Novel shock absorber for deep well hoisting steel wire rope

Abstract

The invention discloses a novel shock absorber for a deep well hoisting steel wire rope, which utilizes the advantages that a hydraulic spring passes through low frequency and resists high frequency and a hydraulic inerter passes through high frequency and resists low frequency, utilizes resultant force generated by the spring, the inerter and damping to counteract abnormal impact on the steel wire rope, and equivalently enhances the inertial effect of a flywheel through a hydraulic inerter mechanism. The vibration phase in the inerter damper is asynchronous with the main body structure of the elevator, the effective deformation stroke of the dissipation device is amplified, the energy dissipation efficiency is improved, and the vibration of the steel wire rope is inhibited. According to the novel shock absorber for the deep well hoisting steel wire rope, the requirement for stable operation of a deep well hoist under the limitation of objective factors such as long-distance power supply difficulty, narrow shaft space and electromagnetic explosion prevention in a deep well can be met, and efficient absorption and rapid dissipation of vibration energy of the deep well hoisting steel wire rope are achieved; meanwhile, abrasion of the steel wire rope can be reduced, service time is prolonged, and high-speed and stable operation of the deep well elevator is guaranteed.

Description

Technical Field

[0001] This invention relates to the field of vibration damping devices for hoisting wire ropes in deep mines, and specifically to a novel vibration damper for hoisting wire ropes in deep mines. Background Technology

[0002] Coal is a vital energy source for my country, contributing to the country's industrial development and economic growth. Furthermore, coal plays a crucial role in industries such as chemical engineering and metallurgy, providing essential energy security for national infrastructure construction. Most of my country's coal reserves are located in deep wells, and deep well hoists are essential equipment connecting the surface and underground. Wire ropes play a crucial role in these hoists. As the hoist cage extends deeper into the well, the length of the wire rope continuously increases. Under the harsh conditions underground, it is subjected to alternating loads, leading to accelerated fatigue wear and a high risk of breakage. This severely restricts the application and development of kilometer-level deep well hoisting systems.

[0003] Currently, vibration reduction methods for mine hoist wire ropes mainly focus on active vibration control technology in shallow well environments. However, this technology requires real-time monitoring and feedback of the cage or wire rope's operating status, which is difficult to implement by placing sensors on its surface in practice. Furthermore, the active control system relies on an external power source, while the harsh environment and confined space of deep wells, coupled with safety restrictions such as electromagnetic explosion protection, further weaken the applicability of this technology for vibration reduction in deep well hoist wire ropes. Summary of the Invention

[0004] To suppress the vibration of deep well hoisting wire ropes, this invention discloses a novel vibration damper for deep well hoisting wire ropes, in order to solve the problems mentioned in the background above.

[0005] To achieve the above objectives, the technical solution of the present invention is as follows:

[0006] A novel vibration damper for hoisting steel wire ropes in deep wells includes a three-cavity main structure 1, a hydraulic inertial container 2, an upper U-shaped frame 26, a lower U-shaped frame 27, a #1 pin 28, and a #2 pin 29. The three-cavity main structure 1 further includes a piston rod 3, a cylinder 5, a sealing cover 10, a #1 sealing ring 14, a #2 sealing ring 17, a #3 sealing ring 18, a valve core 6, and a valve sleeve 8. The hydraulic inertial container 2 includes a hydraulic rectifier bridge 30, a hydraulic pipe 31, a hydraulic motor 32, and a flywheel 33.

[0007] The main structure of the piston rod 3 is a hollow cylinder. A piston rod connector 24 is machined at the middle of the upper end of the hollow cylinder. The piston rod connector 24 is a cuboid with a thickness of 1 / 3 to 1 / 2 of the inner diameter of the hollow cylinder. A through hole 11 is machined at 2 / 5 of the upper end of the piston rod connector 24. The diameter of the through hole 11 is 1 / 3 of the inner diameter of the hollow cylinder. A frustum with an outer diameter 0.02-0.05 mm smaller than the inner diameter of the cylinder body 5 is machined at the lower part of the piston rod 3. A stepped through hole 39 is opened on the frustum. The larger diameter hole in the stepped through hole 39 is located at the lower part, where a check valve 16 is installed. The check valve 16 is normally closed. A sealing ring groove for a sealing ring 17 is machined on the outside of the frustum. The sealing ring 17 is placed in the sealing ring groove.

[0008] The cylinder body 5 is a hollow cylinder with an opening at one end and a cuboid cylinder connector 25 at the other end. A #2 through hole 19 is machined at the lower 1 / 3 of the cylinder connector 25. The diameter of the #2 through hole 19 is 1 / 4 of the inner diameter of the hollow cylinder, and the axis of the #2 through hole 19 is perpendicular to the axis of the #1 through hole 11. The ratio of the height of the hollow part of the cylinder body 5 to the height of the hollow part of the piston rod 3 is 0.8.

[0009] The valve core 6 is a cylinder. A limiting frustum 20 is machined at the bottom end of the valve core 6, 2 cm-3 cm from the end face. The diameter of the limiting frustum 20 is 1 cm-1.5 cm larger than the diameter of the valve core. M sets of parallel throttling grooves 21 are machined 10 cm-13 cm above the limiting frustum 20. Each set contains two or more throttling grooves 21 with a spacing of 2 cm-2.5 cm. M is a positive integer ≥5. Two valve core guide holes 23 are machined along the valve core axis at the upper end of the cylinder. The two valve core guide holes 23 are connected to the two rows of parallel throttling grooves 21 respectively.

