A method for accurately determining the technical parameters and layout dimensions of a swing hydraulic press

Abstract

The present invention discloses a method for accurately determining the technical parameters and layout dimensions of a swing type hydraulic press. The hydraulic press opening force is assumed according to the size of the arc door. The center position of the upper hinge point is determined by using the principle that the intersection of the opening force lines when the arc door is fully opened and fully closed is unique. Then, the length from the center of the cylinder hinge point to the lower lifting head is determined according to the distance between the center position of the upper hinge point and the center of the lifting lug when the arc door is fully opened. Then, the cylinder working stroke is determined according to the difference in the radius of the concentric circles as the maximum length of the piston rod in the cylinder. Subsequently, the elevation of the hydraulic pump station installation platform and the swing amplitude range are successively determined according to the height from the center of the cylinder support hinge seat to the outer edge of the bottom plate and the height of the cylinder support frame, thereby determining the layout dimensions such as the elevation of the maintenance bridge crane track platform, the width of the hydraulic pump room in the water flow direction, and the vertical height. The method can make the opening and closing capacity of the swing type hydraulic press required for the fully opened and closed states of the arc door the same, shorten the size of the hydraulic pump room or the installation platform of the cylinder support frame, and save engineering investment.

Description

Technical Field

[0001] The invention relates to a method for accurately determining technical parameters and layout dimensions of a swing type hydraulic press, and belongs to the technical field of metal structures of hydropower and water conservancy projects. Background Art

[0002] At present, for submerged arc gates with high water heads and above in hydropower and water conservancy projects, the upward lifting force generated by the high-speed water flow is so large that the gate’s own weight is not enough to overcome the closing resistance. Usually, it is necessary to add counterweights or increase the downward pressure of the hydraulic press to overcome the resistance and successfully close the gate. Therefore, submerged arc gates are generally operated by a swinging hydraulic press with a double-acting piston rod that can swing back and forth along the water flow.

[0003] For the swing hydraulic press, a structural type with two upper and lower movable hinges is usually adopted. The lower hinge is the center of the lifting point where the lower lifting head of the hydraulic press is connected to the arc door lifting ear, and the upper hinge is the center of the supporting hinge shaft after the cylinder is connected to the support hinge seat. Since the setting position of the supporting hinge shaft on the cylinder is determined according to the position of the upper hinge, the force arm of the hydraulic press cylinder will be different if the upper hinge setting position is different, which makes the opening and closing capacity and stroke in the basic technical parameters of the hydraulic press vary greatly, resulting in different safety margins of the opening and closing torque of the hydraulic press, as well as different equipment layout dimensions such as the size of the hydraulic press pump room and the setting height of the maintenance bridge crane track. Therefore, whether the position of the hinge on the swing hydraulic press is determined reasonably is directly related to the project safety and investment.

[0004] As for the method for determining the upper hinge point of the swing hydraulic press, the traditional method is to use a trial method based on engineering experience and then calculate the opening and closing capacity and stroke according to the torque of the hydraulic press in the fully open and fully closed states. Usually, an upper hinge position is preset at the top of the arc door in the open state, and the upper hinge point is connected with the center of the lifting lug when the arc door is in the fully open state to form the fully closed action line of the hydraulic press. The distance between the rotation center of the arc door support hinge and the fully closed action line of the hydraulic press is measured to determine the force arm when the arc door is in the fully open state. The upper hinge point is connected with the center of the lifting lug when the arc door is in the fully closed state to form the fully open action line of the hydraulic press. The distance between the rotation center of the arc door support hinge and the fully open action line of the hydraulic press is measured to determine the force arm when the arc door is in the fully closed state. The hydraulic press determined by this method has a large difference in the opening and closing capacity required when the arc door is fully opened or fully closed, and the opening and closing torque margin when fully opened or fully closed is also large, which makes the technical indicators of the hydraulic press poor, the size of the equipment layout increases, and the project investment is increased. Sometimes, the upper hinge point position needs to be modified repeatedly for many times, which is not conducive to improving the design efficiency. Therefore, the existing technology is still not perfect and needs to be further improved. Summary of the invention

[0005] The purpose of the present invention is to provide a method for accurately determining the technical parameters and layout dimensions of a swing hydraulic press, so that the opening and closing capacities of the swing hydraulic press required for the fully open and closed states of the arc gate are the same, with good technical and economic performance. The layout of related equipment such as the cylinder, cylinder support frame, cylinder support hinge seat, hydraulic pump station and control cabinet of the swing hydraulic press is compact and reasonable, shortening the size of the hydraulic pump room or the cylinder support frame installation platform, saving project investment.

[0006] In order to solve the above technical problems, the present invention adopts the following technical solutions:

[0007] S100, first determine the rotation center O1 of the radial door hinge, and the corresponding lifting eye centers O2 and O3 when the radial door is fully closed and fully opened;

[0008] S200, according to the calculation formula F of the gate opening force in the "Design Specifications for Steel Gates of Hydropower Projects" (NB35055) or the "Design Specifications for Steel Gates of Water Conservancy and Hydropower Projects" (SL74) Q =[n T (T zd r0+T zs r1)+n` G Gr2+G j R j +P x r4] / R2 reversely deduce the force arm l1 required to open the arc door when it is in the fully closed state. The reverse calculation of the force arm l1 includes the following steps:

[0009] S200-1, determine the gravity G and counterweight G according to the size of the arc gate (width × height × design water head / 5000), the radius of the arc surface R, and the height from the hinge rotation center O1 to the bottom sill H. j , using the analogy method to assume that the radial gate opening force F Q =T;

[0010] S200-2, determine the hinge friction resistance T when the arc door is fully closed zd , according to the radius of the pivot joint, determine the friction resistance T of the pivot joint zd The lever arm r0 to the pivot rotation center O1;

