Static balance method for runner of pump turbine

Abstract

The invention discloses a static balance method for a pump turbine runner. Belongs to the field of static balance after part machining, and adopts a flange, a convex ball, a supporting sleeve, a lifting shaft and a lifting piece in a rotating wheel upright placing state, the lifting piece and the lifting shaft are used for overturning the rotating wheel to an inverted placing state, static balance is completed after the lifting shaft and the lifting piece are detached, and a lightening hole is machined in the unbalanced position of the rotating wheel at a static balance station so that the rotating wheel can be balanced. The device has the advantages of being convenient to assemble, easy to operate, high in efficiency, low in labor intensity and high in precision.

Description

Technical Field

[0001] The invention relates to the field of static balancing of parts after mechanical processing, and in particular to a static balancing method for a runner of a water pump turbine. Background Art

[0002] The runner is the core component of the pump-turbine unit. To ensure the smooth operation of the unit, the runner needs to be statically balanced after manufacturing to reduce the weight of the unbalanced parts. The conventional runner static balancing method is completed when the runner is placed upright. Because the outer circle of the static balancing ball seat support or convex ball determined according to the weight of the runner is larger than the inner circle of the runner drain cone, in order to avoid the inner circle of the drain cone interfering with the ball seat support and the convex ball during the static balancing of the runner, the drain cone and the upper crown need to be divided into two parts. The joint surface between the drain cone and the upper crown is located at a certain position in the height direction of the runner. The drain cone does not participate in the static balancing of the runner. After the runner is balanced, the drain cone and the upper crown are welded. At present, the method of welding the drain cone on the runner that has been finely processed and balanced will cause deformation of the finely processed part, welding spatter will cause damage to the runner surface, and the weld defect treatment will have a certain period. At the same time, due to the uneven weld between the drain cone and the upper crown and the installation deviation of the drain cone, the coaxiality with the runner rotation axis will have an adverse effect on the balanced runner. Summary of the invention

[0003] The object of the present invention is to provide a method for static balancing of a pump turbine runner with a short cycle, high efficiency, low labor intensity and high precision. The method of the present invention is achieved by the following steps:

[0004] Step 1: After the wheel is processed, place it on the box;

[0005] Step 2: Use the first bolt to fix the flange to the runner;

[0006] Step 3: Use the first screw to fix the convex ball and the support sleeve;

[0007] Step 4: Use the second screw to fix the support sleeve to the hanging shaft;

[0008] Step 5: Hang the assembled convex ball, support sleeve, and suspension shaft on the flange, and use the second bolt to fix the support sleeve and the flange;

[0009] Step 6: Use the first through hole of the hanging shaft and the hanging hook installed on the flange to turn the wheel over to an inverted state where the lower ring end surface A faces upward, the upper crown flange surface B and the outer side surface C of the upper crown face downward;

[0010] Step 7: Lift the inverted rotating wheel to the top of the ball seat support through the first through hole of the lifting shaft and drop it down until the third outer circle of the ball seat support penetrates the second inner circle of the support sleeve and the lower end surface E of the support sleeve is 5-10mm lower than the upper end surface F of the ball seat support; the piston rod of the synchronous cylinder rises synchronously to support the outer side surface C of the upper crown of the rotating wheel and lift the rotating wheel by 5mm;

[0011] Step 8: Adjust the ball seat support position until the circumferential gap between the third outer circle of the ball seat support and the second inner circle of the support sleeve is uniform;

[0012] Step 9: Loosen the second screw and remove the hanging shaft;

[0013] Step 10: Remove the hanging climbing;

[0014] Step 11: The piston rod of the synchronous cylinder falls synchronously until the distance between the concave ball and the convex ball of the ball seat support is 2 to 5 mm;

[0015] Step 12: Inject high-pressure oil into the concave ball of the ball seat support, and the piston rod of the synchronous cylinder falls synchronously until it is separated from the outer side surface C of the upper crown of the runner, and the runner is floated by the oil film between the convex ball and the concave ball of the ball seat support;

[0016] Step 13: Measure the inclination of the end face A of the lower ring of the runner, and determine the eccentricity and orientation of the runner according to the inclination;

[0017] Step 14: The piston rod of the synchronous cylinder rises synchronously to lift the runner until the oil film between the convex ball and the concave ball supported by the ball seat disappears;

[0018] Step 15: Process weight-reducing holes at the overweight part of the runner;

[0019] Step 16: Repeat steps 12 to 15 until the wheel eccentricity is less than the allowable value and the wheel balancing is completed.

