Receipt control valve, 21-Output pump, 22-Input pump, 120-Guide slope, 500-Oil storage chamber, 501-First channel, 600-Oil passage, 610-Circumferential linkage surface, 611-Groove, 612-Linkage plate, 613-Outer contour surface. Detailed Implementation

[0019] The following description provides specific application scenarios and requirements for this specification, intended to enable those skilled in the art to make and use the contents of this specification. Various partial modifications to the disclosed embodiments will be apparent to those skilled in the art, and the general principles defined herein can be applied to other embodiments and applications without departing from the spirit and scope of this specification. Therefore, this specification is not limited to the embodiments shown, but rather to the widest scope consistent with the claims.

[0020] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "longitudinal", "lateral", "radial", "length", "width", "thickness", "upper", "lower", "left", "right", "front", "rear", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These terms are mainly for the purpose of better describing this application and its embodiments, and are not intended to limit the indicated device, element or component to have a specific orientation, or to be constructed and operated in a specific orientation.

[0021] It should be noted that the terms "first," "second," and similar words do not indicate any order, quantity, or importance, but are only used to distinguish different components and should not be construed as limiting the embodiments of this application.

[0022] It should be noted that the terms "installation," "setup," "equipped with," "connection," and "connected" should be interpreted broadly. For example, they can refer to fixed connections, detachable connections, or integral structures; they can refer to mechanical connections or electrical connections; they can refer to direct connections or indirect connections through an intermediate medium, or internal connections between two devices, components, or parts.

[0023] It should be noted that the terms "in some embodiments," "exemplarily," and "for example" are used to indicate examples, illustrations, or descriptions. Any embodiment or design described in this application as "in some embodiments," "exemplarily," or "for example" should not be construed as being more preferred or advantageous than other embodiments or designs. Specifically, the use of terms such as "in some embodiments," "exemplarily," and "for example" is intended to present related concepts in a specific manner, meaning that a particular feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of this application. The appearance of the above terms in various places in the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment mutually exclusive with other embodiments. Those skilled in the art will explicitly and implicitly understand that the embodiments described herein can be combined with other embodiments.

[0024] Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0025] Regarding the accompanying drawings of this application, it should be clearly understood that the drawings are for illustrative and descriptive purposes only and are not intended to limit the scope of this specification. It should also be understood that the drawings are not necessarily drawn to scale.

[0026] like Figures 1 to 5 As shown, this application provides a multi-turn valve gearbox, including a housing 1, a transmission shaft 2 rotatably disposed laterally on the housing 1, and a drive shaft 3 rotatably disposed longitudinally on the housing 1. A driven bevel gear 4 is disposed on the transmission shaft 2 for connecting with an actuator. One end of the drive shaft 3 is provided with a driving bevel gear 5 that meshes with the driven bevel gear 4 for connecting with a valve stem. An oil storage chamber 500 is opened at the end of the driving bevel gear 5, which can be an annular cavity, and its internal space is used to store lubricating oil.

[0027] A fixed shaft 6 is provided inside the housing 1. One end of the fixed shaft 6 is coaxially arranged with the oil storage cavity 500 and extends into the oil storage cavity 500. An oil passage 600 communicating with the oil storage cavity 500 is provided inside the fixed shaft 6, so that lubricating oil can be transported from the fixed shaft 6 to the oil storage cavity 500. The oil passage 600 can be arranged to run through the fixed shaft 6 axially or radially.

[0028] The driving bevel gear 5 has a plurality of first channels 501 arranged circumferentially therethrough. The outlet end of the first channel 501 is located at the root of the adjacent teeth on the driving bevel gear 5. These channels can be evenly distributed on the circumference of the driving bevel gear 5 to ensure that the lubricating oil can be evenly delivered to each tooth surface. It can be understood that the shape and number of the first channels 501 can also be adjusted according to the tooth profile and lubrication requirements of the driving bevel gear 5. For example, circular, elliptical, rectangular channels, long narrow slits, or racetrack-shaped through holes can be used, and the number of channels can be determined according to the size of the gear and the working conditions. For example, one or more channels can be arranged at intervals at the root of adjacent teeth.