[0011] S200-3, determine the water seal friction resistance T when the arc door is fully closed zs , according to the distance from the center of the water seal head to the rotation center of the hinge O1, determine the water seal friction resistance T zs The lever arm r1 to the pivot rotation center O1;

[0012] S200-4, determining the force arm r2 from the gravity G to the support hinge rotation center O1 according to the vertical distance from the center of gravity to the support hinge rotation center O1 when the arc door is in a fully closed state;

[0013] S200-5, according to the counterweight Gj The placement position determines the counterweight G when the arc door is fully closed. j The arm R to the pivot rotation center O1 j ;

[0014] S200-6, according to the downward suction force P when the radial gate is opened x , determine the suction force P x The lever arm r4 to the pivot rotation center O1;

[0015] S200-7, according to the door opening force calculation formula T = [n T (T zd r0+T zs r1)+n` G Gr2+G j r3+P x r4] / l1

[0016] l1=[n T (T zd r0+T zs r1)+n` G Gr2+G j r3+P x r4] / T;

[0017] S200-8, draw a circle O1 with the arc door hinge rotation center O1 as the center and R1=l1 as the radius;

[0018] S300, according to the calculation formula F of the gate opening force in the "Design Specifications for Steel Gates of Hydropower Projects" (NB35055) or the "Design Specifications for Steel Gates of Water Conservancy and Hydropower Projects" (SL74) Q =[n T (T zd r0+T zs r1)+n` G Gr2+G j R1+P x r4] / R2 reversely calculates the required force arm l2 when the arc door is fully open. The reverse calculation of the force arm l2 includes the following steps:

[0019] ``

[0020] S300-1, determine the hinge friction resistance T when the radial gate is fully open zd , rotational friction resistance T zd The lever arm r0 to the pivot rotation center O1;

[0021] S300-2, determine the water seal friction resistance T' when the arc door is fully open zs According to the distance from the center of the water seal head to the rotation center of the hinge O1, determine the water seal friction resistance T` zsThe lever arm r`1 to the pivot rotation center O1;

[0022] S300-3, determining the lever arm r'2 from the gravity G to the support hinge rotation center O1 according to the vertical distance from the center of gravity to the support hinge rotation center O1 when the arc door is in the fully open state;

[0023] S300-4, according to the counterweight G j The placement position determines the counterweight G when the arc door is fully open. j The arm of force from the pivot rotation center O1

[0024] R j ;

[0025] S300-5, according to the door opening force calculation formula T = [n T (T` zd r0+T` zs r`1)+n` G Gr`2+G j r`3] / l2

[0026] l2=[n T (T` zd r0+T` zs r`1)+n` G Gr`2+G j r`3] / T;

[0027] S300-6, draw a concentric circle O1 with the arc door hinge rotation center O1 as the center and R2=l2 as the radius;

[0028] S400, draw a tangent line A with the circle O1 of radius R2=l2 from the center of the lifting ear O2 when the arc door is fully opened, draw a tangent line B with the concentric circle O1 of radius R1=l1 from the center of the lifting ear O3 when the arc door is fully closed, extend the tangent line A upwards and intersect the tangent line B at point O4, which is the center position of the upper hinge point of the oil cylinder, and the length of the line segment O2O4 is the length L1 from the center of the hinge point of the oil cylinder to the center of the lower lifting head;

[0029] S500, draw a circle O4 with O4 as the center and the length of line segment O2O4 as the radius R3, circle O4 and line segment O3O4 intersect at point P1, according to the reduced length of the cylinder in the process from full closing to full opening of the arc door, the maximum retracted length of the piston rod (the cylinder working stroke L), the maximum retracted length of the piston rod = line segment O3O4-line segment O2O4, according to the equal radius of the circle, line segment O2O4 = line segment O4P1, the maximum retracted length of the piston rod = line segment O3O4-line segment O4P1 = line segment P1O3, the length of line segment P1O3 is the cylinder working stroke L;

[0030] S600, determine the length L2 of the cylinder in the fully open state according to the hydraulic press opening force T, the length L1 from the center of the cylinder hinge point to the center of the lower lifting head, and the working stroke L. The length from the center of the cylinder hinge point to the upper outer edge of the cylinder = the length L2 of the cylinder in the fully open state - the length L1 from the center of the cylinder hinge point to the center of the lower lifting head. According to the maximum swing angle of the arc door from the fully closed to the fully opened process with the length from the center of the cylinder hinge point to the upper outer edge of the cylinder as the radius, determine the maximum height and swing range of the outer edge of the cylinder from the center of the cylinder hinge point. The length L1 from the center of the cylinder hinge point to the center of the lower lifting head = R3, and the length from the center of the cylinder hinge point to the upper outer edge of the cylinder = L2-R 3. With O4 as the center and R4=L2-R3 as the radius, draw a concentric circle O4. The extended straight line P1O4 intersects the concentric circle O4 with the radius R4 at point P2. Point P2 is the position of the upper outer edge of the hydraulic cylinder when the arc door is fully closed. The extended straight line O2O4 intersects the concentric circle O4 with the radius R4 at point P3. Point P3 is the position of the upper outer edge of the hydraulic cylinder when the arc door is fully open. The position corresponding to the upper outer edge of the cylinder when the arc door is fully open and fully closed is the swing range of the cylinder. According to the positions of points P2 and P3, determine the maximum swing angle α of the cylinder during operation and the maximum height H1 of the outer edge of the cylinder from the center of the cylinder hinge point;

[0031] S700, based on the elevation of the hydraulic pump station installation platform being the same as the elevation of the bottom plate of the cylinder support frame or the bottom plate of the cylinder support hinge seat, determine that the elevation of the hydraulic pump station installation platform = the elevation of the center of the upper hinge point of the cylinder O4 - the height from the center of the cylinder support hinge seat (coincides with O4) to the outer edge of its bottom plate H2 - the height of the cylinder support frame H3 or the elevation of the hydraulic pump station installation platform = the elevation of the center of the upper hinge point of the cylinder O4 - the height from the center of the cylinder support hinge seat (coincides with O4) to the outer edge of its bottom plate H2.

