A fine positioning method for underwater driving device of submerged gate

Abstract

The application discloses a fine positioning method for an underwater driving device of a submerged gate, and the submerged gate comprises a movable door leaf and a flow passage gate, and the positioning method comprises the following steps: step S1: according to the width B and the height H of a flow passage gate flow hole and water pressure borne, the radius of a cylinder body of the underwater driving device is estimated, and the minimum safety distance r of the underwater driving device in operation not being collided with the flow passage gate and the movable door leaf is determined according to the radius of the cylinder body; step S2: according to the minimum safety distance r value, the maximum force arm value L of the driving movable door leaf movement is determined max ; step S3: the pull-push force ratio coefficient ζ of the underwater driving device is determined; step S4: the rotating hinge point of the underwater driving device is determined; step S5: the working stroke of the underwater driving device is determined; and step S6: the hinge structure and hinge point position of the upper end of the underwater driving device and a cantilever support are determined.

Description

Technical Field

[0001] This invention relates to the field of metal structure technology for hydropower and water conservancy projects, and in particular to a precise positioning method for an underwater drive device of a submerged gate. Background Technology

[0002] Traditionally, submerged gates are operated via opening and closing devices located on the top of the dam (gate). This arrangement typically uses winches, which require a significant lifting or lowering stroke for each gate operation. Furthermore, only one winch can be installed on top of each gate, meaning each winch can only operate one gate at a time. This makes operation cumbersome and time-consuming, sometimes failing to meet functional requirements. With technological advancements, and to meet functional needs, domestic research has been conducted on incorporating underwater drive devices into submerged gates in hydropower, water conservancy, port and navigation, and landscape sluice gate projects. For example, in the field of water ecological environmental protection in hydropower projects, addressing the limitations of existing stratified water intake technologies—limited intake range, cumbersome operation, excessive time consumption, and difficult maintenance—development is underway to create efficient and rapid intake gates or equipment. This aims to precisely control the water volume, temperature, and quality at high dam reservoir intakes, better meeting the requirements of river water ecological environmental protection.

[0003] Chinese Patent CN114215020A discloses a highly efficient and rapid stepless tiered water intake gate device. This gate device is permanently submerged underwater. Each gate section consists of a movable gate flap, a flow channel gate supporting the flap, and an underwater drive device. The movable gate flap is operated by the underwater drive device located within the flow channel gate. The underwater drive device allows for partial or full opening / closing of the movable gate flap to achieve water intake at any depth. However, this stepless tiered water intake gate device does not disclose a method for positioning the underwater drive device, and the lifting point of the underwater drive device is located within the flow channel gate. This results in a small lever arm and large pushing / pulling force for the underwater drive device, increasing its size and weight. The costs are relatively high; moreover, the hanging plate installed inside the flow gate, which is used to rotate and hinge with the upper end of the underwater drive device, is suspended in the flow passage hole of the flow channel. During water intake operation, it will obstruct the water flow, reduce the flow passage area of ​​the flow channel, and increase the damping. This will lead to an increase in the flow velocity in the flow passage hole of the flow gate, induce the underwater drive device to vibrate due to overflow, and the fatigue effect is quite prominent in the long term, which is not conducive to the long-term safe and stable operation of the underwater drive device. In addition, for the underwater drive device using a deep-diving hydraulic press, the traditional oil pump adopts a box structure with large water flow damping, and the problem of the upper edge of the oil pump colliding with the movable gate is prominent. Sometimes it is necessary to widen the distance between the movable gate and the flow gate, which increases the investment significantly. Therefore, the existing technology is still not perfect and needs to be further improved. Summary of the Invention

[0004] The main objective of this invention is to propose a refined positioning method for an underwater drive device of a submerged gate, aiming to solve the aforementioned technical problems.

[0005] To achieve the above objectives, this invention proposes a refined positioning method for an underwater drive device of a submerged gate. The submerged gate includes a movable gate flap and a flow channel gate. A rotating hinge plate is provided at the bottom of the movable gate flap, and a fixed hinge plate is provided at the bottom of the upstream side of the flow channel gate. The rotating hinge plate and the fixed hinge plate are connected by a rotating hinge shaft. The upper end of the underwater drive device is rotatably hinged to a cantilever support located at the top of the downstream side of the flow channel gate, and the lower end of the underwater drive device is rotatably hinged to an ear plate on the downstream surface of the movable gate flap. The positioning method includes the following steps: Step S1: Based on the width B and height H of the flow passage orifice of the flow channel gate and the water pressure it can withstand, estimate the radius of the cylinder of the underwater drive device, and determine the minimum safe distance r of the underwater drive device to avoid collision with the flow channel gate and the movable gate flap during operation based on the radius of the cylinder. Step S2: Determine the maximum lever arm value L for driving the movable door flap movement based on the minimum safety distance r value. max ; Step S3: Determine the thrust-pull ratio coefficient ζ of the underwater drive device; Step S4: Locate and determine the rotation hinge point of the underwater drive device; Step S5: Determine the working stroke of the underwater drive device; Step S6: Determine the hinge structure and hinge point position between the upper end of the underwater drive device and the cantilever support.

[0006] Preferably, based on the resistance torque when the movable door is open and closed, a reasonable push-pull force value is determined according to the torque balance equation method, and a reasonable push-pull arm value is derived. The rotation hinge point of the underwater drive device is located and determined according to the unique intersection point rule of the intersection lines. It is the intersection point of the push-pull force lines when the movable door is fully closed and fully open. The working stroke is determined by the difference between the distance between the upper and lower hinge points in the fully extended state and the distance between the upper and lower hinge points in the fully retracted state of the underwater drive device.

[0007] Preferably, in step S2, the maximum lever arm L driving the movable door flap motion is determined. max At this time, it is necessary to determine the maximum angle between the central axis of the underwater drive device and the horizontal direction. The maximum included angle The calculation method is as follows: When the movable gate is fully open, the rotation center of the ear plate is marked as point A. Take a point at the rear edge of the top of the flow passage of the flow gate and mark it as the rear edge point B. Draw a circle with the minimum safe distance r as the radius at the rear edge point B to obtain the first circle. Draw a tangent line through point A to the first circle, with the tangent point as C, to obtain the tangent line AC. The tangent line AC is the upper limit center axis of the underwater drive device. θ=sin-1 (H0 / L0); α=sin -1 (r / L0); In the formula: θ is the angle between the line AB connecting point A and the trailing edge point B and the horizontal direction; H0 is the vertical height from point A to the trailing edge point B when the movable door flap is fully open; L0 is the distance from point A to the trailing edge point B when the movable gate is fully open; α is the angle between the line AB connecting point A and trailing edge point B and the upper limit center axis of the underwater drive device when the movable gate is fully open.