[0010] The sealing cap 10 is a hollow frustum, the inner diameter of which is 0.02 mm-0.05 mm larger than the outer diameter of the piston rod 3. The maximum outer diameter of the frustum is the same as the outer diameter of the cylinder 5, and the minimum outer diameter is the same as the inner diameter of the cylinder 5. A sealing ring groove for fitting the #1 sealing ring 14 is opened inside the cylinder with the larger diameter, and the #1 sealing ring 14 is placed in the sealing ring groove.

[0011] The valve sleeve 8 is a hollow circular ring, the diameter of which is 0.02 mm-0.05 mm larger than the outer diameter of the valve core 6, and its outer diameter is the same as the inner diameter of the piston rod 3 hole. Valve sleeve guide holes 15 and 2# stepped through holes 40 are evenly distributed on the valve sleeve 8. The valve sleeve guide holes 15 are cylindrical through holes that run vertically through the valve sleeve. The larger diameter hole in the 2# stepped through hole 40 is located at the top, where a 2# one-way valve 22 is installed. The 2# one-way valve 22 is normally closed. A sealing ring groove for a 3# sealing ring 18 is machined in the middle of the inner wall of the valve sleeve 8, and the 3# sealing ring 18 is placed in the sealing ring groove.

[0012] The upper U-shaped frame 26 is a U-shaped plate, consisting of two parallel #1 side plates 261 and a semi-circular #1 connecting plate 262. The lower end of the #1 side plate 261 has a circular #3 through hole 263, the diameter of which is the same as the diameter of the #2 through hole 19. A rectangular #1 hollow hole 264 is machined in the middle of the #1 side plate 261. A #1 lifting hole 265, a circular through hole, is opened in the middle of the circular end face of the #1 connecting plate 262. The circular end face of the #1 connecting plate 262 faces upwards, and the two #1 side plates 261 are respectively fixed to the lower end face of the #1 connecting plate 262. The lower U-shaped frame 27 is a U-shaped plate, consisting of two parallel #2 side plates 261... It consists of a 71 and a semi-circular #2 connecting plate 272. The lower end of the #2 side plate 271 has a circular #4 through hole 273, the diameter of which is the same as the diameter of the #1 through hole 11. A rectangular #2 hollow hole 274 is machined in the middle of the #2 side plate 271. A #2 lifting hole 275, a circular through hole, is formed in the middle of the circular end face of the #2 connecting plate 272. The circular end face of the #2 connecting plate 272 faces downwards. The two #2 side plates 271 are respectively fixed to the upper end face of the #2 connecting plate 272. The diameter of the #2 lifting hole 275 is the same as the diameter of the #1 lifting hole 265, and the width of the #2 side plate 271 is 0.2 mm smaller than the width of the #1 side plate 261. The width of connecting plate 272 is 0.2 mm-0.5 mm smaller than that of connecting plate 262. The length ratio of side plate 261 to side plate 271 is 1.2. The diameter of pin 28 is the same as that of through hole 263, and the diameter of pin 29 is the same as that of through hole 273.

[0013] The hydraulic rectifier bridge 30 is composed of two head-to-head one-way valve branches connected in series and two tail-to-tail one-way valve branches connected in parallel. The first one-way valve 301 and the second one-way valve 303 connected in series at the head form the first branch, and the third one-way valve 302 and the fourth one-way valve 304 connected in series at the tail form the second branch.

[0014] The valve core 6 is machined with a limiting frustum 20 on one side, which is fixed to the bottom end face inside the cylinder body 5. The cylinder body connector 25 faces downward. The end face of the lower frustum of the piston rod 3 is flush with and fixed to one end face of the valve sleeve 8. The piston rod connector 24 of the piston rod 3 faces upward. The valve sleeve 8 is fitted onto the valve core 6. The sealing cover 10 is fitted onto the piston rod 3 to seal the cylinder body 5. The upper U-shaped bracket 26 and the lower U-shaped bracket 27 are installed at a 90° offset, so that the lower U-shaped bracket 27 is embedded in the upper U-shaped bracket 26. At the same time, the 1# connecting plate 262 faces upward and the 2# connecting plate 272 faces downward. The 1# pin 2 8 passes through two through holes 263 and 19 at the lower end of the 1# side plate 261 of the upper U-shaped frame, and 2# pin 29 passes through two through holes 273 and 1# through hole 11 at the lower end of the 2# side plate 271 of the lower U-shaped frame, and 1# pin 28 and 2# pin 29 are fixed to the 1# side plate 261 of the upper U-shaped frame and the 2# side plate 271 of the lower U-shaped frame respectively; the lifting wire rope 37 passes through the 1# hoisting hole 265 on the upper U-shaped frame 26 and the 2# hoisting hole 275 on the lower U-shaped frame 27 respectively and is fixed to the upper U-shaped frame 26 and the lower U-shaped frame 27.