[0029] The housing 1 is provided with a first oil passage 7 that communicates with the inner cavity of the housing 1 and a second oil passage 8 that communicates with the oil channel 600. The first oil passage 7 and the second oil passage 8 are connected in series with an opening control valve 9. The first oil passage 7 and the second oil passage 8 are the delivery paths of the lubricating oil, while the opening control valve 9 is used to regulate the flow rate of the lubricating oil. The opening control valve 9 can be an electric valve, a pneumatic valve or a solenoid valve, etc., used to accurately control the flow rate of the lubricating oil, and preferably a control valve suitable for lubricating oil delivery.

[0030] It is understandable that the pipe diameter and layout of the first oil passage 7 and the second oil passage 8 can be optimized according to the overall structure of the gearbox and the delivery distance of the lubricating oil in order to reduce fluid resistance and improve lubrication efficiency.

[0031] The above settings ensure efficient and precise lubrication of the meshing surfaces of key gears in multi-rotation gearboxes, effectively solving the problem in existing technologies where lubricating oil cannot effectively and evenly cover the tooth surface, leading to gear wear and reduced lifespan.

[0032] Meanwhile, the traditional lubrication method is the same as the first oil passage 7. The second oil passage 8 of this application outputs lubricating oil from inside the active bevel gear 5 to its tooth surface, which is more efficient and precise, and greatly improves the lubrication effect on the gear meshing surface.

[0033] Furthermore, as the driving bevel gear 5 rotates, the lubricating oil in the oil reservoir 500 is transported to the root of the adjacent teeth on the driving bevel gear 5 through a plurality of first channels 501 arranged circumferentially by centrifugal force or pressure. The first channels 501 enable the lubricating oil to act directly on the key area of ​​gear meshing, thereby providing continuous and effective lubrication to the meshing tooth surfaces of the driving bevel gear 5 and the driven bevel gear 4.

[0034] Furthermore, based on the fact that the first channel 501 is an elongated hole located at the root of the adjacent teeth of the active bevel gear 5, a linkage disk 61 is coaxially arranged on the fixed shaft 6 and the oil storage cavity 500. The linkage disk 61 includes a circumferential linkage surface 610, on which a plurality of grooves 611 are evenly arranged. A moving block 10 is slidably arranged in the first channel 501. Preferably, in this application, four moving blocks 10 and four grooves 611 are configured in a cross shape. The moving block 10 slides in contact with the circumferential linkage surface 610, and springs 11 are provided between its two ends and the inner wall of the first channel 501. A first oil groove 12 is opened on its two side walls, and a second oil groove 13 communicating with the inner cavity of the housing 1 is opened on the two side walls of the first channel 501. Figure 4 As shown, the first channel 501 has side channels at both ends, and the moving block 10 has protrusions at both ends, with positioning holes or positioning pins for positioning springs on the protrusions.

[0035] The movable block 10 has a first position abutting against the groove 611 and a second position sliding out of the groove 611. In the first position, the first oil groove 12 and the oil storage chamber 500 are connected, while the second oil groove 13 is isolated. In the second position, the first oil groove 12 and the oil storage chamber 500 are isolated, while the second oil groove 13 is connected. When the valve is opened or closed by the actuator, the drive shaft 2 drives the active bevel gear 5 to rotate relative to the linkage disc 61, causing the movable block 10 to switch between the first and second positions, thus delivering the lubricating oil in the oil storage chamber 500 to the tooth surface of the active bevel gear 5. Specifically, by introducing the synergistic effect of the linkage disc 61 and the movable block 10, the problem of insufficient lubricating oil delivery efficiency and uniformity in traditional lubrication methods is effectively solved. When the actuator opens or closes the valve, the drive shaft 2 drives the active bevel gear 5 to rotate. Since the linkage disc 61 is fixed, the rotation of the active bevel gear 5 causes the first channel 501 on it and the movable block 10 inside to rotate relative to the linkage disc 61. When the moving block 10 encounters the groove 611 on the circumferential linkage surface 610 of the linkage disk 61 during rotation, the moving block 10 will abut into the groove 611 under the action of the spring, at which point the moving block 10 is in the first position. In the first position, the first oil groove 12 on the moving block 10 is connected to the oil storage chamber 500, thereby allowing the lubricating oil in the oil storage chamber 500 to enter the first channel 501 through the first oil groove 12. As the driving bevel gear 5 continues to rotate, the moving block 10 will slide out of the groove 611, at which point the moving block 10 is in the second position. In the second position, the first oil groove 12 is isolated from the oil storage chamber 500, while the second oil groove 13 is connected to the inner cavity of the housing 1. Due to the rotation of the driving bevel gear 5, centrifugal force will throw the lubricating oil in the first channel 501 out through the second oil groove 13, directly delivering it to the tooth surface of the driving bevel gear. This periodic switching mechanism ensures that the lubricating oil can be continuously and evenly delivered to each tooth surface of the driving bevel gear, thereby effectively improving the lubrication condition of the gear.

