Movable guide vane journal and shaft sleeve action measurement test device and use method thereof

Abstract

The invention discloses a movable guide vane journal and shaft sleeve action measurement test device and a use method thereof, the movable guide vane journal and shaft sleeve action measurement test device is mounted on a plurality of crank arms of a movable guide vane assembly, the plurality of crank arms are annularly distributed, two groups of spaced crank arms are matched for testing, a supporting piece is rotatably connected with an oil cylinder, and a piston rod of the oil cylinder is connected with a movable turntable; a push-pull force sensor is arranged between the piston rod and the movable rotary table, an angle sensor is fixedly connected to the top of the movable rotary table, a movable base is rotationally connected to the bottom of the movable rotary table, a connecting rod shaft hole is formed in the crank arm, a positioning shaft connected with the connecting rod shaft hole in an inserted mode is arranged at the bottom of the movable base, and the positioning shaft is hollow. The oil cylinder and the push-pull force sensor are used for replacing a test mode that a hand-drive block is matched with an electronic scale in the related technology, so that the labor intensity of a tester is effectively reduced, and compared with a friction force value measured by adopting the hand-drive block to be matched with the electronic scale, the friction force value measured by adopting the hand-drive block to be matched with the electronic scale is greatly improved. And the accuracy is obviously improved.

Description

Technical Field

[0001] The present invention relates to the technical field of friction force measuring devices, and in particular to a movable guide vane journal and sleeve motion measurement test device and a use method thereof. Background Art

[0002] In hydraulic machinery such as turbines and pump turbines, movable guide vanes are key components for regulating the direction and flow of water flow. Their flexibility, sealing performance and friction characteristics directly affect the operating efficiency and stability of the unit. In order to ensure that the movable guide vanes maintain a good condition during long-term operation, regular action tests are required to detect their opening and closing torque, friction torque and movement jamming. At the same time, in the water guide mechanism of the hydro-generator unit, the upper and middle shaft sleeves of the guide vane sleeve are nylon shaft sleeves. The expansion generated during operation causes the friction between the shaft neck and the shaft sleeve of the movable guide vane to increase. When the friction exceeds a certain value, the movable guide vane will not be able to operate normally. Therefore, during the maintenance of the water guide mechanism, a movable guide vane action test is required to measure the friction between the shaft neck and the shaft sleeve of the movable guide vane. At present, the movable guide vane action test mainly relies on a manual hoist in combination with an electronic scale. In the test, the measuring end of the electronic scale is connected to the crank arm, and the electronic scale is pulled manually using a manual hoist. The electronic scale drives the crank arm, the shaft neck and the movable guide vane to rotate, and the friction value is converted according to the measurement value of the electronic scale. However, when the manual hoist is used in conjunction with the electronic scale for testing, only the crank arm can be pulled but not pushed. Therefore, the measuring position needs to be changed during measurement in order to measure the friction force during forward and reverse rotation of the shaft neck, which is inconvenient to operate. At the same time, the manual hoist needs to be pulled manually during measurement, which increases the labor intensity of the test personnel. Moreover, the angle between the pulling direction and the crank arm cannot be measured during measurement, resulting in a low accuracy of the friction value obtained after conversion. At the same time, the existing measuring tools need to be manually pulled or are only installed and contacted with the crank arm through a simple connection structure, which may lead to inaccurate measurement results. Summary of the Invention

[0003] The patent of this invention aims to solve the deficiencies in the existing technology and provide a movable guide vane shaft neck and sleeve movement measurement test device and its use method, which is used to solve the problems of the related technology of using a manual hoist in combination with an electronic scale for testing, resulting in inconvenient operation, high labor intensity for testers, and low measurement accuracy of friction value.

[0004] In order to solve the above technical problems, the technical solution adopted by the present invention is: a movable guide vane shaft neck and shaft sleeve movement measurement test device and its use method, which are installed on several crank arms of the movable guide vane assembly, and the several crank arms are distributed in a ring shape. The crank arms are provided with support members and movable turntables, and two groups of spaced crank arms are tested together. The support member is rotatably connected to an oil cylinder, and the piston rod of the oil cylinder is connected to the movable turntable. A push-pull force sensor is provided between the piston rod and the movable turntable, and an angle sensor is fixedly connected to the top of the movable turntable, and a movable base is rotatably connected to the bottom of the movable turntable. A connecting rod shaft hole is provided on the crank arm, and a positioning shaft that is plugged into the connecting rod shaft hole is provided at the bottom of the movable base. The positioning shaft is hollow, and a locking assembly is also provided in the positioning shaft for connecting the movable base and the crank arm.