[0015] #3 sealing ring 18 seals the valve core 6 and valve sleeve 8, forming an energy storage chamber 4 in the internal cavity of the piston rod 3. The upper part of the energy storage chamber 4 is filled with nitrogen gas 12, and the lower part is filled with hydraulic oil 13. #2 sealing ring 17 seals the piston rod 3 and cylinder 5, and #1 sealing ring 14 seals the piston rod 3 and sealing cover 10. The upper part of the outer truncated cone of the piston rod 3, the lower part of the sealing cover 10, and the interior of the cylinder 5 form an auxiliary chamber 9, which is filled with hydraulic oil 13. The truncated cone of the piston rod 3 and the lower part of the valve sleeve 8, together with the interior of the cylinder 5, form the main... The auxiliary chamber 9 is filled with hydraulic oil 13. When the 1# check valve 16 is opened, the hydraulic oil 13 flows from the auxiliary chamber 9 to the main chamber 7. When the 2# check valve 22 is opened, the hydraulic oil 13 flows from the main chamber 7 to the energy storage chamber 4. The auxiliary chamber 9 and the main chamber 7 are respectively connected to the upper middle and lower middle of the hydraulic rectifier bridge 30 through hydraulic pipes 31. The middle of the first branch and the second branch are respectively connected to the outlet and inlet of the hydraulic motor 32 through hydraulic pipes 31. The output shaft of the hydraulic motor 32 is connected to the flywheel 33.

[0016] The throttling groove 21 is a round hole type 211 valve port, a triangular type 212 valve port, or a rectangular type 213 valve port.

[0017] The present invention has the following beneficial effects:

[0018] 1) This invention utilizes the advantages of hydraulic springs (allowing low frequencies while blocking high frequencies) and hydraulic inertial capacitance (allowing high frequencies while blocking low frequencies), integrating them into a three-cavity main structure. It proposes a passive vibration damper based on the adaptive adjustment of hydraulic springs, hydraulic inertial capacitance, and damping according to working conditions. The inertial capacitance system is applied to the vibration damping of the hoisting wire rope. Through the hydraulic inertial capacitance mechanism, the inertial effect of the flywheel is equivalently enhanced, causing the vibration phase inside the inertial capacitance damper to be asynchronous with the main structure of the hoist. This asynchronous vibration amplifies the effective deformation stroke of the dissipation device, thereby improving energy dissipation efficiency and further suppressing the vibration of the wire rope.

[0019] 2) This invention utilizes nitrogen gas in the energy storage chamber to provide additional buffering. A valve core with a hollow structure, a certain number of throttling grooves on its surface, and internal holes is designed. The sliding of the valve sleeve embedded in the valve core changes the flow area of ​​the hydraulic oil in the throttling grooves, thereby achieving passive variable damping energy dissipation of the wire rope. The throttling grooves can be circular, triangular, or rectangular, etc., and different damping effects are achieved through the design of the groove shape. Under no-load conditions, the valve port has the largest flow area and the smallest damping; under full-load conditions, the valve port has the smallest flow area and the largest damping; during the transition between no-load and full-load conditions, the valve port is in a partially conductive state, and the damping adaptively adjusts according to the operating conditions of the wire rope.

[0020] 3) This invention eliminates the need for external power sources and heavy-duty actuators to adaptively adjust damping according to the working conditions of the wire rope. It breaks through the key technology of built-in passive variable damping throttle valve vibration damper. By using the combined force generated by springs, inertial capacitance, and damping, it counteracts abnormal impacts on the wire rope. This can ensure the stable operation of deep well hoists under objective limitations such as difficulty in long-distance power supply, confined shaft space, and electromagnetic explosion protection. It achieves efficient absorption and rapid dissipation of vibration energy of deep well hoisting wire ropes, while reducing wire rope wear, increasing service life, and ensuring high-speed and stable operation of deep well hoists. This further improves the safe and efficient mining and utilization of deep coal resources. Attached Figure Description

[0021] Figure 1 This is a schematic diagram of the overall structure of the novel vibration damper of the present invention;

[0022] Figure 2 This is a schematic diagram of the three-cavity main structure and the upper and lower U-shaped frames of the present invention;

[0023] Figure 3 This is a schematic diagram of the main structure of the three-cavity body and the upper and lower U-shaped frames of the present invention;

[0024] Figure 4 This is a cross-sectional schematic diagram of the side view of the main structure of the three-cavity body of the present invention;

[0025] Figure 5 This is a top view of the piston rod of the present invention;

[0026] Figure 6 This is a top view of the valve sleeve of the present invention;

[0027] Figure 7 This is a schematic diagram of the upper U-shaped frame structure of the present invention;

[0028] Figure 8 This is a schematic diagram of the lower U-shaped frame structure of the present invention;

[0029] Figure 9 This is a schematic diagram of the valve port configuration of the novel shock absorber valve core throttling groove dispersion circular hole type of the present invention;

[0030] Figure 10 This is a diagram showing the configuration of the novel shock absorber valve core throttling groove with a dispersed triangular valve port according to the present invention.

[0031] Figure 11 This is a schematic diagram of the novel shock absorber valve core throttling groove with a dispersed rectangular valve port configuration according to the present invention.

[0032] Figure 12 This is a schematic diagram of the valve sleeve position under no-load conditions for the novel vibration damper of the present invention;

[0033] Figure 13 This is a schematic diagram of the valve sleeve position under full load conditions for the novel vibration damper of the present invention;

[0034] Figure 14 This is a schematic diagram of the valve sleeve position for the novel vibration damper of the present invention under no-load and full-load transition conditions;

[0035] Figure 15 This is a schematic diagram of the operation of the deep well hoist of the present invention;

[0036] Figure 16 This is a simplified schematic diagram of the novel vibration damper of the present invention.