[0036] Through the above technical solution, this application achieves efficient and uniform lubrication of the tooth surface of the drive bevel gear, significantly reducing gear wear and extending the service life of the gearbox. Compared with the basic solution that relies solely on the oil reservoir and oil passages for lubrication, this application actively and periodically delivers the lubricating oil in the oil reservoir to the tooth surface through the mechanical linkage of the linkage disc and the moving block, avoiding the problems of lubrication dead zones and insufficient lubrication. This active lubrication mechanism, especially under high-speed or heavy-load operating conditions of the gearbox, can provide more reliable lubrication protection, thereby improving the overall performance and reliability of the multi-turn valve gearbox.

[0037] Preferably, when the moving block 10 is in the first position, the protrusion is also located in the side channel to prevent lubricating oil from flowing in and affecting the spring 11.

[0038] In some implementations, the linkage disk 61 is located in the middle of the moving block 10 and includes at least two spaced linkage plates 612. This means the linkage disk 61 is centrally located along the length of the moving block 10, ensuring that the moving block 10 maintains stable contact with the circumferential linkage surface 610 of the linkage disk 61 when sliding within the first channel 501, thus guaranteeing reliable engagement between the moving block 10 and the groove 611. The linkage plates 612 are thin plates with minimal thickness, preventing lubricating oil from accumulating in the grooves 611 and affecting the linkage with the moving block 10. The circumferential linkage surface 610 is the outer contour surface 613 of the linkage plate 612. The number of grooves 611 is the same as the number of moving blocks 10 and they are evenly distributed on the outer contour surface 613. One groove 611 is located at the lowest point in the vertical direction of the outer contour surface 613. This ensures that during the rotation of the drive bevel gear 5, at least one groove 611 is positioned below the point most favorable for the gravity flow of lubricating oil, thereby assisting in the delivery of lubricating oil.

[0039] In some implementations, when the moving block 10 is in the first position, its outer end face is lower than the outer tooth surface of the driving bevel gear 5; when the moving block 10 is in the second position, its outer end face does not exceed the outer tooth surface of the driving bevel gear 5. This arrangement ensures that the moving block 10 can effectively deliver lubricating oil in different positions without interfering with the normal meshing of the driving bevel gear 5.

[0040] In some implementations, the side wall of the first oil groove 12 near the second oil groove 13 is configured as an oil guiding slope 120. The side of the oil guiding slope 120 near the linkage disc 61 is inclined towards the second oil groove 13. Specifically, the oil guiding slope can be configured as a plane or a curved surface, and its inclination angle can be adjusted according to actual needs to achieve the best oil guiding effect. This configuration can optimize the oil groove structure, guide the lubricating oil to flow more smoothly, and improve lubrication efficiency.

[0041] In some implementations, an annular baffle 14 is provided on the side of the oil storage cavity 500 near its opening end. The outer ring of the annular baffle 14 is in close contact with the inner wall of the oil storage cavity 500, and the diameter of its inner ring is larger than the outer diameter of the fixed shaft 6. It can store a certain amount of lubricating oil in the oil storage cavity 500 for long-term lubrication.

[0042] Furthermore, the open end of the oil storage chamber 500 is rotatably mounted on the inner wall of the housing 1 via a rotary bearing 15. The rotary bearing 15 is located on the side of the annular baffle 14 away from the linkage disc 61. This arrangement not only ensures the stable rotation of the oil storage chamber 500 and improves the output efficiency of the lubricating oil, but also provides rotational positioning for both ends of the drive bevel gear 5, improving its stability during rotation. It should be understood that the drive shaft 2 is also connected to the housing 1 via a rotary bearing.