[0032] S800, according to the height of the center of the hinge point O4 on the cylinder + (the length of the hydraulic press in the fully open state L2-the working stroke L) + the upper lift h of the maintenance bridge hanging rail, the height H4 from the top of the maintenance bridge hanging rail to the installation platform of the hydraulic pump room is obtained, and the total vertical height H of the hydraulic pump room is 总 =H4+the height of the maintenance bridge crane itself H5+the space height above the top required for installing the maintenance bridge crane H6.

[0033] S900, according to the cylinder diameter and the maximum swing angle α, determine the width B1 from the upstream outer edge of the cylinder to the intersection O4 and the width B2 from the downstream outer edge of the cylinder to the intersection O4 in the downstream direction of the flow; according to the width B`1 from the upstream outer edge of the cylinder frame to the intersection O4 and the width B`2 from the downstream outer edge of the cylinder frame to the intersection O4, and considering the safety space width B3 and the control cabinet width B4, the width B of the hydraulic pump room in the downstream direction of the flow is ≥Max(B1, B`1)+Max(B2, B`2)+2B3+B4, and the width C of the cylinder support frame installation platform in the downstream direction of the flow is ≥Max(B1, B`1)+Max(B2, B`2)+2B3.

[0034] Compared with the prior art, the present invention first assumes the door-opening force of the swing hydraulic press according to the size of the arc door (width×height×water head / 5000), and determines the center position of the upper hinge point based on the principle that the intersection of the door-opening force lines when the arc door is fully opened and fully closed is unique. Then, the length from the center of the cylinder hinge point to the lower hanging head is determined according to the distance between the center position of the upper hinge point and the center of the lifting ear when the arc door is fully opened. Then, the working stroke of the cylinder is determined according to the difference in the radii of the concentric circles as the maximum length of the piston rod in the cylinder for retraction and extension. Subsequently, the elevation of the installation platform of the hydraulic pump room and the swing amplitude range are successively determined according to the height from the center of the cylinder support hinge seat to the outer edge of the bottom plate and the height of the cylinder support frame. , thereby determining the layout dimensions such as the elevation of the maintenance bridge crane track platform, the width of the hydraulic pump room along the water flow direction and the vertical height. Because the opening and closing torque required when the arc door is in the fully open and fully closed states is considered as equal opening force, the opening and closing torque margin when fully open or fully closed is the same and can be considered in advance, which can improve the safety of the entire operation process of the hydraulic press, and the technical indicators of the hydraulic press are well matched. The cylinder, cylinder support frame, cylinder support hinge seat, hydraulic pump station, control cabinet and maintenance bridge crane and other related equipment of the swing hydraulic press are compactly and reasonably arranged, which effectively shortens the size of the hydraulic pump room or cylinder support frame installation platform and saves project investment. BRIEF DESCRIPTION OF THE DRAWINGS

[0035] Figure 1 This is a schematic diagram of the first step of applying the first embodiment of the present invention to a deep hole arc door;

[0036] Figure 2 It is a schematic diagram of the second step of the application of the first embodiment of the present invention in a deep hole arc door;

[0037] Figure 3 It is a schematic diagram of the third step of applying the first embodiment of the present invention to a deep hole arc door;

[0038] Figure 4 It is a schematic diagram of the fourth step of applying the first embodiment of the present invention to a deep hole arc door;

[0039] Figure 5 It is a schematic diagram of the fifth step of applying the first embodiment of the present invention to a deep hole arc door;

[0040] Figure 6 It is a schematic diagram of the sixth step of applying the first embodiment of the present invention to a deep hole arc door;

[0041] Figure 7 Schematic diagram of the fully closed state of the swing hydraulic press applied to the deep hole arc door in Embodiment 1 of the present invention;

[0042] Figure 8 Schematic diagram of the fully open state of the swing hydraulic press applied to the deep hole arc door in the first embodiment of the present invention;

[0043] Fig. 9Schematic diagram of a cylinder support hinge seat of a swing hydraulic press applied to a deep hole arc door in Embodiment 1 of the present invention;

[0044] Fig.10 It is a schematic diagram of a cylinder support frame of a swing hydraulic press applied to a deep hole arc door in Embodiment 1 of the present invention;

[0045] Fig.11 It is a schematic diagram of the seventh step of applying the first embodiment of the present invention to a deep hole arc door;

[0046] Fig.12 It is a schematic diagram of the eighth step of applying the first embodiment of the present invention to a deep hole arc door;

[0047] Fig.13 It is a ninth step schematic diagram of the application of the first embodiment of the present invention in a deep hole arc door;

[0048] Fig.14 This is a schematic diagram of the first step of applying the second embodiment of the present invention to a submerged hole arc gate with a medium to high water head;

[0049] Fig.15 This is a schematic diagram of the second step of the application of the embodiment 2 of the present invention to the submerged hole arc gate with medium and high water head;

[0050] Fig.16 It is a schematic diagram of the third step of the application of the embodiment 2 of the present invention in the submerged hole arc gate with medium and high water head;

[0051] Fig.17 It is a schematic diagram of the fourth step of the application of the embodiment 2 of the present invention in the submerged hole arc gate with medium and high water head;

[0052] Fig.18 It is a schematic diagram of the fifth step of the application of the embodiment 2 of the present invention to the submerged hole arc gate with medium and high water head;

[0053] Fig.19 Schematic diagram of the fully closed state of the swing hydraulic press applied to the medium-high head submerged hole arc gate in Embodiment 2 of the present invention;

[0054] Fig. 20 Schematic diagram of the fully open state of the swing hydraulic press applied to the medium-high head submerged hole arc gate in the second embodiment of the present invention;

[0055] Fig.21 Schematic diagram of a cylinder support hinge seat of a swing hydraulic press applied to a submerged hole arc gate with a medium and high head according to Embodiment 2 of the present invention;

[0056] Fig. 22 Schematic diagram of a cylinder support frame of a swing hydraulic press applied to a submerged hole arc gate with a medium and high head according to Embodiment 2 of the present invention;

[0057] Fig.23 It is a schematic diagram of the sixth step of the application of the embodiment 2 of the present invention in the submerged hole arc gate with medium and high water head;

[0058] Fig.24 It is a schematic diagram of the seventh step of the application of the embodiment 2 of the present invention to the submerged hole arc gate with medium and high water head;

[0059] Fig.25 It is a schematic diagram of the eighth step of the application of implementation scheme 2 of the present invention in the submerged hole arc gate with medium and high water heads.