[0037] In the diagram, 1-Three-cavity main structure, 2-Hydraulic inertia, 3-Piston rod, 4-Energy storage chamber, 5-Cylinder body, 6-Valve core, 7-Main chamber, 8-Valve sleeve, 9-Auxiliary chamber, 10-Sealing cover, 11-1# Through hole, 12-Nitrogen, 13-Hydraulic oil, 14-1# Sealing ring, 15-Valve sleeve guide hole, 16-1# Check valve, 17-2# Sealing ring, 18-3# Sealing ring, 19-2# Through hole, 20-Limiting frustum, 21-Throttle groove, 22-2# Check valve, 23-Valve core guide hole, 24-Piston rod connector, 25-Cylinder body connector, 26-Upper U-shaped frame, 261-1# Side plate, 262-1# Connecting plate, 263-3 # Through hole, 264-1# hollow hole, 265-1# lifting hole, 27-lower U-shaped frame, 271-2# side plate, 272-2# connecting plate, 273-4# through hole, 274-2# hollow hole, 275-2# lifting hole, 28-1# pin, 29-2# pin, 30-hydraulic rectifier bridge, 301-first check valve, 302-third check valve, 303-second check valve, 304-fourth check valve, 31-hydraulic pipe, 32-hydraulic motor, 33-flywheel, 34-new type of shock absorber, 35-friction drum, 36-head sheave, 37-lifting wire rope, 38-cage, 39-1# stepped through hole, 40-2# stepped through hole. Detailed Implementation

[0038] The detailed technical solution of the present invention is described below with reference to the accompanying drawings:

[0039] A new type of vibration damper for hoisting steel wire ropes in deep wells, such as Figure 1-4 As shown, the structure includes a three-cavity main structure 1, a hydraulic inertial container 2, an upper U-shaped frame 26, a lower U-shaped frame 27, a #1 pin 28, and a #2 pin 29. The three-cavity main structure 1 further includes a piston rod 3, a cylinder 5, a sealing cover 10, a #1 sealing ring 14, a #2 sealing ring 17, a #3 sealing ring 18, a valve core 6, and a valve sleeve 8. The hydraulic inertial container 2 includes a hydraulic rectifier bridge 30, a hydraulic pipe 31, a hydraulic motor 32, and a flywheel 33. The main structure of the piston rod 3 is a hollow cylinder, with a piston rod connector 24 machined at the upper center of the hollow cylinder. The piston rod connector 24 is a cuboid. The thickness is 1 / 3 to 1 / 2 of the inner diameter of the hollow cylinder. A through hole 11 is machined at 2 / 5 of the upper end of the piston rod connector 24. The diameter of the through hole 11 is 1 / 3 of the inner diameter of the hollow cylinder. A frustum with an outer diameter 0.02-0.05 mm smaller than the inner diameter of the cylinder body 5 is machined at the lower part of the piston rod 3. A stepped through hole 39 is opened on the frustum. The larger diameter hole in the stepped through hole 39 is located at the lower part, where a check valve 16 is installed. The check valve 16 is normally closed. A sealing ring groove adapted to a sealing ring 17 is machined on the outside of the frustum. The sealing ring 17 is placed in the sealing ring groove.

[0040] The cylinder body 5 is a hollow cylinder with an opening at one end and a cuboid cylinder connector 25 at the other end. A #2 through hole 19 is machined at the lower 1 / 3 of the cylinder connector 25. The diameter of the #2 through hole 19 is 1 / 4 of the inner diameter of the hollow cylinder. The axis of the #2 through hole 19 is perpendicular to the axis of the #1 through hole 11. The ratio of the height of the hollow part of the cylinder body 5 to the height of the hollow part of the piston rod 3 is 0.8.

[0041] The valve core 6 is a cylinder. A limiting frustum 20 is machined at the bottom end of the valve core 6, 2 cm-3 cm from the end face. The diameter of the limiting frustum 20 is 1 cm-1.5 cm larger than the diameter of the valve core. M sets of parallel throttling grooves 21 are machined 10 cm-13 cm above the limiting frustum 20. Each set contains two or more throttling grooves 21 with a spacing of 2 cm-2.5 cm. M is a positive integer ≥5. Two valve core guide holes 23 are machined along the valve core axis at the upper end of the cylinder. The two valve core guide holes 23 are connected to the two parallel rows of throttling grooves 21.

[0042] The sealing cap 10 is a hollow frustum, the inner diameter of which is 0.02 mm-0.05 mm larger than the outer diameter of the piston rod 3. The maximum outer diameter of the frustum is the same as the outer diameter of the cylinder 5, and the minimum outer diameter is the same as the inner diameter of the cylinder 5. A sealing ring groove for fitting the No. 1 sealing ring 14 is opened inside the cylinder with the larger diameter, and the No. 1 sealing ring 14 is placed in the sealing ring groove.

[0043] The valve sleeve 8 is a hollow circular ring, the diameter of which is 0.02 mm-0.05 mm larger than the outer diameter of the valve core 6, and its outer diameter is the same as the inner diameter of the piston rod 3 hole. Valve sleeve guide holes 15 and 2# stepped through holes 40 are evenly distributed on the valve sleeve 8. The valve sleeve guide holes 15 are cylindrical through holes that run vertically through the valve sleeve. The larger diameter hole in the 2# stepped through hole 40 is located at the top, where a 2# one-way valve 22 is installed. The 2# one-way valve 22 is normally closed. A sealing ring groove adapted to a 3# sealing ring 18 is machined in the middle of the inner wall of the valve sleeve 8, and the 3# sealing ring 18 is placed in the sealing ring groove.