[0005] Preferably, the locking assembly includes a telescopic column and a lower limit block, the telescopic column is arranged in the positioning shaft, the positioning shaft is provided with an axial driving member for driving the telescopic column to axially extend and retract relative to the positioning shaft, the lower limit block is arranged on the telescopic column, the positioning shaft is provided with a radial driving member for driving the lower limit block to radially extend and retract relative to the telescopic column, the lower limit block can abut against the bottom surface of the crank arm, and the outer wall of the positioning shaft is provided with an upper limit plate that can abut against the top of the crank arm.

[0006] The top of the telescopic column is provided with a stud, and the stud is screwed to the worm gear of the outer surface of the worm gear, and the first worm gear is screwed to the worm gear of the outer surface of the worm gear, and the first worm gear is screwed to the worm gear of the outer surface of the worm gear. The first worm gear is rotatably arranged on the side surface of the positioning shaft and meshes with the first worm gear. One end of the first worm gear passes through the positioning shaft and is provided with a driving rod, and the driving rod is provided with a hexagon socket bolt head. The radial driving member includes a rotating shaft rotatably arranged on the top wall of the positioning shaft, the stud is provided with a center hole, one end of the rotating shaft is inserted into the center hole and fixedly connected to the transmission rod, the outer surface of the transmission rod is rotatably connected to the gear shaft, and the bottom of the gear shaft is fixedly connected to the gear, and two lower limit blocks are respectively meshed with two lower limit blocks on both sides of the gear. The outer surface of the rotating shaft is provided with a second worm gear, and the side surface of the positioning shaft is further penetrated by a second worm gear, and the second worm gear is meshed with the second worm gear, and the second worm gear is provided with a joystick at one end passing through the positioning shaft.

[0007] Preferably, the telescopic column is provided with a radial guide groove, the two lower limit blocks are slidably arranged in the radial guide groove, the support member includes a fixed base, the fixed base is detachably fixed on the crank arm, and a fixed turntable is provided on the cylinder body of the oil cylinder, the fixed turntable is rotatably connected to the fixed base, the rotation axis of the fixed turntable coincides with the axis of the movable guide vane shaft neck, and also includes a pull-wire sensor, the pull-wire sensor is fixed on the cylinder body of the oil cylinder, the pull wire of the pull-wire sensor is connected to the piston rod of the oil cylinder, and the pull-wire sensor is used to measure the maximum or minimum stroke of the piston rod of the oil cylinder.

[0008] Preferably, it also includes a laser centering instrument, the transmitter of the laser centering instrument is arranged on the crank arm of the movable guide vane to be measured, the receiver of the laser centering instrument is arranged on the movable turntable, and the laser centering instrument is used to determine the initial angular position of the movable turntable. It also includes a photoelectric sensor, which is fixed on the side of the crank arm of the movable guide vane to be measured, and the photoelectric sensor is used to detect whether the adjacent crank arm collides with the crank arm of the movable guide vane to be measured.

[0009] In addition, the present invention also discloses a method for using the above-mentioned movable guide vane journal and sleeve motion measurement test device and its use method, which includes the following steps: 6. A method for using the movable guide vane journal and sleeve motion measurement test device and its use method according to any one of claims 1 to 5, characterized in that it comprises the following steps: Step 1: Before conducting the movable guide vane action test, first connect the positioning shaft with the connecting rod shaft hole, and then fix the base with the crank arm.

[0010] Step 2: The crank arm where the fixed base is located is separated from the crank arm of the movable guide vane to be measured by one crank arm. The rotation connection point between the cylinder body and the piston rod of the oil cylinder and the crank arm is separated by one crank arm. This can minimize the change in the angle between the oil cylinder piston rod and the crank arm during the extension and retraction of the oil cylinder piston rod, and make it closest to 90°. Therefore, the torque loss during the push-pull action is smaller, and the measurement value is more accurate. Step 3: Conduct the movable guide vane action test.