[0060] Figures 1 to 25 In: 1-deep hole arc door, 2-swing hydraulic press, 3-door body, 4-hinge, 5-water seal device, 6-cylinder, 7-cylinder support frame, 8-cylinder hinge seat, 9-hydraulic pump station, 10-control cabinet, 11-maintenance bridge crane, 12-medium and high head submerged arc door, (1)-arc door hinge rotation center O1, (2)-the center position of the lifting lug when the arc door is fully open O2, (3)-the center position of the lifting lug when the arc door is fully closed O3, (4)-circle O1 with radius R1=l1, (5)-tangent A, (6)-concentric circle O1 with radius R2=l2, (7)-tangent B, (8)-length L1 from the center of the cylinder hinge point to the center of the lower lifting head, (9)-circle O4 with radius R3=L1, (10)-point P1, (11)-cylinder working stroke L, (12)-cylinder Length of the fully open state L2, (13) - concentric circle O4 with radius R4 = L2 - R3, (14) - point P2, (15) - point P3, (16) - maximum swing angle α, (17) - maximum height H1 of the outer edge of the cylinder from the center of the cylinder hinge, (18) - elevation of the hydraulic pump station installation platform, (19) - elevation of the bottom plate of the cylinder support frame, (20) - elevation of the center of the cylinder hinge O4, (21) - height H2 from the center of the cylinder support hinge (coinciding with O4) to the outer edge of its bottom plate, (22) - height H3 of the cylinder support frame, (23) - lift h of the maintenance bridge hanging rail, (24) - elevation of the top of the maintenance bridge hanging rail, (25) - height H4 from the top of the maintenance bridge hanging rail (24) to the elevation (18) of the hydraulic pump station installation platform, (26) - total vertical height H of the hydraulic pump room 总 、(27)-the height of the maintenance bridge crane itself H5、(28)-the space height above the top of the maintenance bridge crane required for installation H6、(29)-the width from the upstream outer edge of the cylinder to the intersection O4 B1、(30)-the width from the downstream outer edge of the cylinder to the intersection O4 B2、(31)-the width from the upstream outer edge of the cylinder frame to the intersection O4 B`1、(32)-the width from the downstream outer edge of the cylinder frame to the intersection O4 B`2、(33)-the width of the safety space B3、(34)-the width of the control cabinet B4、(35)-the width in the direction of water flow B、(36)-the elevation of the bottom plate of the cylinder support hinge seat、(37)-the width C of the cylinder support frame installation platform in the direction of water flow

[0061] The present invention will be further described below in conjunction with the accompanying drawings and specific embodiments. DETAILED DESCRIPTION

[0062] Embodiment 1 of the present invention: A method for accurately determining technical parameters and layout dimensions of a swing hydraulic press, characterized in that a deep hole arc door 1 is operated by a swing hydraulic press 2, the deep hole arc door 1 is composed of a door body 3, a support hinge 4, and a water seal device 5, the swing hydraulic press 2 is composed of an oil cylinder 6, an oil cylinder support frame 7, an oil cylinder support hinge seat 8, a hydraulic pump station 9 and a control cabinet 10, the installation and overhaul and maintenance of the swing hydraulic press 2 are operated by an overhaul bridge crane 11, and determining the basic technical parameters and layout dimensions of the swing hydraulic press 2 includes the following steps:

[0063] S100, first determine the rotation center O1(1) of the radial door hinge, and the corresponding lifting eye centers O2(2) and O3(3) when the radial door is fully opened and fully closed;

[0064] S200, according to the calculation formula F of the gate opening force in the "Design Specifications for Steel Gates of Hydropower Projects" (NB35055) or the "Design Specifications for Steel Gates of Water Conservancy and Hydropower Projects" (SL74) Q =[n T (T zd r0+T zs r1)+n` G Gr2+G j R j +P x r4] / R2 reversely deduce the force arm l1 required to open the arc door when it is in the fully closed state. The reverse calculation of the force arm l1 includes the following steps:

[0065] S200-1, determine the gravity G and counterweight G according to the size of the arc gate (width × height × design water head / 5000), the radius of the arc surface R, and the height from the hinge rotation center O1 to the bottom sill H. j , using the analogy method to assume that the radial gate opening force F Q =T;

[0066] S200-2, determine the hinge friction resistance T when the arc door is fully closed zd , according to the radius of the pivot joint, determine the friction resistance T of the pivot joint zd The lever arm r0 to the pivot rotation center O1;

[0067] S200-3, determine the water seal friction resistance T when the arc door is fully closed zs , according to the distance from the center of the water seal head to the rotation center of the hinge O1, determine the water seal friction resistance T zs The lever arm r1 to the pivot rotation center O1;

[0068] S200-4, determining the force arm r2 from the gravity G to the support hinge rotation center O1 according to the vertical distance from the center of gravity to the support hinge rotation center O1 when the arc door is in a fully closed state;

[0069] S200-5, according to the counterweight G j The placement position determines the counterweight G when the arc door is fully closed. j The arm R to the pivot rotation center O1 j ;