[0044] like Figure 7-8As shown, the upper U-shaped frame 26 is a U-shaped plate, consisting of two parallel #1 side plates 261 and a semi-circular #1 connecting plate 262. The lower end of the #1 side plate 261 has a circular #3 through hole 263, the diameter of which is the same as the diameter of the #2 through hole 19. A rectangular #1 hollow hole 264 is machined in the middle of the #1 side plate 261. A #1 lifting hole 265, a circular through hole, is opened in the middle of the circular end face of the #1 connecting plate 262. The circular end face of the #1 connecting plate 262 faces upwards, and the two #1 side plates 261 are respectively fixed to the lower end face of the #1 connecting plate 262. The lower U-shaped frame 27 is a U-shaped plate, consisting of two parallel #2 side plates 261. The system consists of a plate 271 and a semi-circular connecting plate 272. The lower end of the connecting plate 271 has a circular through hole 273 (circular size 4), the diameter of which is the same as the diameter of through hole 11 (circular size 11). A rectangular hollow hole 274 (rectangular size 274) is machined in the center of the connecting plate 271. A lifting hole 275 (circular size 275) is formed in the center of the circular end face of the connecting plate 272. The circular end face of the connecting plate 272 faces downwards. The two connecting plates 271 are fixed to the upper end face of the connecting plate 272. The diameter of the lifting hole 275 is the same as the diameter of the lifting hole 265 (circular size 11), and the width of the connecting plate 271 is 0.2 mm smaller than the width of the connecting plate 261 (circular size 11). The width of connecting plate 272 is 0.2 mm-0.5 mm smaller than that of connecting plate 262. The length ratio of side plate 261 to side plate 271 is 1.2. The diameter of pin 28 is the same as that of through hole 263, and the diameter of pin 29 is the same as that of through hole 273.

[0045] The hydraulic rectifier bridge 30 is composed of two head-to-head one-way valve branches connected in series and two tail-to-tail one-way valve branches connected in parallel. The first one-way valve 301 and the second one-way valve 303 connected in series at the head form the first branch, and the third one-way valve 302 and the fourth one-way valve 304 connected in series at the tail form the second branch.

[0046] The valve core 6 is machined with a limiting frustum 20 on one side, which is fixed to the bottom end face inside the cylinder body 5. The cylinder body connector 25 faces downward. The end face of the lower frustum of the piston rod 3 is flush with and fixed to one end face of the valve sleeve 8. The piston rod connector 24 of the piston rod 3 faces upward. The valve sleeve 8 is fitted onto the valve core 6. The sealing cover 10 is fitted onto the piston rod 3 to seal the cylinder body 5. The upper U-shaped bracket 26 and the lower U-shaped bracket 27 are installed at a 90° offset, so that the lower U-shaped bracket 27 is embedded in the upper U-shaped bracket 26. At the same time, the 1# connecting plate 262 faces upward and the 2# connecting plate 272 faces downward. The 1# pin 2 8 passes through two through holes 263 and 19 at the lower end of the 1# side plate 261 of the upper U-shaped frame, and 2# pin 29 passes through two through holes 273 and 1# through holes 11 at the lower end of the 2# side plate 271 of the lower U-shaped frame, and 1# pin 28 and 2# pin 29 are fixed to the 1# side plate 261 of the upper U-shaped frame and the 2# side plate 271 of the lower U-shaped frame respectively; the lifting wire rope 37 passes through the 1# hoisting hole 265 on the upper U-shaped frame 26 and the 2# hoisting hole 275 on the lower U-shaped frame 27 respectively and is fixed to the upper U-shaped frame 26 and the lower U-shaped frame 27.

[0047] #3 sealing ring 18 seals the valve core 6 and valve sleeve 8, forming an energy storage chamber 4 in the internal cavity of the piston rod 3. The upper part of the energy storage chamber 4 is filled with nitrogen gas 12, and the lower part is filled with hydraulic oil 13. #2 sealing ring 17 seals the piston rod 3 and cylinder 5, and #1 sealing ring 14 seals the piston rod 3 and sealing cover 10. The upper part of the outer truncated cone of the piston rod 3, the lower part of the sealing cover 10, and the interior of the cylinder 5 form an auxiliary chamber 9, which is filled with hydraulic oil 13. The truncated cone of the piston rod 3 and the lower part of the valve sleeve 8, together with the interior of the cylinder 5, form the main... The auxiliary chamber 9 is filled with hydraulic oil 13. When the 1# check valve 16 is opened, the hydraulic oil 13 flows from the auxiliary chamber 9 to the main chamber 7. When the 2# check valve 22 is opened, the hydraulic oil 13 flows from the main chamber 7 to the energy storage chamber 4. The auxiliary chamber 9 and the main chamber 7 are respectively connected to the upper middle and lower middle of the hydraulic rectifier bridge 30 through hydraulic pipes 31. The middle of the first branch and the second branch are respectively connected to the outlet and inlet of the hydraulic motor 32 through hydraulic pipes 31. The output shaft of the hydraulic motor 32 is connected to the flywheel 33.

[0048] like Figure 9-11 The throttling groove 21 is a round hole type 211 valve port, a triangular type 212 valve port, or a rectangular type 213 valve port.