[0043] In some implementations, the aforementioned multi-turn valve gearbox also includes a lubricating oil circulation system. The bottom of the gearbox 1 has an oil drain port 16. The lubricating oil circulation system includes a lubricating oil storage device 17, an input oil passage 18, and an output oil passage 19. The input oil passage 18 is connected to the oil inlet, and the output oil passage 19 is connected to the oil drain port 16. A recovery control valve 20 and an output pump 21 are installed on the output oil passage 18. An input pump 22 is installed on the input oil passage 18. This configuration allows for the recycling and timely replacement of the lubricating oil. Specifically, the input pump draws lubricating oil from the lubricating oil storage device and injects it into the gearbox through the input oil passage to lubricate the gears. After lubrication, the lubricating oil flows out through the oil drain port, and the output pump draws it out. After filtration and cooling, the lubricating oil is returned to the lubricating oil storage device, thus completing one cycle.

[0044] Regarding the lubricating oil storage device 17, it is preferable to use existing devices that can filter and purify refluxed lubricating oil, such as separation through two steps of coalescence and sedimentation, adsorption separation, centrifugal separation, etc.

[0045] This application provides a method of using the aforementioned multi-turn valve gearbox, including the following steps: The real-time torque value T of drive shaft 2 is collected in real time by a torque sensor; When T ≤ rated torque, it is a low load condition. At this time, the opening of the first oil circuit 7 is dynamically adjusted according to the change of T to avoid the increase in resistance caused by excessive lubrication; the second oil circuit 8 maintains the basic opening to achieve dual oil circuit lubrication.

[0046] Preferably, within the range of T ≤ rated torque, there are low-load and medium-load zones respectively. Under low load, the opening of the first oil circuit increases slowly with T, such as increasing the opening by 5% for every 10% increase in torque, while the second oil circuit maintains its basic opening. Under medium load, the opening of the first oil circuit increases rapidly, such as increasing the opening by 10% for every 10% increase in torque, while the second oil circuit maintains its basic opening. This avoids sudden changes in the oil circuit opening when switching from low load to high load and reduces lubrication fluctuations.

[0047] Regarding the basic opening of the second oil circuit 8, the basic opening of the second oil circuit 8 under low load is bound to the rated torque. For example, the basic opening = 50% of the opening of the first oil circuit corresponding to the rated torque, rather than a fixed value. When the rated torque changes due to wear after long-term operation of the gearbox, the basic opening can automatically adapt, avoiding insufficient lubrication caused by a fixed reference.

[0048] When T > rated torque, it is a high load condition. At this time, the first oil circuit 7 is opened to the maximum opening, and the opening of the second oil circuit 8 is dynamically adjusted according to the change of T. Oil is supplied directly to the gear meshing part through the second oil circuit 8 to achieve rapid lubrication.

[0049] Preferably, when T > rated torque, different adjustment slopes are set according to the torque excess ratio: the more the torque exceeds the standard, the faster the opening of the second oil circuit increases, and the more accurately the lubrication demand gradient under high load is matched.

[0050] During the above adjustment, the level of lubricating oil inside the housing 1 is monitored in real time by a level sensor, and the lubricating oil level is controlled within a preset range through the input oil passage 18 and the discharge oil passage 19. The preset range includes an upper limit and a lower limit of the oil level. It can be understood that the upper limit of the oil level should be less than the actual maximum oil level of the gearbox, generally 70%-90% of the actual maximum oil level, so that there is sufficient oil level space for adjustment by the first oil passage 7 and the second oil passage 8.

[0051] By using the above methods, the supply of lubricating oil can be dynamically adjusted according to the actual operating conditions of the gearbox, thereby ensuring that the gearbox can obtain the best lubrication effect under various operating conditions, extending the service life of the gearbox, and improving the reliability of the gearbox.