[0011] Preferably, in step 1, when it is necessary to fix the movable base and the crank arm, the positioning shaft is first inserted into the connecting rod shaft hole until the upper limit plate abuts against the top surface of the crank arm, and then the lower limit block is driven to radially extend relative to the telescopic column by the radial driving member, and then the telescopic column is driven to axially contract relative to the positioning shaft by the axial driving member, so that the lower limit block abuts against the bottom surface of the crank arm, thereby clamping the movable base and the crank arm together through the upper limit plate and the lower limit block; Preferably, when performing the movable guide vane actuation test in step 3, the crank arm of the movable guide vane under test is pushed or pulled by the oil cylinder to rotate around the axis of the shaft neck. When the oil cylinder moves, the force F output by the oil cylinder can be decomposed into two directions, namely, a force F1 along the direction of the crank arm and a force F2 perpendicular to the direction of the crank arm; Preferably, the force value measured by the push-pull force sensor is F. F is not the actual force pushing or pulling the crank arm to rotate. The angle sensor is required to measure the real-time angle α between the oil cylinder and the crank arm, and then calculate the force F2 perpendicular to the direction of the crank arm. F2 is multiplied by the lever arm L1 of the crank arm to obtain the torque M that pushes or pulls the crank arm to rotate. If the friction force of the crank arm rotation needs to be calculated, the torque M is divided by the friction part lever arm L2 to obtain the friction force value F. The calculation process and formula are as follows: The push and pull forces F are measured in real time by the push and pull force sensors. The angle α between the oil cylinder and the crank arm is measured in real time by the angle sensor. The crank arm force arm L1 and the friction force arm L2 are inherent parameters of the equipment and can be pre-recorded or input in real time. After the test starts, the force F2 perpendicular to the crank arm is calculated: F2=F×sinα; Then the torque M that pushes or pulls the crank arm to rotate is: M=F2×L1; When the crank arm rotates at a constant speed, it can be considered that the push and pull forces only overcome the friction force to do work, that is, the friction force F is: F = M ÷ L2; The friction force F is actually the kinetic friction. If you need to measure the maximum static friction, you should adjust the test method to continuously increase the push and pull force F until the crank arm rotates. Record the push and pull force F at the moment of pushing, and repeat the above calculation. Preferably, if the crank arm does not rotate at a uniform speed during the pushing or pulling process, the pushing or pulling torque M not only needs to overcome the friction force, but also drives the crank arm to accelerate or decelerate, which will cause calculation errors. Therefore, in the electronic control system, a speed feedback adjustment algorithm will be used to achieve uniform rotation of the crank arm.

[0012] Beneficial effects of the present invention: The oil cylinder and push-pull force sensor replace the test method of using a manual hoist with an electronic scale in the related technology, thereby effectively reducing the labor intensity of the test personnel. In addition, the oil cylinder can realize the pushing and pulling force on the crank arm, so that the friction force during the forward and reverse rotation of the shaft neck can be measured without adjusting the measuring position, thereby improving the operation convenience. At the same time, the push-pull force sensor is used to measure the pulling force or pushing force of the piston rod of the oil cylinder on the movable turntable, and the angle sensor is used to measure the angle between the piston rod of the oil cylinder and the crank arm. The friction force value can be calculated by combining the push-pull force value measured by the push-pull force sensor and the angle value measured by the angle sensor. Compared with the friction force value measured by the manual hoist with an electronic scale, the accuracy is significantly improved. At the same time, the present invention ensures that the measuring device is stably installed on the guide vane through the axial drive member and the radial drive member. BRIEF DESCRIPTION OF THE DRAWINGS

[0013] The present invention will be further described below with reference to the accompanying drawings and examples.

[0014] Figure 1 Schematic diagram of the structure of the movable guide vane journal and sleeve motion measurement test device in an embodiment of the present application; Figure 2 for Figure 1 A partial enlarged schematic diagram of part A; Figure 3 A cross-sectional view from a first perspective of a test device for measuring the movement of a movable guide vane journal and a sleeve in an embodiment of the present application; Figure 4 for Figure 3 A partial enlarged schematic diagram of part B; Figure 5 A cross-sectional view of the movable guide vane journal and sleeve motion measurement test device from a second perspective in an embodiment of the present application; Figure 6 for Figure 5 A partial enlarged schematic diagram of part C in the middle; Figure 7 for Figure 6 A partial enlarged schematic diagram of the C1 part; Figure 8 A cross-sectional view of the movable guide vane journal and sleeve motion measurement test device from a third perspective in an embodiment of the present application; Figure 9 for Figure 8 A partial enlarged schematic diagram of part D in the middle; Figure 10 Schematic diagram of the conversion principle of friction value.