[0008] Preferably, the maximum lever arm value L driving the motion of the active gate flap is calculated. max The method is as follows: taking the rotation center of the rotating hinge shaft as point O, and the angle between the upper limit center axis of the underwater drive device and the horizontal direction as... When the rotation center O of the rotating hinge shaft is perpendicular to the central axis of the underwater drive device, let d be the perpendicular distance. Extend the tangent AC in the opposite direction, and it intersects the horizontal line passing through the rotation center O of the rotating hinge shaft at point D. Let L1 be the horizontal distance between the rotation center O of the rotating hinge shaft and point D. Then: d=L1sin L max =L1sin ).

[0009] Preferably, in step S3, when determining the thrust-pull ratio coefficient ζ of the underwater drive device, it is necessary to determine the resistance torque M when the movable door flap closes from the fully open state. f Then calculate the pulling force F required for the underwater drive device to close the movable door from the fully open state. L The calculation formula is: M f =P s1 L2+GL3+f d1 r1+f s1 L4; F L ≥n L M f / L max =n L (P) s1 L2+GL3+ f d1 r1+ f s1 L4) / L max ; Where: P s1 L1 is the water pressure when the movable door is fully open, and L2 is the water pressure when the movable door is fully open. s1The horizontal distance from the center of action to the rotation center O of the pivot hinge; G is the weight of the movable door flap, and L3 is the horizontal distance from the center of gravity of the movable door flap to the rotation center O of the rotating hinge when the movable door flap is fully open. f d1 R1 is the frictional force on the hinge shaft when the movable door is closed while fully open; R2 is the radius of the hinge shaft. f s1 L4 is the frictional force of the side water seal when the movable door is fully open and closed, and f is the frictional force of the side water seal. s1 The horizontal distance from the center of force to the rotation center O of the pivot hinge; n L The safety factor for the tensile torque is taken as 1.0~3.5.

[0010] Preferably, in step S3, when determining the thrust-pull ratio coefficient ζ of the underwater drive device, it is also necessary to determine the resistance torque M when the movable door flap is opened from the fully closed state. f Then calculate the thrust F required for the underwater propulsion device to open the movable door from the fully closed state. T The calculation formula is: M f `=P s2 L5+GL6+f d2 r1+f s2 L7; F T ≥n T M f ` / L max =n T (P) s2 L5+GL6+f d2 r1+f s2 L7) / L max ; Where: P s2 L5 represents the water pressure exerted by the movable door flap when it is fully closed; P represents the pressure exerted by the movable door flap when it is fully closed. s2 The perpendicular distance from the center of action to the rotation center O of the pivot hinge; G is the weight of the movable door flap, and L6 is the horizontal distance from the center of gravity of the movable door flap to the rotation center O of the rotating hinge when the movable door flap is fully closed. f d2 R1 is the frictional force on the hinge shaft when the movable door is fully closed and open; f s2 L7 is the frictional force of the side water seal when the movable door is fully closed and open. s2 The perpendicular distance from the center of force to the rotation center O of the pivot hinge; n T The thrust torque safety factor is taken as 1.0~3.5; According to the tension F L Thrust F T The calculated thrust-to-pull ratio coefficient ζ of the underwater drive device is: ζ = (n L M f ) / (n T M f `), then: F L =ζF T .

[0011] Preferably, the underwater drive device is configured according to standard series parameters F. T ≥n T M f ` / L max Please select F. T `numerical value, then based on F` L= ζF T F is determined according to the standard series parameters of underwater drive devices. L The numerical value is used to determine the lever arm L that satisfies the opening and closing of the movable door flap. T = n T M f ` / F T `、L L =n L M f / F L `.

[0012] Preferably, the rotation hinge point of the underwater drive device is located and determined in step S4, as follows: When the movable door is fully closed, the rotation center of the ear plate is marked as point A'. With the rotation center O of the pivot shaft as the center, the lever arm L... T Using the value of as the radius R1, draw a circle to obtain a second circle. Draw the tangent line between point A' and the second circle to determine the point of tangency E, and obtain the tangent line A'E. With point O, the center of rotation of the pivot shaft, as the center, the tension F L Using the value of as the radius R2, draw a circle to obtain a third circle. Draw the tangent line between point A and the third circle to determine the point of tangency F, and obtain the tangent line AF. Extend tangent A'E and tangent AF to obtain intersection point G; With intersection point G as the center, and the length of the line segment GA' between intersection point G and point A' as the radius R3, draw a circle to obtain the fourth circle. The line AG connecting point A and intersection point G intersects the fourth circle at point H. The length L of the line segment AH between point A and point H is the working stroke of the underwater drive device; The length of line segment HG, which intersects point H at point G, is the fully retracted length L of the underwater propulsion device. s L s =R3.

[0013] Preferably, when the total contraction length L s When the external geometric dimensions of the upper lifting head are met when the underwater drive device is fully retracted, and the cylinder of the underwater drive device is located outside the cantilever support, an upper lifting head is provided on the upper part of the underwater drive device, and the thickness of the upper lifting head is δ. The cantilever support is composed of a top plate and two hanging plates welded together. The width between the two hanging plates is adapted to the thickness δ of the upper hanging head, and the intersection point G is located on the center line of the rotation pin of the upper hanging head and the two hanging plates.

[0014] Preferably, when the total contraction length L s When the underwater drive device is fully retracted and the upper lifting head is arranged to meet the external geometric dimensions, and the cylinder of the underwater drive device is located inside the cantilever support, an upper lifting head is provided on the upper part of the underwater drive device; the cantilever support is composed of a top plate and double lifting plates welded together, the width between the double lifting plates is adapted to the outer diameter of the cylinder of the underwater drive device, and the intersection point G is located on the center line of the rotation pin shaft of the upper lifting head and the double lifting plates.

[0015] Preferably, when the total contraction length L s The external geometric dimensions of the upper lifting head cannot be met when the underwater drive device is fully retracted. The underwater drive device is designed with a central rotating hinge point and a central fixed hinge cylinder is provided on the underwater drive device. The cantilever support is composed of a top plate and double hanging plates welded together. A slot is provided at the downstream end of the top plate to form a clearance structure. The width between the double hanging plates is adapted to the outer diameter of the central fixed hinge cylinder, and the intersection point G is located on the center line of the rotating pin shaft of the central fixed hinge cylinder and the double hanging plates.

[0016] Preferably, when the total contraction length L s If the geometric dimensions of the upper lifting head when the underwater drive unit is fully retracted cannot be met, the following method is used when repositioning the upper end rotation hinge point of the underwater drive unit: Using intersection point G as the center, the length L that satisfies the geometric dimensions of the upper lifting head when the underwater drive unit is fully retracted is... s `and the total contraction length L s The difference △L s A circle with radius R4 is drawn to obtain a fifth circle. The line AG connecting the extension point A and the intersection point G intersects the fifth circle at point I; the line A'G connecting the extension point A' and the intersection point G intersects the fifth circle at point J; the points on the arc between the intersection points I and J on the fifth circle can meet the requirements for arranging the upper lifting head when the underwater drive device is fully retracted; an upper lifting head is set on the upper part of the underwater drive device; the cantilever support is composed of a top plate and double lifting plates welded together; the top plate is composed of a lower horizontal section, a reverse arc section, a forward arc section, and an upper horizontal section; a bottom water seal device is set at the bottom of the downstream side of the flow channel gate; the length b of the lower horizontal section is greater than the width c of the bottom water seal device; the width between the double lifting plates is adapted to the outer diameter of the cylinder of the underwater drive device, and the hinge point between the upper lifting head and the double lifting plates is located on the arc between the intersection points I and J.