[0052] Furthermore, it also includes long-term shutdown start-up control, comprising the following steps: The duration of a single shutdown of the gearbox is obtained. If the duration of a single shutdown exceeds a preset threshold, it is determined that the gearbox has not been started for a long time. When the gearbox actuator receives an opening / closing command, it first controls the opening of the second oil circuit 8 to supply oil continuously at its maximum opening for a preset time, while simultaneously opening the first oil circuit 7 to supply oil at its basic opening, until the oil supply from the second oil circuit 8 reaches the preset amount; the preset amount is generally set according to the capacity of the oil reservoir 500. Thus, by pre-supplying oil through the second oil circuit 8, the gearbox opening time can be shortened, mainly because the second oil circuit 8 supplies oil directly to the meshing point, resulting in better lubrication. In the traditional method, relying solely on the first oil circuit for oil supply requires replenishing the lubricating oil in the gearbox to a certain level.

[0053] The actuator is started and the starting torque value is monitored in real time by the torque sensor. A mapping model of shutdown time, starting torque value and preset amount is established. The preset amount is optimized and adjusted in real time based on the starting torque value so that the subsequent preset amount directly matches the output value of the model.

[0054] The preset threshold refers to the time limit for determining whether the gearbox is in a long-term shutdown state. This preset threshold can be adjusted according to the actual application scenario; for example, it can be set to a week, a month, or longer. The preset amount refers to the amount of lubricating oil that needs to be pre-injected after a long-term shutdown to ensure the gearbox can start smoothly. The mapping model is a correspondence model between the shutdown duration, the starting torque value, and the preset amount. This model can be established using experimental data or historical data and is used to automatically adjust the preset amount according to different shutdown durations and starting torque values ​​to achieve the best lubrication effect.

[0055] By using the above method, after the gearbox has been shut down for a long time, an appropriate amount of lubricating oil is pre-injected, and the starting torque value is monitored in real time during the startup process. Based on the starting torque value, the preset amount is optimized and adjusted in real time, thereby effectively solving the problem of difficulty in starting the gearbox after a long period of shutdown, avoiding damage to the gears caused by dry friction, and extending the service life of the gearbox.

[0056] In summary, after reading this detailed disclosure, those skilled in the art will understand that the foregoing detailed disclosure is presented by way of example only and is not restrictive. Although not explicitly stated herein, those skilled in the art will understand that the requirements of this application encompass various reasonable changes, improvements, and modifications to the embodiments. These changes, improvements, and modifications are intended to be made by this application and are within the spirit and scope of the exemplary embodiments of this application.

[0057] Furthermore, it should be understood that in the foregoing description of the embodiments of this application, various features are combined in a single embodiment, drawing, or description for the purpose of simplifying the understanding of a feature. However, this does not mean that the combination of these features is necessary, and those skilled in the art may readily identify some of the devices as separate embodiments when reading this application. That is, the embodiments in this application can also be understood as an integration of multiple sub-embodiments. It is also valid when each sub-embodiment contains fewer than all the features of a single foregoing disclosed embodiment.

[0058] Finally, it should be understood that the embodiments disclosed herein are illustrative of the principles of the embodiments of this application. Other modified embodiments are also within the scope of this application. Therefore, the embodiments disclosed herein are merely examples and not limitations. Those skilled in the art can adopt alternative configurations to implement the applications in this application based on the embodiments in this application. Therefore, the embodiments of this application are not limited to the embodiments precisely described in the application.

Claims

1. A multi-turn valve gearbox, comprising a housing, a transmission shaft laterally rotatably mounted on the housing, and a drive shaft longitudinally rotatably mounted on the housing, wherein a driven bevel gear is mounted on the transmission shaft for connection to an actuator, and a driving bevel gear is mounted at one end of the drive shaft for connection to a valve stem, characterized in that: An oil storage chamber is provided at the end of the driving bevel gear. A fixed shaft is provided inside the housing. One end of the fixed shaft extends into the oil storage chamber, and an oil passage communicating with the oil storage chamber is provided inside. Several first channels are provided circumferentially on the driving bevel gear. The outlet end of the first channel is located at the root of the adjacent tooth on the driving bevel gear. A first oil passage communicating with the inner cavity of the housing and a second oil passage communicating with the oil passage are provided on the housing. The first oil passage and the second oil passage are connected in series with an opening control valve.