[0015] Description of reference numerals: 10. Crank arm; 11. Connecting rod shaft hole; 12. Crank arm sleeve; 13. Bolt; 14. Crank arm end cover; 20. Oil cylinder; 21. Cylinder body; 22. Piston rod; 23. Connecting rod; 30. Moving turntable; 40. Push-pull force sensor; 50. Angle sensor; 60. Moving base; 61. Positioning shaft; 611. Axial guide groove; 612. Ridge; 613. Upper limit plate; 70. Locking assembly; 71. Telescopic column; 711. Slide; 712. Stud; 713. Radial guide groove; 714. Center hole; 72. Lower stop block; 721. Rack; 73. Screw sleeve; 731. First worm gear; 74. First worm; 741. Drive rod; 742. Hexagon socket bolt head; 75. Gear; 751. Gear shaft; 752. Transmission groove; 76. Rotating shaft; 761. Transmission rod; 762. Second worm gear; 77. Second worm; 771. Control lever. 80. Pull wire sensor; 81. Pull wire; 90. Laser centering device; 100. Photoelectric sensor; 110. Fixed base; 120. Fixed turntable. DETAILED DESCRIPTION

[0016] The present invention will be described in further detail below with reference to the accompanying drawings and specific embodiments.

[0017] This embodiment discloses a movable guide vane journal and sleeve motion measurement test device and a method for using the same.

[0018] A movable guide vane journal and sleeve motion measurement test device and a method of using the same include a movable guide vane, a crank arm 10, a support member, an oil cylinder 20, a movable turntable 30, a push-pull force sensor 40, an angle sensor 50, a movable base 60, a locking assembly 70, a pull wire sensor 80, a laser centering instrument 90, and a photoelectric sensor 100.

[0019] Reference Figure 1 and Figure 2 In the water guide mechanism of the hydro-generator set, the crank arm 10 is connected to the shaft neck of the movable guide vane through the crank arm sleeve 12. The movable guide vane is distributed in a ring shape. Correspondingly, the crank arm 10 is distributed in a ring shape. A crank arm end cover 14 is installed on the crank arm 10 by bolts 13.

[0020] The cylinder body 21 of the oil cylinder 20 is rotatably connected to a support member. More specifically, the support member includes a fixed base 110, which is detachably fixed to the crank arm 10. When installing the fixed base 110, the bolts 13 can be removed first, and then the fixed base 110 can be fixed to the crank arm end cover 14 of the crank arm 10 using the bolts 13. A fixed turntable 120 is provided on the cylinder body 21 of the oil cylinder 20. The fixed turntable 120 is rotatably connected to the fixed base 110 via a bearing. The rotation axis of the fixed turntable 120 coincides with the axis of the movable guide vane journal, allowing the oil cylinder 20 to rotate around the axis of the movable guide vane journal.

[0021] Reference Figures 2 to 6 The movable turntable 30 is rotatably mounted on the crank arm 10 of the movable guide vane under test. More specifically, the crank arm 10 is provided with a connecting rod shaft hole 11, through which the crank arm 10 is rotatably connected to the connecting rod of the water guide mechanism of the hydro-generator set. When the movable guide vane operation test is required, the connecting rod is disassembled from the crank arm 10 to expose the connecting rod shaft hole 11. The movable base 60 is provided with a positioning shaft 61 that can be plugged into the connecting rod shaft hole 11 of the crank arm 10. The locking assembly 70 is used to fixedly connect the movable base 60 to the crank arm 10. The movable turntable 30 is rotatably mounted on the movable base 60 via a bearing.

[0022] The push-pull force sensor 40 is connected to the piston rod 22 of the oil cylinder 20 and the movable turntable 30. More specifically, the push-pull force sensor 40 is fixedly connected to the movable turntable 30, and the piston rod 22 of the oil cylinder 20 is fixedly connected to the measuring end of the push-pull force sensor 40 via a connecting rod 23. The push-pull force sensor 40 is used to measure the pulling or pushing force exerted by the piston rod 22 of the oil cylinder 20 on the movable turntable 30.

[0023] The pull-wire sensor 80 is fixed on the cylinder body 21 of the oil cylinder 20. The pull-wire 81 of the pull-wire sensor 80 is connected to the piston rod 22 of the oil cylinder 20. The pull-wire sensor 80 is used to measure the maximum or minimum stroke of the piston rod 22 of the oil cylinder 20, so that during the movable guide vane action test, when the piston rod 22 of the oil cylinder 20 reaches the maximum or minimum stroke, the action of the oil cylinder 20 can be stopped in time to prevent damage to the oil cylinder 20.