[0020] In the above-mentioned pump-turbine impeller static balancing method, in the step one, the impeller lower ring end face A faces downward, the upper crown flange face B and the upper crown outer side face C face upward and are placed upright and supported on a square box; four square boxes are evenly distributed around the circumference; after the impeller is processed, the lower ring end face A, the upper crown flange face B, and the upper crown outer side face C are parallel and perpendicular to the impeller rotation axis G, and the second concave stopper on the impeller upper crown and the first inner circle of the drain cone are coaxial with the impeller rotation axis G.

[0021] In the above-mentioned pump turbine impeller static balancing method, in the step two, eight first bolts are evenly distributed circumferentially; the second convex stop of the flange and the third inner circle of the flange are coaxial with the flange axis H, and the second concave stop of the impeller crown coaxial with the impeller rotation axis G is centered with the second convex stop of the flange.

[0022] In the above-mentioned pump turbine impeller static balancing method, in the step three, the first screw is a hexagon socket cylindrical head screw; the first screw fixes the convex ball on the support sleeve through the second through hole of the support sleeve, the countersunk hole, and the first threaded hole on the aspheric side of the convex ball; a second threaded hole is provided on the spherical side of the convex ball; the aspheric side of the convex ball and the support sleeve are matched with a centering stop, wherein the first convex stop is provided on the convex ball, and the first concave stop is provided on the support sleeve; the first threaded hole, the second threaded hole, and the first convex stop of the convex ball are coaxial with the convex ball axis I; the second through hole and the countersunk hole of the support sleeve, and the first concave stop are coaxial with the support sleeve axis J.

[0023] In the above-mentioned pump turbine impeller static balancing method, in step four, eight second screws are evenly distributed circumferentially; the second screw is a hexagon socket cylindrical head screw and the cylindrical head protrudes from the crown end surface D of the impeller; the hanging shaft and the support sleeve are matched with a centering stop; the first outer diameter of the hanging shaft is 2 mm smaller than the first inner diameter of the drain cone.

[0024] In the above-mentioned pump turbine impeller static balancing method, in step five, eight second bolts are evenly distributed circumferentially; the second outer circle of the support sleeve is coaxial with the support sleeve axis J, and the second outer circle of the support sleeve and the third inner circle of the flange are matched with a centering stop.

[0025] In the above-mentioned pump-turbine runner static balancing method, in step six, two hanging brackets are evenly distributed circumferentially installed on the flange; the hanging bracket and the flange are connected by threads.

[0026] In the above-mentioned pump-turbine impeller static balancing method, in the step seven, four synchronous cylinders are evenly distributed in the circumferential direction; before synchronously rising, the piston rods of the four synchronous cylinders are at the same height.

[0027] In the above-mentioned pump-turbine impeller static balancing method, in step eight, the third outer diameter of the ball seat support is 30 mm smaller than the second inner diameter of the support sleeve.

[0028] In the above-mentioned static balancing method for the pump-turbine impeller, in the step fifteen, at the balancing station, a small movable device is used to process weight-reducing holes at the overweight part of the impeller to balance the impeller.

[0029] Due to the adoption of the above scheme, the beneficial effects of the present invention are:

[0030] The present invention installs a flange, a convex ball, a supporting sleeve, a hanging shaft and a hanging bracket in an upright state of the wheel. The wheel is flipped to an inverted state, the hanging shaft and the hanging bracket are removed to complete static balancing, and weight-reducing holes are processed at the overweight position of the wheel at a balancing station to balance the wheel. The assembly is convenient, the operation is simple, and the balancing accuracy is high. The drain cone and the upper crown of the wheel are integrated into a structure to avoid the drain cone and the upper crown being divided into two parts. After the wheel is balanced, welding the drain cone will have an adverse effect on the wheel that has reached a balanced state. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] Figure 1 This is a schematic diagram of the support for the rotating wheel in the upright position.

[0032] Figure 2 The AA section view of the support for the wheel is placed upright.

[0033] Figure 3 This is a schematic diagram of the rotor before being turned upside down for static balance.

[0034] Figure 4 This is a schematic diagram of the P direction of the statically balanced wheel inverted position.