2. The multi-turn valve gearbox according to claim 1, characterized in that: A linkage disc is coaxially mounted on the fixed shaft and the oil storage chamber. The linkage disc includes a circumferential linkage surface, on which multiple grooves are evenly distributed. A movable block is slidably disposed within the first channel, slidingly contacting the circumferential linkage surface. Springs are provided between both ends of the movable block and the inner wall of the first channel. First oil grooves are formed on both side walls of the movable block, and second oil grooves are formed on both side walls of the first channel, communicating with the inner cavity of the housing. The movable block has a first position abutting against the groove and a second position sliding out of the groove. When in the first position, the first oil groove and the oil storage chamber are connected and the second oil groove is isolated. When in the second position, the first oil groove and the oil storage chamber are isolated and the second oil groove is connected. When the valve is opened or closed by the actuator, the transmission shaft drives the active bevel gear to rotate relative to the linkage disc, causing the movable block to switch between the first and second positions, thus delivering the lubricating oil in the oil storage chamber to the tooth surface of the active bevel gear.

3. A multi-turn valve gearbox according to claim 2, characterized in that: The linkage disk is located in the middle of the moving block and includes at least two linkage plates spaced apart. The circumferential linkage surface is the outer contour surface of the linkage plate. The number of grooves is the same as that of the moving block and they are evenly distributed on the outer contour surface. One of the grooves is located at the lowest part of the outer contour surface in the vertical direction.

4. A multi-turn valve gearbox according to claim 2, characterized in that: When the moving block is in the first position, the outer end face of the moving block is lower than the outer tooth surface of the driving bevel gear. When the moving block is in the second position, the outer end face of the moving block does not exceed the outer tooth surface of the driving bevel gear.

5. A multi-turn valve gearbox according to claim 2, characterized in that: The side wall of the first oil tank near the second oil tank is configured as an oil guiding slope, and the side of the oil guiding slope near the linkage plate is inclined toward the second oil tank.

6. A multi-turn valve gearbox according to claim 2, characterized in that: An annular baffle is provided on one side of the oil storage chamber near its opening end. The outer ring of the annular baffle is in close contact with the inner wall of the oil storage chamber, and the diameter of its inner ring is larger than the outer diameter of the fixed shaft.

7. A multi-turn valve gearbox according to claim 6, characterized in that: The opening end of the oil storage chamber is rotatably mounted on the inner wall of the box via a rotary bearing, which is located on the side of the annular baffle away from the linkage plate.

8. A multi-turn valve gearbox according to any one of claims 1 to 7, characterized in that: It also includes a lubricating oil circulation system. The bottom of the tank is provided with an oil drain port. The lubricating oil circulation system includes a lubricating oil storage device, an oil inlet circuit and an oil outlet circuit. The oil inlet circuit is connected to the oil filling port, and the oil outlet circuit is connected to the oil drain port. A recovery control valve and a discharge pump are provided on the oil outlet circuit. An input pump is provided on the oil inlet circuit.

9. The method of using the multi-turn valve gearbox as described in claim 8, characterized in that: Includes the following steps: The real-time torque value T of the drive shaft is collected by a torque sensor. When T ≤ rated torque, the opening of the first oil circuit is dynamically adjusted to follow the change of T, while the second oil circuit maintains the basic opening. When T > rated torque, the first oil circuit is controlled to open to the maximum opening, and the opening of the second oil circuit is dynamically adjusted according to the change of T. The lubricating oil level in the internal cavity of the tank is monitored in real time by a liquid level sensor, and the lubricating oil level is controlled within a preset range by the oil input and discharge circuits.

10. The method of using the multi-turn valve gearbox according to claim 9, characterized in that: It also includes long-term shutdown start-up control, including the following steps: The duration of a single shutdown of the gearbox is obtained. If the duration of a single shutdown exceeds a preset threshold, it is determined that the gearbox has not been started for a long time. When the gearbox actuator receives the opening and closing command, it first controls the opening of the second oil circuit to supply oil continuously at the maximum opening for a preset time, and simultaneously opens the first oil circuit to supply oil at the basic opening until the oil supply of the second oil circuit reaches the preset amount. The actuator is started and the starting torque value is monitored in real time by the torque sensor. A mapping model of shutdown time, starting torque value and preset amount is established. The preset amount is optimized and adjusted in real time based on the starting torque value so that the subsequent preset amount directly matches the output value of the model.

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