[0024] Reference Figure 2 and Figure 4 The angle sensor 50 is fixed on the dynamic turntable 30, and the measuring end of the angle sensor 50 is fixedly connected to the dynamic base 60. The rotation axis of the measuring end of the angle sensor 50 coincides with the rotation axis of the dynamic turntable 30. The angle sensor 50 is used to measure the angle between the piston rod 22 of the oil cylinder 20 and the crank arm 10, that is, the angle rotated by the dynamic turntable 30 relative to the initial position.

[0025] The laser plummeting device 90's transmitter is fixed to the crank arm sleeve 12 of the movable guide vane crank arm 10 being measured, and its receiver is fixed to the movable turntable 30. It should be noted that the receiver of the laser plummeting device 90 is not shown in the drawings. The laser plummeting device 90 is used to determine the initial angular position of the movable turntable 30. The laser beam emitted by the laser plummeting device 90's transmitter is parallel to the line connecting the center of the crank arm sleeve 12 and the center of the connecting rod shaft hole 11. When the laser plummeting device 90's receiver receives the laser beam emitted by the transmitter, the movable turntable 30 is in the initial angular position.

[0026] The emitter and receiver of the photoelectric sensor 100 are fixed to the side of the crank arm 10 of the movable guide vane under test. The photoelectric sensor 100 is used to detect whether an adjacent crank arm 10 collides with the crank arm 10 of the movable guide vane under test. During the movable guide vane operation test, if factors such as human error cause the adjacent crank arm 10 to collide with the crank arm 10 of the movable guide vane under test, the light beam emitted by the emitter of the photoelectric sensor 100 is blocked and the receiver cannot receive the light beam. At this time, an alarm can be issued to remind the test personnel that the crank arm 10 has collided with the crank arm 10 of the movable guide vane under test, so that the test personnel can take timely measures to avoid affecting the test results.

[0027] The implementation principle of the movable guide vane shaft neck and sleeve movement measurement test device and the use method thereof in this embodiment is as follows: when conducting a movable guide vane movement test, the crank arm 10 where the fixed base 110 is located is separated from the crank arm 10 of the movable guide vane to be measured by one crank arm 10, and the cylinder body 21 and the piston rod 22 of the oil cylinder 20 and the rotation connection point of the crank arm 10 are separated by one crank arm 10. This can ensure that during the telescopic movement of the piston rod 22 of the oil cylinder 20, the angle between the piston rod 22 of the oil cylinder 20 and the crank arm 10 changes as little as possible and is closest to 90°. Therefore, the torque loss during the push-pull movement is smaller and the measurement value is more accurate.

[0028] When conducting the movable guide vane motion test, the crank arm 10 of the movable guide vane under test is pushed or pulled by the oil cylinder 20 to rotate around the axis of the journal. When the oil cylinder 20 moves, the force F output by the oil cylinder 20 can be decomposed into two directions, namely the force F1 along the direction of the crank arm 10 and the force F2 perpendicular to the direction of the crank arm 10. The force decomposition diagram is as follows: Figure 10 shown.

[0029] The force F measured by the push-pull force sensor 40 is not the actual force pushing or pulling the crank arm 10. Instead, the angle sensor 50 measures the real-time angle α between the oil cylinder 20 and the crank arm 10. This calculates the force F2 perpendicular to the crank arm 10. Multiplying F2 by the lever arm L1 of the crank arm 10 yields the torque M that pushes or pulls the crank arm 10. To calculate the frictional force causing the crank arm 10 to rotate, divide the torque M by the friction lever arm L2 to obtain the friction force F. The calculation process and formula are as follows: The push and pull forces F are measured in real time by the push and pull force sensors 40. The angle α between the oil cylinder 20 and the crank arm 10 is measured in real time by the angle sensor 50. The crank arm 10 force arm L1 and the friction force arm L2 are inherent parameters of the equipment and can be pre-recorded or input in real time. After the test begins, the force F2 perpendicular to the crank arm 10 is calculated as: F2=F×sinα; Then the torque M that pushes or pulls the crank arm 10 to rotate is: M=F2×L1; When the crank arm 10 rotates at a constant speed, it can be considered that the pushing and pulling forces only overcome the friction force to do work, that is, the friction force F is: F = M ÷ L2; The friction force F obtained here is actually the dynamic friction force. If the maximum static friction force needs to be measured, the test method should be adjusted to continuously increase the push and pull force F until the crank arm 10 rotates, record the push and pull force F at the moment of pushing, and repeat the above calculation. I will not go into details here. If the crank arm 10 does not rotate at a constant speed during pushing or pulling, the pushing or pulling torque M not only needs to overcome the friction force, but also drives the crank arm 10 to accelerate or decelerate, which will cause calculation errors. Therefore, in the electronic control system, a speed feedback adjustment algorithm will be used to achieve constant rotation of the crank arm 10.