[0035] Figure 5 This is a schematic diagram of the Q direction of the statically balanced wheel inverted position.

[0036] Figure 6 This is a schematic diagram of the static balance of the inverted wheel.

[0037] Figure 7 This is the sectional view of the inverted static balance BB of the rotor.

[0038] Figure 8 This is a flange schematic diagram.

[0039] Fig. 9 Schematic diagram of a convex ball.

[0040] Fig.10 Schematic diagram of the support sleeve.

[0041] Explanation of the numbers in the figure: 1-wheel; 2-box; 3-first screw; 4-convex ball; 5-support sleeve; 6-second screw; 7-suspension shaft; 8-first bolt; 9-flange; 10-axis H; 11-second bolt; 12-first through hole; 13-suspension; 14-lower ring end face A; 15-upper crown flange face B; 16-upper crown outer side C; 17-ball seat support; 18-lower end face E; 19-upper end face F; 20-synchronous cylinder; 21-piston rod; 2 2-third outer circle; 23-second inner circle; 24-concave sphere; 25-axis of rotation G; 26-second concave stop; 27-first inner circle of drain cone; 28-second through hole; 29-counterbore; 30-first threaded hole; 31-second threaded hole; 32-first convex stop; 33-first concave stop; 34-second convex stop; 35-third inner circle; 36-upper crown end face D; 37-second outer circle; 38-first outer circle; 39-axis I; 40-axis J. DETAILED DESCRIPTION

[0042] In order to make the purpose, technical scheme and beneficial effects of the present invention clearer, further explanation will be given below in conjunction with the accompanying drawings and specific embodiments, but each embodiment does not constitute a limitation of the present invention. The specific embodiments described in the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0043] The exemplary embodiments of the technical features of the present invention are described in detail below in detail so that the present invention is fully understood. However, for those skilled in the art, the present invention can still be implemented without the need for some of the following details. The following description of the embodiments is only for a better understanding of the present invention through examples of the present invention. The present invention is by no means limited to any method provided below, but covers any modification, replacement and improvement of elements, parts and methods without departing from the spirit of the present invention. In the accompanying drawings and the following description, known structures and prior art are not shown to avoid unnecessary fuzzy understanding of the present invention.

[0044] Specific implementation method 1: Figure 1 , Figure 2 , Figure 3 , Figure 4 , Figure 6 , Figure 7 , Fig.10 As shown, this embodiment provides a method for static balancing of a pump turbine runner, which is implemented by the following steps:

[0045] Step 1: After processing, the wheel 1 is placed on the box 2;

[0046] Step 2: Use the first bolt 8 to fix the flange 9 to the runner 1;

[0047] Step 3: Use the first screw 3 to fix the convex ball 4 and the support sleeve 5;

[0048] Step 4: Use the second screw 6 to fix the support sleeve 5 and the hanging shaft 7;

[0049] Step 5: Hang the assembled convex ball 4, support sleeve 5, and suspension shaft 7 on the flange 9, and use the second bolt 11 to fix the support sleeve 5 and the flange 9;

[0050] Step 6: Using the first through hole 12 of the hanging shaft 7 and the hanging hook 13 installed on the flange 9, turn the rotating wheel 1 over to an inverted state where the lower ring end surface A14 faces upward, the upper crown flange surface B15 and the upper crown outer surface C16 face downward;

[0051] Step 7: The inverted rotating wheel 1 is hoisted above the ball seat support 17 through the first through hole 12 of the hanging shaft 7 and dropped until the third outer circle 22 of the ball seat support 17 penetrates the second inner circle 23 of the support sleeve 5 and the lower end surface E18 of the support sleeve 5 is 5-10mm lower than the upper end surface F19 of the ball seat support 17; the piston rod 21 of the synchronous cylinder 20 rises synchronously to support the outer side surface C16 of the upper crown of the rotating wheel 1 and lifts the rotating wheel 1 by 5mm;

[0052] Step 8: Adjust the position of the ball seat support 17 until the circumferential gap between the third outer circle 22 of the ball seat support 17 and the second inner circle 23 of the support sleeve 5 is uniform;

[0053] Step 9: Loosen the second screw 6 and remove the hanging shaft 7;

[0054] Step 10: Remove the hanging climbing 13;

[0055] Step 11: The piston rod 21 of the synchronous cylinder 20 falls synchronously to the ball seat support 17, and the distance between the concave ball 24 and the convex ball 4 is 2 to 5 mm;