[0017] Preferably, the underwater drive unit is a deep-sea hydraulic press, which has an oil pump with a ring structure.

[0018] Due to the adoption of the above technical solution, the beneficial effects of the present invention are as follows: (1) In the positioning method provided by the present invention, the outer diameter of the cylinder of the underwater drive device is estimated based on the width B and height H of the flow passage orifice of the flow gate and the water pressure Ps. The maximum lever arm value is determined under the premise that the underwater drive device does not collide with the flow gate or the movable gate during operation. Based on the resistance torque when the movable gate is open and closed, the reasonable push-pull force value is determined according to the torque balance equation method. The reasonable push-pull lever arm value is then derived. The rotation hinge point of the underwater drive device is located and determined according to the unique intersection point rule of the intersection line. It is used for driving the device in the fully closed and fully open states of the movable gate. The intersection of the lines of action of the push and pull forces is determined, and the working stroke is determined by the difference between the distance between the upper and lower lifting points in the fully extended state and the distance between the upper and lower lifting points in the fully retracted state of the underwater drive device. This not only enables the rapid and precise positioning of the rotation hinge point of the underwater drive device to determine its reasonable push and pull force value and working stroke, thus improving design efficiency, but also maximizes the force arm of the underwater drive device while ensuring its own safety and preventing collision with the flow channel gate. This effectively reduces the push and pull force value of the underwater drive device, achieving the goal of saving investment by reducing the size and weight of the underwater drive device.

[0019] (2) In the positioning method provided by the present invention, the rotation hinge point of the upper end of the underwater drive device is positioned outside the flow passage hole of the flow gate. Since the cantilever support that is rotatably hinged to the upper end of the drive device is not in the flow passage hole, the cantilever support hinged to the underwater drive device does not affect the flow passage of the flow gate, thereby reducing the impact of the water flow on the drive device, reducing the amplitude and frequency of the underwater drive device's flow vibration, and effectively ensuring the long-term safe and stable operation of the underwater drive device.

[0020] (3) In this invention, the underwater drive device can adopt the design of the distance between the hanging plates of the cantilever support fixed at the top of the downstream side of the flow channel gate according to the rotation requirements of the central fixed hinge cylinder, or the selection of the arc segment between the intersection of the full retraction length difference of the underwater drive device with the end hinge as the radius and the line of action of the push and pull force to reposition and determine the rotation hinge point, which solves the problem that the length of the underwater drive device in the fully retracted state cannot meet the requirements for arranging its upper hanging head.

[0021] (4) In this invention, when the underwater drive device adopts a cantilever support with a central hinge and a fixed top on the downstream side of the flow channel gate, the spacing between the hanging plates is designed according to the rotation requirements of the central fixed hinge cylinder. The downstream end of the top plate of the cantilever support is provided with a slot to form a clearance structure, which satisfies the swing amplitude requirements of the exposed part of the upper part of the underwater drive device.

[0022] (5) In this invention, when the underwater drive device uses the difference in the full contraction length of the end hinge as the radius to select the point between the arc segment between the intersection of the circle and the line of action of the push and pull force, the upper top plate of the cantilever support is designed with a streamlined structure, which effectively reduces the damping during water intake operation and reduces the problem of overflow vibration of the flow channel gate. Its top plate consists of a lower horizontal section, a reverse arc section, a forward arc section, and an upper horizontal section. The lower horizontal section is set with a length greater than the width of the bottom water seal device to meet the uniform compression requirements during sealing, effectively preventing the bottom water seal from overturning and failing due to uneven compression, and enhancing the reliability of the bottom water seal water stop.

[0023] (6) In this invention, when the underwater drive device adopts a deep-diving hydraulic press, the oil pump adopts a ring structure, which reduces water flow damping compared with the traditional box-type oil pump. The external protrusion of the upper edge is small, which effectively solves the problem of the upper edge of the oil pump colliding with the movable door flap and saves investment. Attached Figure Description