[0030] Example 2 This embodiment discloses a movable guide vane journal and sleeve motion measurement test device and a method for using the same.

[0031] Reference Figures 4 to 9The movable guide vane actuation test device of this embodiment differs from that of Example 1 in that the locking assembly 70 includes a telescopic column 71 and a lower stopper 72. The telescopic column 71 is disposed on the positioning shaft 61. More specifically, the positioning shaft 61 is provided with an axial guide groove 611, into which the telescopic column 71 is slidably inserted. A ridge 612 is provided on the inner wall of the axial guide groove 611 of the positioning shaft 61. The telescopic column 71 is provided with a slide groove 711 that axially slides and engages with the ridge 612. The positioning shaft 61 is provided with an axial drive member for driving the telescopic column 71 to extend and retract axially relative to the positioning shaft 61.

[0032] The lower limit block 72 is provided on the telescopic column 71. More specifically, the telescopic column 71 is provided with a radial guide groove 713. Two lower limit blocks 72 are provided, and the two lower limit blocks 72 slide in the radial guide groove 713. The positioning shaft 61 is provided with a radial drive member for driving the lower limit block 72 to radially extend and retract relative to the telescopic column 71. The lower limit block 72 can abut the bottom surface of the crank arm 10. The positioning shaft 61 is provided with an upper limit plate 613 that can abut the top surface of the crank arm 10.

[0033] Before conducting the movable guide vane action test, when it is necessary to fix the movable base 60 to the crank arm 10, first insert the positioning shaft 61 into the connecting rod shaft hole 11 until the upper limit plate 613 abuts against the top surface of the crank arm 10, and then drive the lower limit block 72 to radially extend relative to the telescopic column 71 through the radial driving member, and then drive the telescopic column 71 to axially contract relative to the positioning shaft 61 through the axial driving member, so that the lower limit block 72 abuts against the bottom surface of the crank arm 10, thereby clamping the movable base 60 and the crank arm 10 together through the upper limit plate 613 and the lower limit block 72.

[0034] In an optional embodiment, the specific structure of the axial drive member and its specific connection relationship with the telescopic column 71 are as follows: the axial drive member includes a threaded sleeve 73 and a first worm 74. The threaded sleeve 73 is rotatably mounted on the positioning shaft 61 and located within the axial guide groove 611. The telescopic column 71 is provided with a stud 712, which is threadedly connected to the threaded sleeve 73. The threaded sleeve 73 is provided with a first worm gear 731. The first worm 74 is rotatably mounted on the positioning shaft 61 and meshes with the first worm gear 731. The first worm 74 is located within the axial guide groove 611. The first worm 74 is provided with a drive rod 741 that extends through the positioning shaft 61, and the drive rod 741 is provided with a hexagon socket head screw head 742.

[0035] The screw sleeve 73 is rotatably mounted on the positioning shaft 61. Specifically, Figure 6As shown, the inner wall of the positioning shaft 61 is laterally extended with several integrated mounting plates, the screw sleeve 73 passes through the mounting plate, and the outer surface of the screw sleeve 73 is sleeved with a first worm gear 731. During installation, the bottom of the first worm gear 731 can be rotatably connected to the mounting plate. When the first worm gear 731 rotates, the screw sleeve 73 is driven to rotate synchronously. The internal thread of the screw sleeve 73 is threadedly connected to the stud 712, driving the stud 712 to rotate up and down.

[0036] Another solution of this embodiment includes providing a stud 712 on the telescopic column 71. To ensure that the telescopic column 71 only performs up and down telescopic movements, a hollow bearing can be provided on the top of the telescopic column 71. The stud 712 is rotatably connected to the hollow bearing. When the stud 712 rotates and telescopes, the telescopic column 71 is driven to only perform up and down telescopic movements.