[0049] like Figure 12-14 Let the upper part, lower part, and the area between the upper and lower parts of the throttling groove 21 be positions A, B, and C, respectively. Under no-load conditions, the valve sleeve 8 is in position A, the flow area of ​​the throttling groove 21 is the largest, and the damping is the smallest. Under full-load conditions, the valve sleeve 8 is in position B, the flow area of ​​the throttling groove 21 is the smallest, and the damping is the largest. Under the transition conditions between no-load and full-load conditions, the valve sleeve 8 is in position C, part of the throttling groove 21 is in a conducting state, and the damping is adaptively adjusted according to the operating conditions.

[0050] like Figure 15 As shown, each hoisting wire rope 37 of the deep well hoist located above the cage 38 is cut 20cm from the upper end face of the cage 38. The cut hoisting wire ropes 37 are respectively threaded into the No. 1 hoisting hole 265 on the upper U-shaped frame 26 and the No. 2 hoisting hole 275 on the lower U-shaped frame 27, and are fixed to the upper U-shaped frame 26 and the lower U-shaped frame 27. A new type of vibration damper 34 is connected to the hoisting wire rope 37. The function of the upper U-shaped frame 26 and the lower U-shaped frame 27 is to transmit the tension on the hoisting wire rope 37 and convert it into pressure acting on the three-cavity main structure 1. During the operation of the friction drum 35 and the sheave 36 of the deep well hoist, the hoisting wire rope 37 drives the cage 38 to descend to the kilometer-deep well. During this process, the mass m1, stiffness k1, and damping c1 of the hoisting wire rope change in real time, and the cage 38 is subjected to impact and its vibration displacement Z u During this process, the piston rod 3 moves up and down within the cylinder 5. When the piston rod 3 moves downward, it drives the hydraulic motor 32 through the fourth check valve 304 and the first check valve 301 of the hydraulic inertia capacity 2 circuit. When it moves upward, it drives the hydraulic motor 32 through the third check valve 302 and the second check valve 303, converting some of the kinetic energy into rotational kinetic energy stored in the flywheel 33. The rotational inertia of the flywheel 33 is used to provide the required inertia capacity effect for the system. During the movement, the nitrogen gas 12 in the energy storage chamber 4 provides the hydraulic spring stiffness k2. The relative movement between the valve core 6 and the valve sleeve 8 causes the hydraulic oil 13 to flow through the throttling groove 21, and its flow area dynamically changes with the movement state of the piston rod 3, generating a damping force characterized by the damping coefficient c2. This variable damping characteristic effectively dissipates the vibration energy. The resultant force F of the stiffness k2, damping c2, and inertia capacity b of the new type of vibration damper 34 reduces the vibration displacement Z of the lifting wire rope. s This reduces vibration and impact, ensuring a stable lifting process.

[0051] A simplified schematic diagram of the principle of the new type of shock absorber 34 is shown below. Figure 16 As shown, when cage 38 is disturbed by F ext The dynamic equation of the system is:

[0052]

[0053] In the formula, F is the resultant force of the combined action, m1 is the mass of the hoisting wire rope, m2 is the mass of the cage, k1 is the stiffness of the hoisting wire rope, k2 is the stiffness of the new type of vibration damper, b is the inertia coefficient of the new type of vibration damper, c1 is the damping of the hoisting wire rope, c2 is the damping of the new type of vibration damper, and Z... s To increase the vibration displacement of the wire rope, Z u This represents the vibration displacement of the cage.

[0054] If the deep well hoist does not have the new type of vibration damper 34, that is b=0, disturbance F extThe rigid cage 38 will directly act on the hoisting wire rope 37, causing it to experience abnormal impact and vibration instability.

[0055] If the new type of shock absorber 34 is installed, the disturbance F of the cage 38 will be reduced. ext First, it acts on the new type of shock absorber 34, causing relative movement between the piston rod 3 and the cylinder 5. The valve sleeve 8 slides downward along the valve core 6, reducing the volume of the main chamber 7. The hydraulic spring formed by nitrogen 12 and hydraulic oil 13 stores vibration energy. In order to reduce the vibration peak of the lifting wire rope 37, the new type of shock absorber 34 should have a low damping c2 and a high stiffness k2 at the moment of vibration so that the hydraulic spring can store more energy. That is, by installing a 2# check valve 22 on the valve sleeve 8, the hydraulic oil 13 can flow through the main chamber 7 and the energy storage chamber 4 when the main chamber 7 is just compressed, which can effectively ensure that the damping c2 of the new type of shock absorber is low and the stiffness k2 plays a high role during oil flow.

[0056] The hydraulic inertial capacity 2 part converts part of the kinetic energy into rotational kinetic energy and stores it in the flywheel 33 through the hydraulic motor 32. The rotational inertia of the flywheel 33 is used to provide the inertial capacity effect required by the system. The hydraulic inertial capacity 2 and the hydraulic spring can adjust the inertial and stiffness characteristics of the structure, that is, by frequency tuning to avoid resonance between the main structure and external excitation.