[0070] S200-6, according to the downward suction force P when the arc door is opened x , determine the suction force P x The lever arm r4 to the pivot rotation center O1;

[0071] S200-7, according to the door opening force calculation formula T = [n T (T zd r0+T zs r1)+n` G Gr2+G j r3+P x r4] / l1

[0072] l1=[n T (T zd r0+T zs r1)+n` G Gr2+G j r3+P x r4] / T;

[0073] S200-8, draw a circle O1 (4) with the arc door hinge rotation center O1 as the center and R1=l1 as the radius;

[0074] S300, according to the calculation formula F of the gate opening force in the "Design Specifications for Steel Gates of Hydropower Projects" (NB35055) or the "Design Specifications for Steel Gates of Water Conservancy and Hydropower Projects" (SL74) Q =[n T (T zd r0+T zs r1)+n` G Gr2+G j R j +P x r4] / R2 reversely calculates the required force arm l2 when the arc door is fully open. The reverse calculation of the force arm l2 includes the following steps:

[0075] ``

[0076] S300-1, determine the hinge friction resistance T when the radial gate is fully open zd , rotational friction resistance T zd The lever arm r0 to the pivot rotation center O1;

[0077] S300-2, determine the water seal friction resistance T' when the arc door is fully open zsAccording to the distance from the center of the water seal head to the rotation center of the hinge O1, determine the water seal friction resistance T` zs The lever arm r`1 to the pivot rotation center O1;

[0078] S300-3, determining the lever arm r'2 from the gravity G to the support hinge rotation center O1 according to the vertical distance from the center of gravity to the support hinge rotation center O1 when the arc door is in the fully open state;

[0079] S300-4, according to the counterweight G j The placement position determines the counterweight G when the arc door is fully open. j The arm of force from the pivot rotation center O1

[0080] R j ;

[0081] S300-5, according to the door opening force calculation formula T = [n T (T` zd r0+T` zs r`1)+n` G Gr`2+G j r`3] / l2

[0082] l2=[n T (T` zd r0+T` zs r`1)+n` G Gr`2+G j r`3] / T;

[0083] S300-6, draw a concentric circle O1 (6) with the arc door hinge rotation center O1 as the center and R2=l2 as the radius;

[0084] S400, draw a tangent A(5) to the circle O1 with radius R2=l2 from the center of the lifting eye O2 when the arc door is fully opened, draw a tangent B(7) to the concentric circle O1 with radius R1=l1 from the center of the lifting eye O3 when the arc door is fully closed, extend the tangent A(5) upwards and intersect the tangent B(7) at point O4, which is the center position of the upper hinge of the oil cylinder. The length of line segment O2O4 is the length L1(8) from the center of the hinge of the oil cylinder to the center of the lower lifting head;

[0085] S500, with O4 as the center and the length of line segment O2O4 as the radius R3, draw a circle O4 (9). Circle O4 intersects line segment O3O4 at point P1 (10). According to the reduction of the cylinder length in the process from fully closed to fully opened, the maximum retracted length of the piston rod (the cylinder working stroke L) is obtained. The maximum retracted length of the piston rod = line segment O3O4 - line segment O2O4. According to the equal radius of the circle, line segment O2O4 = line segment O4P1. The maximum retracted length of the piston rod = line segment O3O4 - line segment O4P1 = line segment P1O3. The length of line segment P1O3 is the cylinder working stroke L (11).

[0086] S600, determine the length L2(12) of the cylinder in the fully open state according to the hydraulic press opening force T, the length L1(8) from the center of the cylinder hinge point to the center of the lower hanging head, and the working stroke L. The length from the center of the cylinder hinge point to the upper outer edge of the cylinder = the length L2(12) of the cylinder in the fully open state - the length L1(8) from the center of the cylinder hinge point to the center of the lower hanging head. According to the maximum swing angle of the arc door from the fully closed to the fully opened process with the length from the center of the cylinder hinge point to the upper outer edge of the cylinder as the radius, determine the maximum height and swing range of the outer edge of the cylinder from the center of the cylinder hinge point. The length L1 from the center of the cylinder hinge point to the center of the lower hanging head = R3, and the length from the center of the cylinder hinge point to the upper outer edge of the cylinder = L2-R3. With O4 as the center of the circle, A concentric circle O4 (13) is made with R4=L2-R3 as radius, and the extended straight line P1O4 intersects the concentric circle O4 with radius R4 at point P2 (14). Point P2 is the position of the upper outer edge of the hydraulic cylinder when the arc door is fully closed. The extended straight line O2O4 intersects the concentric circle O4 with radius R4 at point P3 (15). Point P3 (15) is the position of the upper outer edge of the hydraulic cylinder when the arc door is fully open. The position corresponding to the upper outer edge of the cylinder when the arc door is fully open and fully closed is the swing range of the cylinder. According to the positions of point P2 (14) and point P3 (15), the maximum swing angle α (16) of the cylinder during operation and the maximum height H1 (17) of the outer edge of the cylinder from the center of the cylinder hinge are determined;

[0087] S700, based on the fact that the elevation of the hydraulic pump station installation platform (18) is the same as the elevation of the bottom plate of the cylinder support frame (19), determine that the elevation of the hydraulic pump station installation platform (18) = the elevation of the center of the hinge point on the cylinder O4 (20) - the height from the center of the cylinder support hinge seat (coinciding with O4) to the outer edge of its bottom plate H2 (21) - the height of the cylinder support frame H3 (22).

[0088] S800, according to the height of the center of the hinge point O4 on the cylinder (20) + (the length of the hydraulic press in the fully open state L2 (12) - the working stroke L (11)) + the lift h (23) of the maintenance bridge hanging rail, the height H4 (25) from the top elevation of the maintenance bridge hanging rail (24) to the elevation of the hydraulic pump station installation platform (18) is obtained, and the total vertical height of the hydraulic pump room H 总(26) = H4 (25) + the height of the maintenance bridge crane itself H5 (27) + the space height above the top of the maintenance bridge crane required for installation H6 (28).