[0024] 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, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0025] Figure 1 This is a schematic diagram of the water pressure effect when the movable gate flaps of the submerged gate in the present invention are fully closed and blocking water. Figure 2 To determine the maximum angle between the centerline of the deep-sea hydraulic press and the horizontal line for the present invention. Step 1 diagram; Figure 3 To determine the maximum angle between the centerline of the deep-sea hydraulic press and the horizontal line for the present invention. Step 2 diagram; Figure 4 To determine the maximum angle between the centerline of the deep-sea hydraulic press and the horizontal line for the present invention. Step 3 diagram; Figure 5 To determine the maximum lever arm L of the deep-sea hydraulic press on the hinge point of the movable door flap in this invention. max Schematic diagram; Figure 6 This is a schematic diagram of the load on the movable door flap when it is fully open in this invention; Figure 7 This is a schematic diagram of the resistance torque when the movable door flap is closed in the fully open state in this invention; Figure 8This is a schematic diagram of the horizontal load on the movable door flap when it is fully closed in this invention. Figure 9 This is a schematic diagram of the vertical load on the movable door flap when it is fully closed in this invention. Figure 10 This is a schematic diagram of the resistance torque when the movable door flap is fully closed during opening in this invention; Figure 11 This is a schematic diagram illustrating the process of determining the thrust line of the deep-sea hydraulic press when the movable door flap is opened from a fully closed state in this invention. Figure 12 This is a schematic diagram illustrating the process of determining the line of action of the deep-sea hydraulic press during the closing of the movable door flap when it is fully open in this invention; Figure 13 This is a schematic diagram illustrating the process of determining the rotation hinge point of the deep-sea hydraulic press in this invention; Figure 14 This is a schematic diagram illustrating the working stroke of the deep-sea hydraulic press in this invention; Figure 15 This is a schematic diagram of step one for repositioning and determining the rotation hinge point when the length of the deep-submersible hydraulic press in its fully retracted state cannot meet the requirements for arranging its upper lifting head. Figure 16 This is a schematic diagram of step two in the invention, where the length of the deep-sea hydraulic press in its fully retracted state cannot meet the requirements for arranging its upper lifting head; Figure 17 The total contraction length L in this invention s An upstream view of a submerged gate that meets the external geometric dimensions of the upper lifting head when the underwater drive unit is fully retracted, and the cylinder of the underwater drive unit is located outside the cantilever support. Figure 18 The total contraction length L in this invention s The downstream view of a submerged gate that meets the external geometric dimensions of the upper lifting head when the underwater drive device is fully retracted, and the cylinder of the underwater drive device is located outside the cantilever support. Figure 19 The total contraction length L in this invention s A side view of a submerged gate when the external geometry of the upper lifting head is arranged in full retraction of the underwater drive unit, and the cylinder of the underwater drive unit is located outside the cantilever support. Figure 20 for Figure 18 Sectional view of AA; Figure 21 The total contraction length L in this invention s A bottom view of a submerged gate when the external geometry of the upper lifting head is arranged in full retraction of the underwater drive unit, and the cylinder of the underwater drive unit is located outside the cantilever support. Figure 22 The total contraction length L in this inventions A top view of a submerged gate when the external geometry of the upper lifting head is arranged in full retraction of the underwater drive unit, and the cylinder of the underwater drive unit is located outside the cantilever support. Figure 23 for Figure 18 BB section view; Figure 24 The total contraction length L in this invention s An upstream view of a submerged gate that meets the external geometric dimensions of the upper lifting head when the underwater drive unit is fully retracted, and the cylinder of the underwater drive unit is located inside the cantilever support. Figure 25 The total contraction length L in this invention s A downstream view of a submerged gate when the external geometry of the upper lifting head is arranged in full retraction of the underwater drive unit, and the cylinder of the underwater drive unit is located inside the cantilever support. Figure 26 The total contraction length L in this invention s A side view of a submerged gate when the external geometry of the upper lifting head is arranged in full retraction of the underwater drive unit, and the cylinder of the underwater drive unit is located inside the cantilever support. Figure 27 for Figure 25 DD section view; Figure 28 The total contraction length L in this invention s A bottom view of a submerged gate when the external geometry of the upper lifting head is arranged in full retraction of the underwater drive unit, and the cylinder of the underwater drive unit is located inside the cantilever support. Figure 29 For the total contraction length L in this invention s A top view of a submerged gate when the external geometry of the upper lifting head is arranged in full retraction of the underwater drive unit, and the cylinder of the underwater drive unit is located inside the cantilever support. Figure 30 for Figure 25 EE section view; Figure 31 The total contraction length L in this invention s The underwater drive unit cannot meet the external geometric dimensions of the upper crane head when it is fully retracted. The upstream view of the submerged gate when the underwater drive unit is designed based on the central rotation hinge point. Figure 32 The total contraction length L in this invention s The underwater drive unit cannot meet the external geometric dimensions of the upper lifting head when fully retracted, and the underwater drive unit is designed based on the central rotation hinge point. (Downstream view of the submerged gate) Figure 33 The total contraction length L in this invention sThe side view of the submerged gate when the shape and geometric dimensions of the upper lifting head are not met when the underwater drive device is fully retracted; the underwater drive device is designed according to the central rotation hinge point. Figure 34 for Figure 32 FF section view; Figure 35 The total contraction length L in this invention s The bottom view of the submerged gate when the shape and geometric dimensions of the upper lifting head are not met when the underwater drive device is fully retracted; the underwater drive device is designed based on the central rotation hinge point. Figure 36 The total contraction length L in this invention s The top view of the submerged gate when the shape and geometric dimensions of the upper lifting head are not met when the underwater drive device is fully retracted; the underwater drive device is designed according to the central rotation hinge point. Figure 37 for Figure 32 Middle GG sectional view; Figure 38 The total contraction length L in this invention s The external geometric dimensions of the upper lifting head cannot be met when the underwater drive device is fully retracted. The upstream view of the submerged gate when the upper end rotation hinge point of the underwater drive device is repositioned and determined. Figure 39 The total contraction length L in this invention s The external geometric dimensions of the upper lifting head cannot be met when the underwater drive device is fully retracted. The downstream view of the submerged gate when the upper end rotation hinge point of the underwater drive device is repositioned and determined. Figure 40 The total contraction length L in this invention s The external geometric dimensions of the upper lifting head cannot be met when the underwater drive device is fully retracted. The submerged gate side view is used when the upper end rotation hinge point of the underwater drive device is repositioned and determined. Figure 41 for Figure 39 Middle HH section view; Figure 42 The total contraction length L in this invention s The external geometric dimensions of the upper lifting head cannot be met when the underwater drive device is fully retracted. The submerged gate bottom view is used when the upper end rotation hinge point of the underwater drive device is repositioned and determined. Figure 43 The total contraction length L in this invention s The external geometric dimensions of the upper lifting head cannot be met when the underwater drive device is fully retracted. The top view of the submerged gate when the upper end rotation hinge point of the underwater drive device is repositioned and determined. Figure 44 for Figure 39 Sectional view II; Figure 45 This is a schematic diagram of the installation and positioning of two adjacent submerged gates in this invention. Figure 46 for Figure 20 , Figure 27 , Figure 34 , Figure 41 CC section view.

[0026] Explanation of reference numerals: 1. Movable door flap; 1a. Rotating hinge plate; 1b. Ear plate; 2. Underwater drive device; 3. Flow gate; 3a. Fixed hinge plate; 4. Cantilever support; 5. Cylinder body; 11. First circle; 13. Rotating hinge shaft; 16. Side water seal; 18. Second circle; 19. Third circle; 22. Fourth circle; 24. Upper lifting head; 26. Rear flange of top main crossbeam; 27. Top plate; 28. Double lifting plate; 29. ​​Oil pump; 31. Slot; 32. Middle fixed hinge cylinder; 33. Fifth circle; 35. Arc; 36. Lower horizontal section; 37. Reverse arc section; 38. Forward arc section; 39. Upper horizontal section; 40. Bottom water seal device; 41. Rotating pin shaft. Detailed Implementation

[0027] 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 a part of the embodiments of the present invention, and not all of the 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.

[0028] It should be noted that all directional indications (such as up, down, left, right, front, back, etc.) in the embodiments of the present invention are only used to explain the relative positional relationship and movement of each component in a certain specific posture (as shown in the figure). If the specific posture changes, the directional indication will also change accordingly.

[0029] Furthermore, the use of terms such as "first" and "second" in this invention is for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of that feature. Additionally, the technical solutions of the various embodiments can be combined with each other, but only on the basis of being achievable by those skilled in the art. When the combination of technical solutions is contradictory or impossible to implement, such a combination of technical solutions should be considered non-existent and not within the scope of protection claimed by this invention.

[0030] As shown in the attached figures, a method for precise positioning of an underwater drive device for a submerged gate is provided. The submerged gate includes a movable gate flap 1 and a flow channel gate 3. A rotating hinge plate 1a is provided at the bottom of the movable gate flap 1, and a fixed hinge plate 3a is provided at the bottom of the upstream side of the flow channel gate 3. The rotating hinge plate 1a and the fixed hinge plate 3a are connected by a rotating hinge shaft 13. The upper end of the underwater drive device 2 is rotatably hinged to a cantilever support 4 located at the top of the downstream side of the flow channel gate 3, and the lower end of the underwater drive device 2 is rotatably hinged to an ear plate 1b on the downstream side surface of the movable gate flap 1. Specifically, in this embodiment, the underwater drive device 2 is a deep-diving hydraulic press, which has an annular oil pump 29. The positioning method includes the following steps: Step S1: Based on the width B and height H of the flow passage orifice of the flow gate 3, and the water pressure P it can withstand... s Estimate the radius of the cylinder 5 of the underwater drive device 2, and determine the minimum safe distance r of the underwater drive device 2 to avoid collision with the flow gate 3 and the movable gate 1 during operation based on the radius of the cylinder 5. Step S2: Determine the maximum lever arm value L for driving the movable door flap 1 based on the minimum safety distance r. max ; Step S3: Determine the thrust-pull ratio coefficient ζ of the underwater drive device 2; Step S4: Locate and determine the rotation hinge point of the underwater drive device 2; Step S5: Determine the working stroke of the underwater drive device 2; Step S6: Determine the hinge structure and hinge point position between the upper end of the underwater drive device 2 and the cantilever support 4.