[0057] The throttling groove 21 and the valve core guide hole 23 of the valve core 6 are connected to form a passive variable damping energy dissipation part, such as Figure 12-14 As shown: Let the upper part, lower part, and the area between the upper and lower parts of the throttling groove 21 be positions A, B, and C, respectively. Under no-load conditions, the valve sleeve 8 is in position A, the flow area of ​​the throttling groove 21 is the largest, and the damping is the smallest. Under full-load conditions, the valve sleeve 8 is in position B, the flow area of ​​the throttling groove 21 is the smallest, and the damping is the largest. Under the transition condition between no-load and full-load conditions, the valve sleeve 8 is in position C, and part of the throttling groove 21 is in a conductive state. Figure 9-11 As shown: The throttling groove 21 is a round hole type 121 valve port, a triangular type 122 valve port, or a rectangular type 123 valve port. When there are more than 5 groups of throttling grooves 21 or 2 in each group, a valve core guide hole parallel to the valve core guide hole 23 needs to be added to the end of the valve core 6 to communicate with it, so as to ensure the effective flow of hydraulic oil 13. By utilizing the relative position of the valve sleeve 8 and the valve core 6, the damping c2 of the new type of shock absorber is adjusted by the adaptive change of the flow area of ​​hydraulic oil 13 flowing through the throttling groove 21, so that the vibration energy of the cage 38 is dissipated inside the new type of shock absorber 34.

[0058] When the cage 38 is impacted in the deep well, the piston rod 3 moves downward within the cylinder 5, and the new type of shock absorber 34 is in the compression stroke. At this time, the volume of the main chamber 7 and the energy storage chamber 4 decreases, nitrogen 12 is compressed, and the volume of the auxiliary chamber 9 increases. Hydraulic oil 13 first flows from the main chamber 7 into the energy storage chamber 4 through the valve sleeve guide hole 15 and the #2 check valve 22. As the compression stroke continues, the hydraulic oil 13 drives the hydraulic motor 32 from the main chamber 7 through the fourth check valve 304, and then enters the auxiliary chamber 9 through the first check valve 301, driving the flywheel 33 to rotate in one direction and store inertial kinetic energy, realizing the hydraulic inertial capacitance effect. At the same time, the hydraulic oil 13 flows to the energy storage chamber 4 through the throttling groove 21 on the valve core 6 along the valve core guide hole 23. Throughout the process, the valve sleeve 8 moves downward with the pressure change, so that the flow area of ​​the valve port gradually decreases from the maximum under no-load conditions to the minimum under full load conditions, and the damping force increases accordingly, realizing passive adaptive energy consumption.

[0059] As the impact weakens and the new shock absorber 34 enters its extension stroke, the piston rod 3 moves upward, increasing the volume of the main chamber 7 and the energy storage chamber 4, while decreasing the volume of the auxiliary chamber 9. Hydraulic oil 13 flows from the auxiliary chamber 9 through the third check valve 302 to drive the hydraulic motor 32, and then flows back to the main chamber 7 through the second check valve 303. The flywheel 33 continues to rotate, and its stored inertial kinetic energy reacts on the piston rod 3 through the hydraulic circuit, forming a damping force opposite to the direction of acceleration. Simultaneously, the valve sleeve 8 moves upward, gradually restoring the throttle valve orifice area, correspondingly weakening the damping force, and the system gradually returns to its initial state.

[0060] Based on the characteristics of hydraulic springs passing low frequencies and blocking high frequencies, and hydraulic inertial capacity 2 passing high frequencies and blocking low frequencies, during the entire working process, the hydraulic spring unit absorbs low-frequency large-amplitude vibrations through the compliance of the cavity, and exhibits high dynamic stiffness due to hydraulic resistance at high frequencies to block high-frequency transmission; hydraulic inertial capacity 2 converts reciprocating hydraulic energy into unidirectional rotational inertial energy through hydraulic rectifier bridge 30 and flywheel 33, realizing inertial suppression and phase adjustment of medium and high frequency vibrations; the passive variable damping part relies on an adaptive throttling mechanism to continuously convert vibration energy into heat energy. The new vibration damper 34, through the parallel and synergistic effect of its stiffness k2, inertial capacity b, and damping c2, jointly generates a resultant force F, effectively isolating the disturbance F received by the cage 38. ext The direct impact on the hoisting wire rope 37. The new vibration damper 34 can adaptively adjust the output force according to changes in working conditions, suppressing the vibration displacement Z of the hoisting wire rope. s This reduces its vibration and impact response, and coordinates the balance of abnormal dynamic tension in the lifting wire rope 37, ultimately achieving efficient absorption and wideband rapid dissipation of vibration energy of the lifting wire rope 37.

Claims

1. A novel vibration damper for hoisting steel wire ropes in deep wells, characterized in that: It includes a three-cavity main structure, a hydraulic inertial container, an upper U-shaped frame, a lower U-shaped frame, a #1 pin, and a #2 pin. The three-cavity main structure further includes a piston rod, a cylinder, a sealing cover, a #1 sealing ring, a #2 sealing ring, a #3 sealing ring, a valve core, and a valve sleeve. The hydraulic inertial container includes a hydraulic rectifier bridge, hydraulic pipes, a hydraulic motor, and a flywheel. The piston rod has a hollow cylinder as its main structure. A piston rod connector is machined at the upper center of the hollow cylinder. The piston rod connector is a cuboid with a thickness of 1 / 3 to 1 / 2 of the inner diameter of the hollow cylinder. A #1 through hole is machined at 2 / 5 of the upper end of the piston rod connector, with a diameter of 1 / 3 of the inner diameter of the hollow cylinder. A frustum with an outer diameter 0.02-0.05 mm smaller than the inner diameter of the cylinder is machined at the lower part of the piston rod. A #1 stepped through hole is opened on the frustum, with the larger diameter hole located at the bottom, where a #1 one-way valve is installed. The #1 one-way valve is normally closed. A sealing ring groove for a #2 sealing ring is machined on the outer side of the frustum, and the #2 sealing ring is placed in this sealing ring groove. The cylinder body is a hollow cylinder with an open end and a rectangular cylinder connector at the other end. A No. 2 through hole is machined at the lower 1 / 3 of the cylinder connector. The diameter of the No. 2 through hole is 1 / 4 of the inner diameter of the hollow cylinder, and the axis of the No. 2 through hole is perpendicular to the axis of the No. 1 through hole. The ratio of the height of the hollow part of the cylinder body to the height of the hollow part of the piston rod is 0.