[0037] When it is necessary to drive the telescopic column 71 to axially extend and retract relative to the positioning shaft 61 through the axial driving member, use an Allen wrench to insert into the hexagonal bolt head 742, rotate the first worm 74 through the driving rod 741, and then drive the first worm gear 731 and the screw sleeve 73 to rotate through the first worm 74. Under the interaction between the screw sleeve 73 and the stud 712, the stud 712 and the telescopic column 71 are driven to axially extend and retract relative to the positioning shaft 61.

[0038] In an alternative embodiment, the specific structure of the radial drive member and its specific connection relationship with the lower stop block 72 are as follows: the radial drive member includes a gear 75, a rotating shaft 76, and a second worm 77. The two lower stop blocks 72 are each provided with a rack 721. The gear 75 is rotatably mounted on the telescopic column 71 via a gear shaft 751 and meshes with the racks 721 on the two lower stop blocks 72. The gear shaft 751 is provided with a transmission groove 752 having a square cross-section. The stud 712 is provided with a center hole 714, and the gear shaft 751 is rotatably mounted within the center hole 714. The rotating shaft 76 is rotatably mounted on the positioning shaft 61 and located within the axial guide groove 611. The rotating shaft 76 is inserted into the center hole 714. The rotating shaft 76 is provided with a transmission rod 761 that is axially slidably engaged with the transmission groove 752. The rotating shaft 76 is provided with a second worm gear 762. The second worm gear 77 is rotatably mounted on the positioning shaft 61 and meshes with the second worm gear 762. The second worm 77 is located in the axial guide groove 611 . The second worm 77 is provided with a manipulation rod 771 passing through the positioning shaft 61 .

[0039] When it is necessary to drive the lower limit block 72 to radially extend or retract relative to the telescopic column 71 through the radial driving member, the second worm 77 is rotated by the operating rod 771, and the second worm 77 drives the second worm gear 762, the rotating shaft 76 and the transmission rod 761 to rotate, and the transmission rod 761 drives the gear shaft 751 and the gear 75 to rotate. Then, under the interaction between the gear 75 and the rack 721, the two lower limit blocks 72 are driven to move back or in opposite directions, thereby realizing the radial telescopic movement of the lower limit block 72 relative to the telescopic column 71.

[0040] The above embodiments are merely preferred technical solutions of the present invention and should not be construed as limiting the present invention. The scope of protection of the present invention shall be the technical solutions set forth in the claims, including equivalent alternatives to the technical features of the technical solutions set forth in the claims. In other words, equivalent alternatives and improvements within this scope are also within the scope of protection of the present invention.

Claims

1. A device for measuring the movement of a guide vane journal and sleeve, mounted on a plurality of crank arms of a guide vane assembly, wherein the crank arms are distributed in a ring shape, and characterized in that: The crank arm is provided with a support and a movable turntable, and two groups of spaced crank arms are tested together. The support is rotatably connected to an oil cylinder, and the piston rod of the oil cylinder is connected to the movable turntable. A push-pull force sensor is provided between the piston rod and the movable turntable. An angle sensor is fixedly connected to the top of the movable turntable, and a movable base is rotatably connected to the bottom of the movable turntable. A connecting rod shaft hole is provided on the crank arm, and a positioning shaft that is plugged into the connecting rod shaft hole is provided at the bottom of the movable base. The positioning shaft is hollow, and a locking assembly is also provided in the positioning shaft for connecting the movable base and the crank arm.

2. The movable guide vane journal and sleeve motion measurement test device according to claim 1, characterized in that: The locking assembly includes a telescopic column and a lower limit block, the telescopic column is arranged in the positioning shaft, the positioning shaft is provided with an axial driving member for driving the telescopic column to axially extend and retract relative to the positioning shaft, the lower limit block is arranged on the telescopic column, the positioning shaft is provided with a radial driving member for driving the lower limit block to radially extend and retract relative to the telescopic column, the lower limit block can abut against the bottom surface of the crank arm, and the outer wall of the positioning shaft is provided with an upper limit plate that can abut against the top of the crank arm.

3. The movable guide vane journal and sleeve motion measurement test device according to claim 2, characterized in that: The worm gear of the first gear is meshed with the worm gear of the second gear, and the worm gear is meshed with the worm gear of the second gear.

4. The movable guide vane journal and sleeve motion measurement test device according to claim 1, characterized in that: The telescopic column is provided with a radial guide groove, and the two lower limit blocks are slidably arranged in the radial guide groove. The support member includes a fixed base, and the fixed base is detachably fixed on the crank arm. A fixed turntable is provided on the cylinder body of the oil cylinder, and the fixed turntable is rotatably connected to the fixed base. The rotation axis of the fixed turntable coincides with the axis of the movable guide vane shaft neck.