[0056] Step 12: Inject high-pressure oil into the concave ball 24 of the ball seat support 17, and the piston rod 21 of the synchronous cylinder 20 falls synchronously until it is separated from the outer side surface C16 of the upper crown of the runner 1, and the runner 1 is floated by the oil film between the convex ball 4 and the concave ball 24 of the ball seat support 17;

[0057] Step 13: Measure the inclination of the lower ring end surface A14 of the runner 1, and determine the eccentricity and orientation of the runner 1 according to the inclination;

[0058] Step 14: The piston rod 21 of the synchronous cylinder 20 rises synchronously to lift the rotating wheel 1 until the oil film between the convex ball 4 and the concave ball 24 of the ball seat support 17 disappears;

[0059] Step 15: Processing weight-reducing holes at the overweight part of the runner 1;

[0060] Step 16: Repeat steps 12 to 15 until the eccentricity of the wheel 1 is less than the allowable value, and the balancing of the wheel 1 is completed.

[0061] In the present embodiment, the flange, convex ball, support sleeve, hanging shaft and hanging bracket are installed in the upright state of the wheel. The wheel is flipped to the inverted state, the hanging shaft and hanging bracket are removed to complete the static balance, and weight-reducing holes are processed at the overweight parts of the wheel at the balancing station to balance the wheel. The assembly is convenient, the operation is simple, and the balancing accuracy is high. The drain cone and the upper crown of the wheel are integrated into a structure to avoid the drain cone and the upper crown being divided into two parts. Welding the drain cone after the wheel is balanced will have an adverse effect on the wheel that has reached a balanced state.

[0062] Specific implementation method 2: Figure 1 , Figure 2 As shown, this embodiment is a further limitation on step one described in specific embodiment one. In this embodiment, in step one, the lower ring end face A14 of the runner 1 faces downward, and the upper crown flange face B15 and the upper crown outer side face C16 face upward and are upright and supported on the square box 2; four square boxes 2 are evenly distributed in the circumference; after processing, the lower ring end face A14, the upper crown flange face B15, and the upper crown outer side face C16 of the runner 1 are parallel and perpendicular to the rotation axis G25 of the runner 1, and the second concave stop 26 of the upper crown of the runner 1 and the first inner circle 27 of the drain cone are coaxial with the rotation axis G25 of the runner 1.

[0063] In this embodiment, after the processing, the wheel is placed on four square boxes evenly distributed around the circumference to realize the installation of the flange and the wheel. The assembled convex ball, support sleeve, hanging shaft and flange are convenient to install, which improves the assembly efficiency and ensures the assembly quality. The lower ring end face A, the upper crown flange face B, and the upper crown outer side face C are parallel and perpendicular to the rotation axis G of the wheel. During static balancing, the lower ring end face A is tilted due to the unbalanced weight of the wheel, and the rotation axis G of the wheel perpendicular to the lower ring end face A is tilted accordingly. By measuring the horizontal deviation of the lower ring end face A, it can be determined whether the rotation axis G of the wheel is plumb, thereby determining whether the wheel has reached a balanced state, avoiding the inability to accurately measure the inclination of the rotation axis G of the wheel, and being unable to determine whether the wheel is balanced, thereby achieving intuitive, accurate and convenient judgment of the wheel balance.

[0064] Specific implementation method three: Figure 1 , Figure 3 , Figure 4 , Figure 8 As shown, this embodiment is a further limitation on step two described in specific embodiment one. In this embodiment, eight first bolts 8 are evenly distributed circumferentially in step two; the second convex stop 34 of flange 9 and the third inner circle 35 of flange 9 are coaxial with the axis H10 of flange 9, and the second concave stop 26 on the crown of wheel 1 coaxial with the rotation axis G25 of wheel 1 and the second convex stop 34 of flange 9 are centered.

[0065] In this embodiment, the second convex stop of the flange and the third inner circle of the flange are coaxial with the flange axis H. The second concave stop on the upper crown of the runner, which is coaxial with the rotation axis G of the runner, and the second convex stop of the flange are matched by centering. After the flange and the runner are fixed, the flange axis H and the rotation axis G of the runner are coaxial.