[0031] Specifically, the principle of this positioning method is as follows: Based on the resistance torque of the movable door 1 in the open and closed states, a reasonable pushing and pulling force value is determined according to the torque balance equation method, and a reasonable pushing and pulling arm value is derived. The rotation hinge point of the underwater drive device 2 is located and determined according to the unique intersection point rule of the intersection lines. It is the intersection point of the pushing and pulling force lines when the movable door 1 is fully closed and fully open. The working stroke is determined by the difference between the distance between the upper and lower hinge points in the fully extended state and the distance between the upper and lower hinge points in the fully retracted state of the underwater drive device 2.

[0032] Combination Figures 2 to 4 As shown, in this embodiment, in step S2, the maximum lever arm L that drives the movable door flap 1 to move is determined. max At this time, it is necessary to determine the maximum angle between the central axis of the underwater drive device 2 and the horizontal direction. The maximum included angle The calculation method includes the following steps: First, when the movable gate 1 is fully open, the rotation center of the ear plate 1b is marked as point A. A point is taken at the rear edge of the top of the flow passage opening of the flow gate 3 and marked as rear edge point B. The vertical height H0 and the straight-line distance L0 between point A and rear edge point B are then determined. Thus, the angle θ between the straight line AB and the horizontal line is obtained as θ = sin -1 (H0 / L0); The second step is to draw a circle with a radius of minimum safety distance r at the trailing edge point B to obtain the first circle 11. Then, draw a tangent line to the first circle 11 passing through point A, with the point of tangency at C, obtaining the tangent line AC. This tangent line AC is the upper limit center axis of the underwater drive device 2. Therefore: α = sin -1 (r / L0); α is the angle between the line AB connecting point A and trailing edge point B and the upper limit center axis of the underwater drive device 2 when the movable door flap 1 is fully open; The third step is to determine the maximum angle between the upper limit center axis of the underwater drive device 2 and the horizontal direction. In the above calculation formula: θ is the angle between the line AB connecting point A and the trailing edge point B and the horizontal direction; H0 is the vertical height from point A to the rear edge point B when the movable door flap 1 is fully open; L0 is the distance from point A to the trailing edge point B when the movable gate flap 1 is fully open.

[0033] Combination Figure 5 As shown, calculate the maximum lever arm value L that drives the motion of the movable door lobe 1. max The method is as follows: taking the rotation center of the rotating hinge 13 as point O, and the angle between the upper limit center axis of the underwater drive device 2 and the horizontal direction as... When the rotation center O of the rotating hinge 13 is determined to be d, the vertical distance from the upper limit center axis of the underwater drive device 2 is determined. Specifically, the tangent AC is extended in the opposite direction and intersects the horizontal line passing through the rotation center O of the rotating hinge 13 at point D. The horizontal distance between the rotation center O of the rotating hinge 13 and point D is L1. Then: d=L1sin L max =L1sin ).

[0034] Combination Figures 6 to 10 As shown, in step S3, when determining the thrust-pull ratio coefficient ζ of the underwater drive device 2, the movable door 1 uses the torque balance equation method to determine the thrust-pull ratio coefficient ζ of the underwater drive device 2 based on the water pressure, gravity, friction of the rotating hinge 13, and resistance torque generated by the friction of the side water seal 16 when it is fully open and fully closed. Specifically, it is first necessary to determine the resistance torque M when the movable door 1 closes from the fully open state. fThen calculate the pulling force F required for the underwater drive device 2 to close the movable door 1 from the fully open state. L The calculation formula is: M f =P s1 L2+GL3+f d1 r1+f s1 L4; F L ≥n L M f / L max =n L (P) s1 L2+GL3+ f d1 r1+ f s1 L4) / L max ; Where: P s1 L1 represents the water pressure exerted on the movable door flap 1 when it is fully open, and L2 represents the water pressure exerted on the movable door flap 1 when it is fully open. s1 The horizontal distance from the center of action to the rotation center O of the rotating hinge shaft 13; G is the weight of the movable door flap 1, and L3 is the horizontal distance from the center of gravity of the movable door flap 1 when it is fully open to the rotation center O of the rotating hinge shaft 13. f d1 r1 is the frictional force of the rotating hinge 13 when the movable door flap 1 is closed in the fully open state; f s1 L4 is the frictional force of the side water seal 16 when the movable door flap 1 is fully open and closed, and f is the frictional force of the side water seal 16. s1 The horizontal distance from the center of force to the rotation center O of the rotating hinge 13; n L The safety factor for the tensile torque is taken as 1.0~3.5.

[0035] In addition, it is necessary to determine the resistance torque M when the movable door flap 1 is opened from the fully closed state. f Then calculate the thrust F required for the underwater drive unit 2 to open the movable door 1 from the fully closed state. T The calculation formula is: M f `=P s2 L5+GL6+f d2 r1+f s2 L7; F T ≥n T M f ` / L max =n T (P) s2 L5+GL6+f d2 r1+f s2L7) / L max , Where: P s2 L1 represents the water pressure exerted on movable door flap 1 when it is fully closed; L2 represents the water pressure exerted on movable door flap 1 when it is fully closed. s2 The perpendicular distance from the center of action to the rotation center O of the rotating hinge 13; G is the weight of the movable door flap 1, and L6 is the horizontal distance from the center of gravity of the movable door flap 1 when it is fully closed to the rotation center O of the rotating hinge shaft 13. f d2 R1 is the frictional force of the rotating hinge 13, and r1 is the radius of the rotating hinge 13. fs2 is the frictional force of the side water seal 16 when the movable door flap 1 is fully closed and open, and L7 is the vertical distance from the center of the force of fs2 to the rotation center O of the rotating hinge shaft 13. n T The thrust torque safety factor is taken as 1.0~3.5; According to the tension F L Thrust F T The calculated thrust-to-pull ratio coefficient ζ of the underwater drive device 2 is: ζ = (n L M f ) / (n T M f `), then: F L =ζF T .

[0036] In this embodiment, the underwater drive device 2 is configured according to standard series parameters F. T ≥n T M f ` / L max Please select F. T `numerical value, then based on F` L= ζF T F is determined according to the standard series parameters of underwater drive device 2. L The numerical value is used to determine the lever arm L that satisfies the opening and closing of the active door flap 1. T = n T M f ` / F T `、L L =n L M f / F L `.