5. The movable guide vane journal and sleeve motion measurement test device according to claim 1, characterized in that: It also includes a pull-wire sensor, which is fixed on the cylinder body of the oil cylinder, and the pull wire of the pull-wire sensor is connected to the piston rod of the oil cylinder, and the pull-wire sensor is used to measure the maximum or minimum stroke of the piston rod of the oil cylinder; it also includes a laser centering instrument, the transmitter of the laser centering instrument is arranged on the crank arm of the measured movable guide vane, and the receiver of the laser centering instrument is arranged on the movable turntable, and the laser centering instrument is used to determine the initial angular position of the movable turntable; it also includes a photoelectric sensor, which is fixed on the side of the crank arm of the measured movable guide vane, and the photoelectric sensor is used to detect whether the adjacent crank arm collides with the crank arm of the measured movable guide vane.

6. A method for using a movable guide vane journal and sleeve motion measurement test device according to any one of claims 1 to 5, characterized in that: The movable guide vane journal and sleeve motion measurement test device further comprises the following steps: Step 1: Before conducting the movable guide vane action test, first connect the positioning shaft with the connecting rod shaft hole, and then fix the base with the crank arm.

7. Step 2: Set the crank arm where the base is located and the crank arm of the movable guide vane being measured one crank arm apart. Also, set the rotational connection point between the cylinder body, piston rod, and crank arm one crank arm apart. This minimizes the change in the angle between the piston rod and the crank arm during the extension and retraction of the cylinder. This results in less torque loss during push-pull movements and more accurate measurements. Step 3: Conduct a movable guide vane action test; Step 4: Record the push and pull force values ​​at the moment of pushing in the movable guide vane action test, and repeat the above calculation.

8. The method of use according to claim 6, characterized in that: In step 1, when it is necessary to fix the movable base and the crank arm, first insert the positioning shaft and the connecting rod shaft hole until the upper limit plate abuts the top surface of the crank arm, then drive the lower limit block to radially extend relative to the telescopic column through the radial drive member, and then drive the telescopic column to axially contract relative to the positioning shaft through the axial drive member, so that the lower limit block abuts against the bottom surface of the crank arm, thereby clamping the movable base and the crank arm through the upper limit plate and the lower limit block.

9. The method of use according to claim 6, wherein: When performing the movable guide vane action test in step 3, the crank arm of the movable guide vane under test is pushed or pulled by the cylinder to rotate around the axis of the shaft neck. When the cylinder moves, the force F output by the cylinder can be decomposed into two directions, namely, force F1 along the direction of the crank arm and force F2 perpendicular to the direction of the crank arm.

10. The method of use according to claim 8, characterized in that: The force value measured by the push-pull force sensor is F. F is not the actual force that pushes or pulls the crank arm to rotate. The angle sensor is required to measure the real-time angle α between the oil cylinder and the crank arm, and then calculate the force F2 perpendicular to the crank arm direction. F2 is multiplied by the crank arm's lever arm L1 to get the torque M that pushes or pulls the crank arm to rotate. If the friction force of the crank arm rotation needs to be calculated, the torque M is divided by the friction part lever arm L2 to get the friction force value F. The calculation process and formula are as follows: The push and pull forces F are measured in real time by the push and pull force sensors. The angle α between the oil cylinder and the crank arm is measured in real time by the angle sensor. The crank arm force arm L1 and the friction force arm L2 are inherent parameters of the equipment and can be pre-recorded or input in real time. After the test starts, the force F2 perpendicular to the crank arm is calculated: F2=F×sinα; Then the torque M that pushes or pulls the crank arm to rotate is: M=F2×L1; When the crank arm rotates at a constant speed, it can be considered that the push and pull forces only overcome the friction force to do work, that is, the friction force F is: F = M ÷ L2; The friction force F obtained here is actually the dynamic friction force. If you need to measure the maximum static friction force, you should adjust the test method to continuously increase the push and pull force F until the crank arm rotates, record the push and pull force F at the moment of pushing, and repeat the above calculation.

11. The method of use according to claim 9, characterized in that: If the crank arm does not rotate at a constant speed during pushing or pulling, the pushing or pulling torque M not only needs to overcome the friction, but also drives the crank arm to accelerate or decelerate, which will cause calculation errors. Therefore, in the electronic control system, a speed feedback adjustment algorithm will be used to achieve constant rotation of the crank arm.

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