[0089] S900, according to the cylinder diameter and the maximum swing angle α(16), determine the width B1(29) from the upstream outer edge of the cylinder to the intersection O4 and the width B2(30) from the downstream outer edge of the cylinder to the intersection O4 in the downstream direction of the flow; according to the width B`1(31) from the upstream outer edge of the cylinder frame to the intersection O4 and the width B`2(32) from the downstream outer edge of the cylinder frame to the intersection O4, and considering the safety space width B3(33) and the control cabinet width B4(34), the width B(35) of the hydraulic pump room in the downstream direction of the flow is ≥Max(B1, B`1)+Max(B2, B`2)+2B3+B4.

[0090] Embodiment 2: A method for accurately determining technical parameters and layout dimensions of a swing hydraulic press, characterized in that a medium-high head submerged hole arc door 12 is operated by a swing hydraulic press 2, the medium-high head submerged hole arc door 12 is composed of a door body 3, a support hinge 4, and a water seal device 5, the swing hydraulic press 2 is composed of an oil cylinder 6, an oil cylinder support frame 7, an oil cylinder support hinge seat 8, a hydraulic pump station 9 and a control cabinet 10, the installation and overhaul and maintenance of the swing hydraulic press 2 is operated by an overhaul bridge crane 11, and determining the basic technical parameters and layout dimensions of the swing hydraulic press 2 includes the following steps:

[0091] S100, first determine the rotation center O1(1) of the radial door hinge and the corresponding lifting eye center O3(3) when the radial door is in a fully closed state;

[0092] S200, according to the calculation formula F of the gate opening force in the "Design Specifications for Steel Gates of Hydropower Projects" (NB35055) or the "Design Specifications for Steel Gates of Water Conservancy and Hydropower Projects" (SL74) Q =[n T (T zd r0+T zs r1)+n` G Gr2+G j R j +P x r4] / R2 reversely deduce the force arm l1 required to open the arc door when it is in the fully closed state. The reverse calculation of the force arm l1 includes the following steps:

[0093] S200-1, determine the gravity G and counterweight G according to the size of the arc gate (width × height × design water head / 5000), the radius of the arc surface R, and the height from the hinge rotation center O1 to the bottom sill H. j , using the analogy method to assume that the radial gate opening force F Q =T;

[0094] S200-2, determine the hinge friction resistance T when the arc door is fully closed zd, according to the radius of the pivot joint, determine the friction resistance T of the pivot joint zd The lever arm r0 to the pivot rotation center O1;

[0095] S200-3, determine the water seal friction resistance T when the arc door is fully closed zs , according to the distance from the center of the water seal head to the rotation center of the hinge O1, determine the water seal friction resistance T zs The lever arm r1 to the pivot rotation center O1;

[0096] S200-4, determining the force arm r2 from the gravity G to the support hinge rotation center O1 according to the vertical distance from the center of gravity to the support hinge rotation center O1 when the arc door is in a fully closed state;

[0097] S200-5, according to the counterweight G j The placement position determines the counterweight G when the arc door is fully closed. j The arm R to the pivot rotation center O1 j ;

[0098] S200-6, according to the downward suction force P when the arc door is opened x , determine the suction force P x The lever arm r4 to the pivot rotation center O1;

[0099] S200-7, according to the door opening force calculation formula T = [n T (T zd r0+T zs r1)+n` G Gr2+G j r3+P x r4] / l1

[0100] l1=[n T (T zd r0+T zs r1)+n` G Gr2+G j r3+P x r4] / T;

[0101] S200-8, draw a circle O1 (4) with the arc door hinge rotation center O1 as the center and R1=l1 as the radius;

[0102] S300, determine the corresponding lifting eye center O2 (2) when the arc door is fully open, and draw a tangent B (7) to the circle O1 with radius R1 = l1 through the lifting eye center O3 when the arc door is fully closed;

[0103] S400, according to the calculation formula F of the gate opening force in the "Design Specifications for Steel Gates of Hydropower Projects" (NB35055) or the "Design Specifications for Steel Gates of Water Conservancy and Hydropower Projects" (SL74) Q=[n T (T zd r0+T zs r1)+n` G Gr2+G j R j +P x r4] / R2 reversely calculates the required force arm l2 when the arc door is fully open. The reverse calculation of the force arm l2 includes the following steps:

[0104] ``

[0105] S400-1, determine the hinge friction resistance T when the arc door is fully open zd , rotational friction resistance T zd The lever arm r0 to the pivot rotation center O1;

[0106] S400-2, determine the water seal friction resistance T' when the arc door is fully open zs According to the distance from the center of the water seal head to the rotation center of the hinge O1, determine the water seal friction resistance T` zs The lever arm r`1 to the pivot rotation center O1;

[0107] S400-3, determining the force arm r'2 from the gravity G to the support hinge rotation center O1 according to the vertical distance from the center of gravity to the support hinge rotation center O1 when the arc door is in the fully open state;

[0108] S400-4, according to the counterweight G j The placement position determines the counterweight G when the arc door is fully open. j The arm of force from the pivot rotation center O1

[0109] R j ;

[0110] S400-5, according to the door opening force calculation formula T = [n T (T` zd r0+T` zs r`1)+n` G Gr`2+G j r`3] / l2

[0111] l2=[n T (T` zd r0+T` zs r`1)+n` G Gr`2+G j r`3] / T;

[0112] S400-6, draw a concentric circle O1 (6) with the arc door hinge rotation center O1 as the center and R2=l2 as the radius;

[0113] S400-7, draw a tangent A(5) with the radius R2=l2 concentric with the lifting eye center O2 when the arc door is fully opened, and extend the tangent A(5) upward to intersect the tangent B(7) at point O4. Point O4 is the center of the upper hinge of the oil cylinder. The length of the line segment O2O4 is the length L1(8) from the center of the hinge of the oil cylinder to the center of the lower lifting head.