[0037] Combination Figures 11 to 16 As shown, in step S4, the rotation hinge point of the underwater drive device 2 is located and determined. Specifically, the rotation hinge point of the underwater drive device 2 is located and determined according to the unique intersection rule of intersecting lines. The intersection point of the lines of action of the push and pull forces when the movable door flap 1 is fully closed and fully open is the rotation hinge point. The specific method is as follows: Combination Figure 11 As shown, when the movable door flap 1 is fully closed, the rotation center of the ear plate 1b is marked as point A'. With the rotation center O of the rotating hinge shaft 13 as the center, the lever arm L... T Using the value of as the radius R1, draw a circle to obtain the second circle 18. Draw the tangent line between point A' and the second circle 18 to determine the point of tangency E, and obtain the tangent line A'E. Combination Figure 12 , Figure 13 As shown, when the movable door flap 1 is fully open, with the rotation center O of the rotating hinge shaft 13 as the center, the pulling force F L Using the value of as the radius R2, draw a circle to obtain the third circle 19. Draw the tangent line between point A and the third circle 19 to determine the point of tangency F, and obtain the tangent line AF. Extend the tangents A'E and AF to obtain the intersection point G.

[0038] Combination Figure 14 As shown, the underwater drive device 2 determines its working stroke L by the difference between the distance between its upper and lower slings in its fully extended state and the distance between its upper and lower slings in its fully retracted state. Specifically, a circle is drawn with intersection point G as the center and the length of the line segment GA' between intersection point G and point A' as the radius R3, resulting in a fourth circle 22. The line AG connecting point A and intersection point G intersects the fourth circle 22 at point H. The length L of the line segment AH between point A and point H is the working stroke of the underwater drive device 2; The length of line segment HG between point H and intersection point G is the fully retracted length L of underwater drive device 2. s L s =R3.

[0039] In this embodiment, in step S6, it is necessary to determine the full retraction length L of the lower drive device (2). s Based on the structural form of the upper cylinder 5, the hinge structure and hinge point position between the upper end of the lower drive device (2) and the cantilever support (4) are determined. The determination of the hinge structure and hinge point position mainly includes the following four situations: Combination Figures 17 to 23 As shown, the first case is: when the total contraction length L sWhen the underwater drive device 2 is fully retracted and the external geometric dimensions of the upper lifting head 24 are met, and the cylinder 5 of the underwater drive device 2 is located outside the cantilever support 4, the intersection point G is determined as the rotation hinge point of the upper end of the underwater drive device 2. Therefore, an upper lifting head 24 is provided on the upper part of the underwater drive device 2; the thickness of the upper lifting head 24 is δ; the cantilever support 4 is welded to the rear flange 26 of the main crossbeam on the downstream side of the flow channel gate 3. The cantilever support 4 is composed of a top plate 27 and double hanging plates 28 welded together. The width between the double hanging plates 28 is adapted to the thickness δ of the upper lifting head 24, that is, the spacing between the two double hanging plates 28 is designed according to the thickness δ of the upper lifting head 24. The upper lifting head 24 is installed between the double hanging plates 28 through a pin 41, and the intersection point G falls on the center line of the rotation pin 41 of the upper lifting head 24 and the double hanging plates 28.

[0040] Combination Figures 24 to 30 As shown, the second case is: when the total contraction length L s When the external geometric dimensions of the upper lifting head are satisfied when the underwater drive device 2 is fully retracted, and the cylinder 5 of the underwater drive device 2 is located inside the cantilever support 4, then the intersection point G is determined as the rotation hinge point of the upper end of the underwater drive device 2. Therefore, an upper lifting head 24 is provided on the upper part of the underwater drive device 2; the diameter of the cylinder 5 of the underwater drive device 2 is D1, and the cantilever support 4 is welded to the rear flange 26 of the main crossbeam on the downstream side of the flow gate 3. The cantilever support 4 is composed of a top plate 27 and double hanging plates 28 welded together. The width between the double hanging plates 28 is adapted to the outer diameter of the cylinder 5 of the underwater drive device 2. That is, the spacing between the double hanging plates 28 is designed according to the diameter D1 of the cylinder 5 of the underwater drive device 2. The upper lifting head 24 is installed between the double hanging plates 28 through a pin 41, and the top of the cylinder 5 of the underwater drive device 2 extends into the space between the double hanging plates 28. The intersection point G falls on the center line of the rotation pin 41 of the upper lifting head 24 and the double hanging plates 28.

[0041] Combination Figures 31 to 37 As shown, the third case is: when the total contraction length L sThe underwater drive device 2 cannot meet the geometric dimensions of the upper lifting head when fully retracted. Therefore, the underwater drive device 2 is designed with a central rotating hinge point, and a central fixed hinge cylinder 32 is provided on the underwater drive device 2. The outer diameter of the central fixed hinge cylinder 32 is D2. The cantilever support 4 is welded to the rear flange 26 of the main crossbeam on the downstream side of the flow gate 3. The cantilever support 4 is composed of a top plate 27 and double hanging plates 28 welded together. A slot 31 is provided at the downstream end of the top plate 27 to form a clearance structure. The width between the double hanging plates 28 is adapted to the outer diameter D2 of the central fixed hinge cylinder 32. That is, the spacing between the double hanging plates 28 is designed according to the outer diameter D2 of the central fixed hinge cylinder 32. The central fixed hinge cylinder 32 is installed between the double hanging plates 28 by a pin 41, and the top of the cylinder 5 of the underwater drive device 2 extends out from the slot 31 of the top plate 27. The intersection point G falls on the center line of the rotating pin 41 of the fixed hinge cylinder 32 and the double hanging plate 28 in the middle.

[0042] Combination Figure 16 ,as well as Figures 38 to 45 As shown, the fourth case is: when the total contraction length L s If the geometric dimensions of the upper lifting head of the underwater drive unit 2 cannot be met when it is fully retracted, the following method is used when repositioning and determining the upper end rotation hinge point of the underwater drive unit 2: taking the intersection point G as the center, the length L that meets the geometric dimensions of the upper lifting head of the underwater drive unit 2 when it is fully retracted is... s `and the total contraction length L s The difference △L s Draw a circle with radius R4 to obtain the fifth circle 33. The line AG connecting the extension point A and the intersection point G intersects the fifth circle 33 at point I; the line A'G connecting the extension point A' and the intersection point G intersects the fifth circle 33 at point J. Then, the point on the arc 35 between the intersection point I and the intersection point J on the fifth circle 33 can meet the requirements for arranging the upper lifting head when the underwater drive device 2 is fully retracted. Therefore, in this case, the cantilever support 4 is welded to the rear flange 26 of the top main crossbeam on the downstream side of the flow gate 3. The cantilever support 4 is composed of a top plate 27 and a double hanging plate 28 welded together. The top plate 27 is composed of a lower horizontal section 36, a reverse arc section 37, a forward arc section 38, and an upper horizontal section 39. A bottom water seal device 40 is set at the bottom of the downstream side of the flow gate 3. The length b of the lower horizontal section 36 is greater than the width c of the bottom water seal device 40 to avoid interference. In this case, an upper lifting head 24 is provided on the upper part of the underwater drive device 2. The width between the double lifting plates 28 is adapted to the outer diameter of the cylinder 5 of the underwater drive device 2. That is, the spacing between the double lifting plates 28 is designed according to the diameter D1 of the cylinder 5 of the underwater drive device 2. The upper lifting head 24 is installed between the double lifting plates 28 through the pin 41, and the hinge point between the upper lifting head 24 and the double lifting plates 28 is located on the arc 35 between the intersection point I and the intersection point J.