[0066] Specific implementation method four: Figure 1 , Figure 3 , Fig. 9 , Fig.10 As shown, this embodiment further limits step three described in specific embodiment one. In this embodiment, the first screw 3 in step three is a hexagon socket head screw; the first screw 3 fixes the convex ball 4 on the support sleeve 5 through the second through hole 28, the countersunk hole 29 and the first threaded hole 30 on the non-spherical side of the convex ball 4; a second threaded hole 31 is provided on the spherical side of the convex ball 4; the non-spherical side of the convex ball 4 and the support sleeve 5 adopt a centering stopper cooperation, wherein the first convex stopper 32 is provided on the convex ball 4, and the first concave stopper 33 is provided on the support sleeve 5; the first threaded hole 30, the second threaded hole 31 and the first convex stopper 32 of the convex ball 4 are coaxial with the axis I39 of the convex ball 4; the second through hole 28 and the countersunk hole 29 and the first concave stopper 33 of the support sleeve 5 are coaxial with the axis J40 of the support sleeve 5.

[0067] In this embodiment, a second through hole and a countersunk hole are provided on the support sleeve, and the support sleeve and the convex ball are connected and fixed by a hexagon socket cylindrical head screw, which can reduce the space required for installation and achieve a compact structure; a second threaded hole is provided on the spherical side of the convex ball, so that the convex ball and the support sleeve can be easily hoisted during installation and disassembly; the first convex stopper, the first threaded hole, and the second threaded hole of the convex ball are coaxial with the convex ball axis I, and the first concave stopper, the second through hole, and the countersunk hole of the support sleeve are coaxial with the support sleeve axis J. The convex ball and the support sleeve are matched with a centering stopper, which can achieve the coaxiality of the convex ball and the support sleeve after installation.

[0068] Specific implementation method five: Figure 1 , Figure 3 , Figure 5 As shown, this embodiment is a further limitation on step four described in specific embodiment one. In this embodiment, eight second screws 6 are evenly distributed circumferentially in step four; the second screw 6 is a hexagon socket cylindrical head screw and the cylindrical head protrudes from the crown end surface D36 of the runner 1; the hanging shaft 7 and the supporting sleeve 5 are matched with a centering stop; the diameter of the first outer circle 38 of the hanging shaft 7 is 2 mm smaller than the diameter of the first inner circle 27 of the drain cone.

[0069] In the present embodiment, the second screw is a hexagon socket cylindrical head screw and the cylindrical head protrudes from the crown end surface D of the rotating wheel. It is not only compact in structure, but also convenient for loosening and tightening the second screw when disassembling and installing the hanging shaft. The hanging shaft and the supporting sleeve are matched with a centering stop to avoid the second screw from bearing shear stress during the subsequent turning of the rotating wheel, thereby improving safety and reducing the diameter of the second screw. It has a compact structure, light weight and low cost.

[0070] Specific implementation method six: Figure 3 , Figure 4 , Figure 8 , Fig.10 As shown, this embodiment further limits step five described in specific embodiment one. In this embodiment, eight second bolts 11 are evenly distributed circumferentially in step five; the second outer circle 37 of the support sleeve 5 is coaxial with the axis J40 of the support sleeve 5, and the second outer circle 37 of the support sleeve 5 and the third inner circle 35 of the flange 9 are matched with a centering stop.

[0071] In this embodiment, the second outer circle of the support sleeve coaxial with the support sleeve axis J and the third inner circle of the flange coaxial with the rotating axis G of the wheel are matched with a centering stop. After the support sleeve and the flange are fixed, the convex ball, support sleeve, flange and wheel are coaxially installed to ensure the accuracy of the static balancing result and avoid the influence of different axes on the static balancing result of the wheel.

[0072] Specific implementation method seven: Figure 3 As shown, this embodiment further limits step six described in the specific embodiment one. In this embodiment, in step six, two hanging hooks 13 installed on the flange 9 are evenly distributed in the circumference; the hanging hook 13 and the flange 9 are connected by threads.

[0073] In this embodiment, the lifting hook and the flange are connected by threads. Before achieving the static balance of the runner, the lifting hook can be removed to avoid the different weights of the two lifting hooks affecting the static balance result of the runner.

[0074] Specific implementation method eight: Figure 6 , Figure 7 As shown, this embodiment further limits step seven described in the specific embodiment one. In this embodiment, four synchronous cylinders 20 are evenly distributed in the circumferential direction in step seven; before synchronous rising, the piston rods 21 of the four synchronous cylinders 20 are at the same height.