[0114] S500, with O4 as the center and the length of line segment O2O4 as the radius R3, draw a circle O4 (9). Circle O4 intersects line segment O3O4 at point P1 (10). According to the reduction of the cylinder length in the process from fully closed to fully opened, the maximum retracted length of the piston rod (the cylinder working stroke L) is obtained. The maximum retracted length of the piston rod = line segment O3O4 - line segment O2O4. According to the equal radius of the circle, line segment O2O4 = line segment O4P1. The maximum retracted length of the piston rod = line segment O3O4 - line segment O4P1 = line segment P1O3. The length of line segment P1O3 is the cylinder working stroke L (11).

[0115] S600, determine the length L2(12) of the cylinder in the fully open state according to the hydraulic press opening force T, the length L1(8) from the center of the cylinder hinge point to the center of the lower hanging head, and the working stroke L. The length from the center of the cylinder hinge point to the upper outer edge of the cylinder = the length L2(12) of the cylinder in the fully open state - the length L1(8) from the center of the cylinder hinge point to the center of the lower hanging head. According to the maximum swing angle of the arc door from the fully closed to the fully opened process with the length from the center of the cylinder hinge point to the upper outer edge of the cylinder as the radius, determine the maximum height and swing range of the outer edge of the cylinder from the center of the cylinder hinge point. The length L1 from the center of the cylinder hinge point to the center of the lower hanging head = R3, and the length from the center of the cylinder hinge point to the upper outer edge of the cylinder = L2-R3. With O4 as the center of the circle, A concentric circle O4 (13) is made with R4=L2-R3 as radius, and the extended straight line P1O4 intersects the concentric circle O4 with radius R4 at point P2 (14). Point P2 is the position of the upper outer edge of the hydraulic cylinder when the arc door is fully closed. The extended straight line O2O4 intersects the concentric circle O4 with radius R4 at point P3 (15). Point P3 (15) is the position of the upper outer edge of the hydraulic cylinder when the arc door is fully open. The position corresponding to the upper outer edge of the cylinder when the arc door is fully open and fully closed is the swing range of the cylinder. According to the positions of point P2 (14) and point P3 (15), the maximum swing angle α (16) of the cylinder during operation and the maximum height H1 (17) of the outer edge of the cylinder from the center of the cylinder hinge are determined;

[0116] S700, based on the fact that the elevation of the hydraulic pump station installation platform (18) is the same as the elevation of the bottom plate of the cylinder support hinge seat (36), determine that the elevation of the hydraulic pump station installation platform (18) = the elevation of the center of the hinge point on the cylinder O4 (20) - the height from the center of the cylinder support hinge seat (coinciding with O4) to the outer edge of its bottom plate H2 (21).

[0117] S800, according to the cylinder diameter and the maximum swing angle α(16), determine the width B1(29) from the upstream outer edge of the cylinder to the intersection O4 and the width B2(30) from the downstream outer edge of the cylinder to the intersection O4 in the downstream direction of the flow; according to the width B`1(31) from the upstream outer edge of the cylinder frame to the intersection O4 and the width B`2(32) from the downstream outer edge of the cylinder frame to the intersection O4, and considering the safety space width B3(33), determine that the width C(37) of the cylinder support frame mounting platform in the downstream direction of the flow is ≥Max(B1, B`1)+Max(B2, B`2)+2B3.