[0043] The above description is merely a preferred embodiment of the present invention and does not limit the patent scope of the present invention. Any equivalent structural transformations made using the contents of the present invention's specification and drawings under the inventive concept of the present invention, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present invention.

Claims

1. A method for precise positioning of an underwater drive device for a submerged gate, the submerged gate comprising a movable gate flap (1) and a flow channel gate (3), wherein a rotating hinge plate (1a) is provided at the bottom of the movable gate flap (1), and a fixed hinge plate (3a) is provided at the bottom of the upstream side of the flow channel gate (3); the rotating hinge plate (1a) and the fixed hinge plate (3a) are connected by a rotating hinge shaft (13); the upper end of the underwater drive device (2) is rotatably hinged to a cantilever support (4) located at the top of the downstream side of the flow channel gate (3), and the lower end of the underwater drive device (2) is rotatably hinged to an ear plate (1b) on the downstream side surface of the movable gate flap (1), characterized in that, The positioning method includes the following steps: Step S1: Based on the width B and height H of the flow passage orifice of the flow gate (3) and the water pressure it can withstand, estimate the radius of the cylinder of the underwater drive device (2), and determine the minimum safe distance r of the underwater drive device (2) from colliding with the flow gate (3) and the movable gate (1) during operation based on the radius of the cylinder; Step S2: determining the maximum lever arm value L for driving the movement of the active door leaf (1) in accordance with the minimum safety distance r value max ; Step S3: Calculate the resistance torque when the movable door is fully open and closed, and the resistance torque when it is fully closed. Determine the thrust-pull ratio coefficient ζ of the underwater drive device according to the torque balance equation method. Step S4: Locate and determine the rotation hinge point of the underwater drive device according to the unique intersection point rule of the intersecting lines, which is the intersection point of the lines of action of the push and pull forces when the movable door is fully closed and fully open. Step S5: Determine the working stroke of the underwater drive device (2); Step S6: Determine the hinge structure and hinge point position between the upper end of the lower drive device (2) and the cantilever support (4).

2. The refined positioning method for an underwater drive device of a submerged gate as described in claim 1, characterized in that, Based on the resistance torque of the movable door (1) in the open and closed states, a reasonable push-pull force value is determined according to the torque balance equation method, and a reasonable push-pull arm value is derived. The rotation hinge point of the underwater drive device (2) is located and determined according to the unique intersection point rule of the intersection line. It is the intersection point of the push-pull force action line when the movable door is fully closed and fully open. The working stroke is determined by the difference between the distance between the upper and lower hinge points in the fully extended state and the distance between the upper and lower hinge points in the fully retracted state of the underwater drive device (2).

3. The refined positioning method for an underwater drive device of a submerged gate as described in claim 1, characterized in that, In step S2, the maximum lever arm L that drives the movable door flap (1) to move is determined. max At this time, it is necessary to determine the maximum angle between the central axis of the underwater drive device (2) and the horizontal direction. The maximum included angle The calculation method is as follows: When the active gate (1) is fully open, the rotation center of the ear plate (1b) is marked as point A. Take a point at the rear edge of the top of the flow passage of the flow gate (3) and mark it as the rear edge point B. Draw a circle at the rear edge point B with the minimum safety distance r as the radius to obtain the first circle (11). Draw a tangent to the first circle (11) with the point A as the tangent point C to obtain the tangent AC. Then the tangent AC is the upper limit center axis of the underwater drive device (2). θ=sin -1 (H0 / L0); α=sin -1 (r / L0); In the formula: θ is the angle between the line AB connecting point A and the trailing edge point B and the horizontal direction; H0 is the vertical height from point A to the rear edge point B when the active door flap (1) is fully open; L0 is the distance from point A to the trailing edge point B when the active door flap (1) is fully open; α is the angle between the line AB connecting point A and trailing edge point B and the upper limit center axis of the underwater drive device (2) when the movable door (1) is fully open.

4. The refined positioning method for an underwater drive device of a submerged gate as described in claim 3, characterized in that, Calculate the maximum lever arm value L of the driving active gate lobe (1) motion. max The method is as follows: taking the rotation center of the rotating hinge (13) as point O, and the angle between the upper limit center axis of the underwater drive device (2) and the horizontal direction as... When the rotation center O of the rotating hinge (13) is perpendicular to the central axis of the underwater drive device (2), the distance is d; the tangent AC is extended in the opposite direction and intersects the horizontal line passing through the rotation center O of the rotating hinge (13) at point D. The horizontal distance between the rotation center O of the rotating hinge (13) and point D is L1. Then: d=L1sin L max =L1sin ().

5. The refined positioning method for an underwater drive device of a submerged gate as described in claim 4, characterized in that, In step S3, when determining the thrust-pull ratio coefficient ζ of the underwater drive device (2), it is necessary to determine the resistance torque M when the movable door (1) closes from the fully open state. f Then calculate the pulling force F required for the underwater drive device (2) to drive the movable door (1) from the fully open state to close. L The calculation formula is: M f =P s1 L2+GL3+f d1 r1+f s1 L4; F L ≥n L M f / L max =n L (P s1 L2+GL3+ f d1 r1+ f s1 L4) / L max ; Where: P s1 L1 is the water pressure exerted on the movable door flap (1) when it is fully open, and L2 is the water pressure exerted on the movable door flap (1) when it is fully open. s1 The horizontal distance from the center of action to the rotation center O of the rotating hinge (13); G is the weight of the movable door flap (1), and L3 is the horizontal distance from the center of gravity of the movable door flap (1) to the rotation center O of the rotating hinge shaft (13) when the movable door flap (1) is fully open. f d1 r1 is the frictional force of the rotating hinge (13) when the movable door flap (1) is closed in the fully open state; f s1 L4 is the frictional force of the side water seal (16) when the movable door flap (1) is closed in the fully open state, and f is the frictional force of the side water seal (16). s1 The horizontal distance from the center of force to the rotation center O of the rotating hinge (13); n L The safety factor for the tensile torque is taken as 1.0~3.

5.