[0075] In this embodiment, before the synchronous rise, the piston rods of the four synchronous cylinders are at the same height. After the piston rods rise synchronously to lift the runner, it is ensured that the outer side surface C of the upper crown of the runner, the flange surface B of the upper crown, and the end surface A of the lower ring are horizontal, and the convex ball, support sleeve, flange, and the axis of the runner are vertical, avoiding inaccurate static balance results caused by inclination of the above-mentioned axis.

[0076] Specific implementation method nine: Figure 3 , Figure 6 , Fig.10 As shown, this embodiment further limits step eight described in specific embodiment one. In this embodiment, in step eight, the diameter of the third outer circle 22 of the ball seat support 17 is 30 mm smaller than the diameter of the second inner circle 23 of the support sleeve 5.

[0077] In this embodiment, the third outer diameter of the ball seat support is 30 mm smaller than the second inner diameter of the support sleeve, which can avoid the imbalance of the wheel itself. After the wheel is floated by the high-pressure oil, the axis of the wheel tilts, and the flange and support sleeve coaxially installed with the wheel tilt accordingly, causing the second inner circle of the support sleeve to contact the second outer circle of the ball seat support, thereby ensuring the accuracy of the imbalance of the wheel and the determination of its orientation.

[0078] Specific implementation method ten: This implementation method further limits step fifteen described in specific implementation method one. In this implementation method, in step fifteen, at a balancing station, a small movable device is used to process weight-reducing holes at the overweight part of the wheel 1 to balance the wheel 1.

[0079] In this embodiment, a small movable device is used to process weight-reducing holes at the unbalanced part of the rotating wheel at the balancing station, so as to avoid lifting the rotating wheel away from the balancing station to remove the unbalanced weight and returning to the balancing station for secondary adjustment, thereby saving time.

[0080] The above are only preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present invention should be included in the protection scope of the present invention.

Claims

1. A method for static balancing a pump turbine runner, characterized in that: The method is implemented by the following steps: Step 1: After processing, the rotating wheel (1) is placed on the box (2); Step 2: Use the first bolt (8) to fix the flange (9) and the rotating wheel (1); Step 3: Use the first screw (3) to fix the convex ball (4) and the support sleeve (5); Step 4: Use the second screw (6) to fix the support sleeve (5) and the suspension shaft (7); Step 5: Hang the assembled convex ball (4), support sleeve (5) and suspension shaft (7) on the flange (9), and use the second bolt (11) to fix the support sleeve (5) and the flange (9); Step 6: Using the first through hole (12) of the hanging shaft (7) and the hanging hook (13) installed on the flange (9), turn the rotating wheel (1) over to an inverted state with the lower ring end face A (14) facing upwards, the upper crown flange face B (15) and the upper crown outer side face C (16) facing downwards; Step 7: The inverted rotating wheel (1) is lifted above the ball seat support (17) through the first through hole (12) of the lifting shaft (7) and dropped until the third outer circle (22) of the ball seat support (17) penetrates the second inner circle (23) of the support sleeve (5) and the lower end surface E (18) of the support sleeve (5) is 5 to 10 mm lower than the upper end surface F (19) of the ball seat support (17); the piston rod (21) of the synchronous cylinder (20) rises synchronously to support the outer side surface C (16) of the upper crown of the rotating wheel (1) and lift the rotating wheel (1) by 5 mm; Step 8: Adjust the position of the ball seat support (17) until the circumferential gap between the third outer circle (22) of the ball seat support (17) and the second inner circle (23) of the support sleeve (5) is uniform; Step 9: Loosen the second screw (6) and remove the hanging shaft (7); Step 10: Remove the hanging rope (13); Step 11: The piston rod (21) of the synchronous cylinder (20) falls synchronously until the distance between the concave ball (24) and the convex ball (4) of the ball seat support (17) is 2 to 5 mm; Step 12: High-pressure oil is injected into the concave ball (24) of the ball seat support (17), and the piston rod (21) of the synchronous cylinder (20) falls synchronously until it is separated from the outer side surface C (16) of the upper crown of the rotating wheel (1), and the rotating wheel (1) is floated by the oil film between the convex ball (4) and the concave ball (24) of the ball seat support (17); Step 13: Measure the inclination of the lower ring end surface A (14) of the rotating wheel (1), and determine the weight and orientation of the rotating wheel (1) according to the inclination; Step 14: The piston rod (21) of the synchronous cylinder (20) rises synchronously to lift the rotating wheel (1) until the oil film between the convex ball (4) and the concave ball (24) of the ball seat support (17) disappears; Step 15: Processing a weight-reducing hole at the heavy part of the wheel (1); Step 16: Repeat steps 12 to 15 until the eccentricity of the wheel (1) is less than the allowable value, and the wheel (1) is balanced.