Claims

1. A method for accurately determining the technical parameters and layout dimensions of a swing hydraulic press. The arc door is operated by a swing hydraulic press. The arc door is composed of a door body, a support hinge, and a water seal device. The swing hydraulic press is composed of an oil cylinder, an oil cylinder support frame, an oil cylinder support hinge seat, a hydraulic pump station, and a control cabinet. The installation, overhaul, and maintenance of the swing hydraulic press are operated by an overhaul bridge crane. The characteristics are: Determining the basic technical parameters and layout dimensions of the swing hydraulic press includes the following steps: S100, determining the rotation center O1 of the arc door hinge, the center O2 of the lifting lug when the arc door is fully closed, and the center O3 of the lifting lug when the arc door is fully opened; S200, according to the door opening force calculation formula F Q =[n T (T zd r0+T zs r1)+n` G Gr2+G j R j +P x r4] / R1 reversely calculates the force arm l1 required to open the arc door when it is in the fully closed state; step S200, the reverse calculation of the force arm l1 includes the following steps: S200-1, determine the gravity G and counterweight G according to the size of the arc door, the radius R of the arc surface, and the height H from the hinge rotation center O1 to the bottom sill. j , using the analogy method to assume that the radial gate opening force F Q =T; S200-2, determine the hinge friction resistance T when the arc door is fully closed zd , according to the radius of the pivot joint, determine the friction resistance T of the pivot joint zd The lever arm r0 to the pivot rotation center O1; S200-3, determine the water seal friction resistance T when the arc door is fully closed zs , according to the distance from the center of the water seal head to the rotation center of the hinge O1, determine the water seal friction resistance T zs The lever arm r1 to the pivot rotation center O1; S200-4, determining the force arm r2 from the gravity G to the support hinge rotation center O1 according to the vertical distance from the center of gravity to the support hinge rotation center O1 when the arc door is in a fully closed state; S200-5, according to the counterweight G j The placement position determines the counterweight G when the arc door is fully closed. j The arm R to the pivot rotation center O1 j ; S200-6, according to the downward suction force P when the arc door is opened x , determine the suction force P x The lever arm r4 to the pivot rotation center O1; S200-7, according to the door opening force calculation formula S200-8, draw a circle O1 with the arc door hinge rotation center O1 as the center and R1=l1 as the radius; S300, according to the door opening force calculation formula F Q =[n T (T zd r0+T zs r1)+n` G Gr2+G j R j +P x r4] / R2 reversely calculates the required force arm l2 when the arc door is in the fully open state; step S300, the force arm l2 reverse calculation includes the following steps: S300-1, determine the hinge friction resistance T ` when the radial gate is fully open zd , rotational friction resistance T ` zd The lever arm r0 to the pivot rotation center O1; S300-2, determine the water seal friction resistance T' when the arc door is fully open zs According to the distance from the center of the water seal head to the rotation center of the hinge O1, determine the water seal friction resistance T` zs The lever arm r`1 to the pivot rotation center O1; S300-3, determining the lever arm r'2 from the gravity G to the support hinge rotation center O1 according to the vertical distance from the center of gravity to the support hinge rotation center O1 when the arc door is in the fully open state; S300-4, according to the counterweight G j The placement position determines the counterweight G when the arc door is fully open. j The lever arm R' to the pivot rotation center O1 j ; S300-5, according to the door opening force calculation formula S300-6, draw a concentric circle O1 with the arc door hinge rotation center O1 as the center and R2=l2 as the radius; S400, draw a tangent line A with the center of the lifting ear O2 when the arc door is fully open and a concentric circle O1 with a radius of R2 = l2, draw a tangent line B with the center of the lifting ear O3 when the arc door is fully closed and a circle O1 with a radius of R1 = l1, extend the tangent line A upward and intersect the tangent line B at point O4, point O4 is the center position of the upper hinge point of the oil cylinder, and the length of the line segment O2 O4 is the length L1 from the center of the hinge point of the oil cylinder to the center of the lower lifting head; S500, draw a circle O4 with O4 as the center and the length of line segment O2O4 as the radius R3. Circle O4 intersects line segment O3O4 at point P1. According to the reduction of the cylinder in the process from full closing to full opening of the arc door, the maximum contraction length of the piston rod is the maximum contraction length of the piston rod. The maximum contraction length of the piston rod = line segment O3O4-line segment O2O4. According to the equal radius of the circle, line segment O2O4 = line segment O4P1. The maximum contraction length of the piston rod = line segment O3O4-line segment O4P1 = line segment P1O3. The length of line segment P1O3 is the working stroke L of the cylinder. S600, determine the length L2 of the cylinder in the fully open state according to the hydraulic press opening force T, the length L1 from the center of the cylinder hinge point to the center of the lower lifting head, and the working stroke L. The length from the center of the cylinder hinge point to the upper outer edge of the cylinder = the length L2 of the cylinder in the fully open state - the length L1 from the center of the cylinder hinge point to the center of the lower lifting head. According to the maximum swing angle of the arc door from the fully closed to the fully opened process with the length from the center of the cylinder hinge point to the upper outer edge of the cylinder as the radius, determine the maximum height and swing range of the outer edge of the cylinder from the center of the cylinder hinge point. The length L1 from the center of the cylinder hinge point to the center of the lower lifting head = R3, and the length from the center of the cylinder hinge point to the upper outer edge of the cylinder = L2-R 3. With O4 as the center and R4=L2-R3 as the radius, draw a concentric circle O4. The extended straight line P1O4 intersects the concentric circle O4 with the radius R4 at point P2. Point P2 is the position of the upper outer edge of the hydraulic cylinder when the arc door is fully closed. The extended straight line O2O4 intersects the concentric circle O4 with the radius R4 at point P3. Point P3 is the position of the upper outer edge of the hydraulic cylinder when the arc door is fully open. The position corresponding to the upper outer edge of the cylinder when the arc door is fully open and fully closed is the swing range of the cylinder. According to the positions of points P2 and P3, determine the maximum swing angle α of the cylinder during operation and the maximum height H1 of the outer edge of the cylinder from the center of the cylinder hinge point; S700, according to the elevation of the hydraulic pump station installation platform being the same as the elevation of the bottom plate of the cylinder support frame or the bottom plate of the cylinder support hinge seat, determine that the elevation of the hydraulic pump station installation platform = the elevation of the center of the upper hinge point of the cylinder O4 - the height from the center of the cylinder support hinge seat to the outer edge of its bottom plate H2 - the height of the cylinder support frame H3 or the elevation of the hydraulic pump station installation platform = the elevation of the center of the upper hinge point of the cylinder O4 - the height from the center of the cylinder support hinge seat to the outer edge of its bottom plate H2.

2. The method for accurately determining the technical parameters and layout dimensions of a swing hydraulic press according to claim 1 is characterized in that: Step S700 also includes the following steps: S800, according to the height of the center of the hinge point O4 on the oil cylinder + (the length L2 of the hydraulic press in the fully open state-working stroke L) + the upper lift h of the maintenance bridge hanging rail, that is, the height H4 from the top of the maintenance bridge hanging rail to the elevation of the hydraulic pump station installation platform, the total vertical height H of the hydraulic pump room 总 =H4+the height of the maintenance bridge crane itself H5+the space height above the top required for installing the maintenance bridge crane H6.

3. The method for accurately determining the technical parameters and layout dimensions of a swing hydraulic press according to claim 2, characterized in that: The following steps are also included after step S800: S900, according to the cylinder diameter and the maximum swing angle α, determine the width B1 from the upstream outer edge of the cylinder to the intersection O4 and the width B2 from the downstream outer edge of the cylinder to the intersection O4; according to the width B`1 from the upstream outer edge of the cylinder frame to the intersection O4 and the width B`2 from the downstream outer edge of the cylinder frame to the intersection O4, and considering the safety space width B3 and the control cabinet width B4, determine the hydraulic pump room downstream width B≥Max(B1, B`1)+Max(B2, B`2)+2B3+B4 or the cylinder support frame installation platform downstream width C≥Max(B1, B`1)+Max(B2, B`2)+2B3.

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