6. The refined positioning method for an underwater drive device of a submerged gate as described in claim 5, characterized in that, In step S3, when determining the thrust-pull ratio coefficient ζ of the underwater drive device (2), it is also necessary to determine the resistance torque M when the movable door (1) is opened from the fully closed state. f Then calculate the thrust F required for the underwater drive device (2) to open the movable door (1) from the fully closed state. T The calculation formula is: M f `=P s2 L5+GL6+f d2 r1+f s2 L7; F T ≥n T M f ` / L max =n T (P s2 L5+GL6+f d2 r1+f s2 L7) / L max , Where: P s2 L5 is the water pressure exerted on the movable door flap (1) when it is fully closed, and P is the pressure exerted on the movable door flap (1) when it is fully closed. s2 The perpendicular distance from the center of action to the rotation center O of the rotation hinge (13); G is the gravity of the movable door flap (1), and L6 is the horizontal distance from the center of gravity of the movable door flap (1) to the rotation center O of the rotating hinge shaft (13) when the movable door flap (1) is fully closed. f d2 r1 is the frictional force of the rotating hinge (13) when the movable door is fully closed and open; f s2 L7 is the frictional force of the side water seal (16) when the movable door flap (1) is fully closed and open, and f is the frictional force of the side water seal (16). s2 The perpendicular distance from the center of force to the rotation center O of the rotating hinge (13); n T The thrust torque safety factor is taken as 1.0~3.5; According to the tension F L Thrust F T The calculated thrust-to-pull ratio coefficient ζ of the underwater drive device (2) is: ζ = (n L M f ) / (n T M f `), then: F L =ζF T .

7. The refined positioning method for an underwater drive device of a submerged gate as described in claim 6, characterized in that, The underwater drive unit (2) is based on the standard series parameters according to F T ≥n T M f ` / L max Please select F. T `numerical value, then based on F` L= ζF T Determine F according to the standard series parameters of underwater drive device (2) L The numerical value is used to determine the lever arm L that satisfies the opening and closing of the active door flap (1). T = n T M f ` / F T `、L L =n L M f / F L `.

8. The refined positioning method for an underwater drive device of a submerged gate as described in claim 7, characterized in that, In step S4, the rotation hinge point of the underwater drive device (2) is located and determined as follows: When the movable door flap (1) is fully closed, the rotation center of the ear plate (1b) is marked as point A'. With the rotation center O of the pivot (13) as the center, the lever arm L T The value of is used as the radius R1 to draw a circle, and the second circle (18) is obtained. The tangent line between point A' and the second circle (18) is drawn to determine the tangent point E, and the tangent line A'E is obtained. With the rotation center O of the pivot (13) as the center, the tension F L Using the value of as the radius R2, draw a circle to obtain the third circle (19). Draw the tangent line between point A and the third circle (19) to determine the point of tangency F, and obtain the tangent line AF. Extend tangent A'E and tangent AF to obtain intersection point G; With intersection point G as the center, and the length of the line segment GA' between intersection point G and point A' as the radius R3, draw a circle to obtain the fourth circle (22). The line AG connecting point A and intersection point G intersects the fourth circle (22) at point H. The length L of the line segment AH between point A and point H is the working stroke of the underwater drive device (2); The length of line segment HG between point H and intersection point G is the fully contracted length L of the underwater drive device (2). s L s =R3.

9. The refined positioning method for an underwater drive device of a submerged gate as described in claim 8, characterized in that, When the total contraction length L s When the underwater drive device (2) is fully retracted, the upper lifting head (24) is arranged to meet the external geometric dimensions of the upper lifting head (24), and the cylinder of the underwater drive device (2) is located outside the cantilever support (4), an upper lifting head (24) is provided on the upper part of the underwater drive device (2); the thickness of the upper lifting head (24) is δ. The cantilever support (4) is composed of a top plate (27) and double hanging plates (28) welded together. The width between the double hanging plates (28) is adapted to the thickness δ of the upper hanging head (24), and the intersection point G is located on the center line of the rotation pin (41) of the upper hanging head (24) and the double hanging plates (28).

10. The refined positioning method for an underwater drive device of a submerged gate as described in claim 8, characterized in that, When the total contraction length L s When the underwater drive device (2) is fully retracted and the upper lifting head is arranged to meet the external geometric dimensions, and the cylinder of the underwater drive device (2) is located inside the cantilever support (4), an upper lifting head (24) is provided on the upper part of the underwater drive device (2). The cantilever support (4) is composed of a top plate (27) and a double hanging plate (28) welded together. The width between the double hanging plates (28) is adapted to the outer diameter of the cylinder of the underwater drive device (2), and the intersection point G is located on the center line of the rotating pin (41) of the upper lifting head (24) and the double hanging plate (28).

11. The refined positioning method for an underwater drive device of a submerged gate as described in claim 8, characterized in that, When the total contraction length L s The shape and geometric dimensions of the upper lifting head of the underwater drive device (2) when fully retracted cannot be met. The underwater drive device (2) is designed according to the central rotation hinge point, and a central fixed hinge cylinder (32) is provided on the underwater drive device (2). The cantilever support (4) is composed of a top plate (27) and double hanging plates (28) welded together. A slot (31) is provided at the downstream end of the top plate (27) to form a clearance structure. The width between the double hanging plates (28) is adapted to the outer diameter of the middle fixed hinge cylinder (32), and the intersection point G is located on the center line of the rotation pin (41) of the middle fixed hinge cylinder (32) and the double hanging plates (28).

12. The refined positioning method for an underwater drive device of a submerged gate as described in claim 8, characterized in that, When the total contraction length L s If the external geometric dimensions of the upper lifting head cannot be met when the underwater drive device (2) is fully retracted, the following method is used when repositioning and determining the upper end rotation hinge point of the underwater drive device (2): With intersection point G as the center, the length L of the upper crane head is arranged to meet the geometric dimensions of the underwater drive device (2) when fully retracted. s `and the total contraction length L s The difference △L s Draw a circle with radius R4 to obtain the fifth circle (33). Extend the line AG connecting point A and intersection point G to intersect the fifth circle (33) at point I. The line A'G connecting the extended point A' and the intersection point G intersects the fifth circle (33) at point J; The points on the arc (35) between the intersection point I and the intersection point J on the fifth circle (33) can meet the requirements for arranging the upper lifting head when the underwater drive device (2) is fully retracted; The cantilever support (4) is welded together from a top plate (27) and a double hanging plate (28). The top plate (27) is composed of a lower horizontal section (36), a reverse arc section (37), a forward arc section (38), and an upper horizontal section (39). A bottom water seal device (40) is provided at the bottom of the downstream side of the flow gate (3). The length b of the lower horizontal section (36) is greater than the width c of the bottom water seal device (40). An upper lifting head (24) is provided on the upper part of the underwater drive device (2). The width between the double lifting plates (28) is adapted to the outer diameter of the cylinder of the underwater drive device (2). The hinge point of the upper lifting head (24) and the double lifting plates (28) is located on the arc (35) between the intersection point I and the intersection point J.

13. The refined positioning method for an underwater drive device of a submerged gate as described in claim 1, characterized in that, The underwater drive unit (2) adopts a deep-diving hydraulic press, which has an oil pump (29) with a ring structure.

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