2. A pump turbine runner balancing method according to claim 1, characterized in that: In the step 1, the lower ring end face A (14) of the runner (1) faces downward, and the upper crown flange face B (15) and the upper crown outer side face C (16) face upward and are supported upright on the square box (2); four square boxes (2) are evenly distributed in the circumferential direction; after the runner (1) is processed, the lower ring end face A (14), the upper crown flange face B (15), and the upper crown outer side face C (16) are parallel and perpendicular to the rotation axis G (25) of the runner (1), and the second concave stop (26) of the upper crown of the runner (1) and the first inner circle (27) of the drain cone are coaxial with the rotation axis G (25) of the runner (1).

3. A method for static balancing a pump turbine runner according to claim 1, characterized in that: In the step 2, eight first bolts (8) are evenly distributed in the circumferential direction; the second convex stop (34) of the flange (9), the third inner circle (35) of the flange (9) are coaxial with the axis H (10) of the flange (9), and the second concave stop (26) on the crown of the runner (1) coaxial with the rotation axis G (25) of the runner (1) and the second convex stop (34) of the flange (9) are centered.

4. A method for static balancing a pump turbine runner according to claim 1, characterized in that: In the step three, the first screw (3) is a hexagon socket head screw; the first screw (3) fixes the convex ball (4) on the support sleeve (5) through the second through hole (28) of the support sleeve (5), the countersunk hole (29), and the first threaded hole (30) on the non-spherical side of the convex ball (4); the spherical side of the convex ball (4) is provided with a second threaded hole (31); the non-spherical side of the convex ball (4) and the support sleeve (5) are matched with a centering stop, wherein the first convex stop (32) is provided on the convex ball (4), and the first concave stop (33) is provided on the support sleeve (5); the first threaded hole (30), the second threaded hole (31), and the first convex stop (32) of the convex ball (4) are coaxial with the axis I (39) of the convex ball (4); the second through hole (28) and the countersunk hole (29) of the support sleeve (5), and the first concave stop (33) are coaxial with the axis J (40) of the support sleeve (5).

5. A method for static balancing a pump turbine runner according to claim 1, characterized in that: In the step 4, eight second screws (6) are evenly distributed in the circumferential direction; the second screws (6) are hexagon socket head screws and the cylindrical head protrudes from the crown end surface D (36) of the rotating wheel (1); the hanging shaft (7) and the supporting sleeve (5) are matched with a centering stop; the diameter of the first outer circle (38) of the hanging shaft (7) is 2 mm smaller than the diameter of the first inner circle (27) of the drain cone.

6. A method for static balancing a pump turbine runner according to claim 1, characterized in that: In the step five, eight second bolts (11) are evenly distributed around the circumference; the second outer circle (37) of the support sleeve (5) is coaxial with the axis J (40) of the support sleeve (5); the second outer circle (37) of the support sleeve (5) and the third inner circle (35) of the flange (9) are matched with a centering stop.

7. A method for static balancing a pump turbine runner according to claim 1, characterized in that: In the step six, two hanging hooks (13) are evenly distributed around the circumference and the hanging hooks (13) and the flange (9) are connected by threads.

8. A method for static balancing a pump turbine runner according to claim 1, characterized in that: In the step seven, four synchronous cylinders (20) are evenly distributed in the circumferential direction; before synchronously ascending, the piston rods (21) of the four synchronous cylinders (20) are at the same height.

9. A method for static balancing a pump turbine runner according to claim 1, characterized in that: In the step eight, the diameter of the third outer circle (22) of the ball seat support (17) is 30 mm smaller than the diameter of the second inner circle (23) of the support sleeve (5).

10. A method for static balancing a pump turbine runner according to claim 1, characterized in that: In the fifteenth step, at the balancing station, a small movable device is used to machine weight-reducing holes at the overweight part of the rotating wheel (1), so that the rotating wheel (1) can be balanced.

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