8. The valve core is a cylinder. A limiting frustum is machined at the bottom end of the valve core 2 cm-3 cm from the end face. The diameter of the limiting frustum is 1 cm-1.5 cm larger than the diameter of the valve core. M sets of parallel throttling grooves are machined 10 cm-13 cm above the limiting frustum. Each set contains two or more throttling grooves spaced 2 cm-2.5 cm apart, where M is a positive integer ≥5. Two valve core guide holes are machined along the valve core axis at the upper end of the cylinder. The two valve core guide holes are connected to the two parallel rows of throttling grooves. The sealing cover is a hollow frustum, the inner diameter of which is 0.02 mm-0.05 mm larger than the outer diameter of the piston rod. The maximum outer diameter of the frustum is the same as the outer diameter of the cylinder, and the minimum outer diameter is the same as the inner diameter of the cylinder. A sealing ring groove for fitting the No. 1 sealing ring is opened inside the cylinder with the larger diameter. The No. 1 sealing ring is placed in the sealing ring groove. The valve sleeve is a hollow circular ring, the diameter of which is 0.02 mm-0.05 mm larger than the outer diameter of the valve core, and its outer diameter is the same as the inner diameter of the piston rod hole. Valve sleeve guide holes and #2 stepped through holes are evenly distributed on the valve sleeve. The valve sleeve guide holes are cylindrical through holes that extend vertically. The larger diameter hole in the #2 stepped through hole is located at the top, where a #2 one-way valve is installed. The #2 one-way valve is normally closed. A sealing ring groove for a #3 sealing ring is machined in the middle of the inner wall of the valve sleeve, and the #3 sealing ring is placed in this sealing ring groove. The upper U-shaped frame is a U-shaped plate, consisting of two parallel #1 side plates and a semi-circular #1 connecting plate. The lower end of the #1 side plate has a circular #3 through hole with the same diameter as the #2 through hole. A rectangular #1 hollow hole is machined in the center of the #1 side plate. A #1 lifting hole, a circular through hole, is located in the center of the circular end face of the #1 connecting plate. The circular end face of the #1 connecting plate faces upwards, and the two #1 side plates are respectively fixed to the lower end face of the #1 connecting plate. The lower U-shaped frame is a U-shaped plate, consisting of two parallel #2 side plates and a semi-circular #1 connecting plate. The system consists of a #1 side plate and a semi-circular #2 connecting plate. The lower end of the #2 side plate has a circular #4 through hole with the same diameter as the #1 through hole. A rectangular #2 hollow hole is machined in the center of the #2 side plate. A #2 lifting hole, a circular through hole, is located in the center of the circular end face of the #2 connecting plate. The circular end face of the #2 connecting plate faces downwards. The two #2 side plates are respectively fixed to the upper end face of the #2 connecting plate. The diameter of the #2 lifting hole is the same as the diameter of the #1 lifting hole. The width of the #2 side plate is 0.2 mm-0.5 mm smaller than the width of the #1 side plate. The width of the #2 connecting plate is also 0.2 mm-0.5 mm smaller than the width of the #1 connecting plate. The length ratio of the #1 side plate to the #2 side plate is 1.

2. The diameter of the #1 pin is the same as the diameter of the #3 through hole, and the diameter of the #2 pin is the same as the diameter of the #4 through hole. The hydraulic rectifier bridge is composed of two heads connected in series with one-way valve branches and two tail-to-tail connected in series with one-way valve branches connected in parallel. The first and second one-way valves connected in series with the heads form the first branch, and the third and fourth one-way valves connected in series with the tails form the second branch. The valve core is machined with a limiting frustum on one side, which is fixed to the bottom end face inside the cylinder body. The cylinder body connector faces downwards. The end face of the lower frustum of the piston rod is flush with and fixed to one end face of the valve sleeve. The piston rod connector of the piston rod faces upwards. The valve sleeve is fitted onto the valve core, and the sealing cap is fitted onto the piston rod to seal the cylinder body. The upper U-shaped bracket and the lower U-shaped bracket are installed at a 90° offset, so that the lower U-shaped bracket is embedded in the upper U-shaped bracket. At the same time, the No. 1 connecting plate faces upwards, and the No. 2 connecting plate faces downwards. With the top facing down, pin #1 passes through two through holes #3 and #2 at the bottom of side plate #1 of the upper U-shaped frame, and pin #2 passes through two through holes #4 and #1 at the bottom of side plate #2 of the lower U-shaped frame, thus fixing pins #1 and #2 to side plate #1 of the upper U-shaped frame and side plate #2 of the lower U-shaped frame, respectively; the lifting wire ropes pass through lifting holes #1 on the upper U-shaped frame and #2 on the lower U-shaped frame, respectively, and are fixedly connected to the upper and lower U-shaped frames. A #3 sealing ring seals the valve core and valve sleeve, forming an energy storage chamber within the piston rod's internal cavity. The upper part of the energy storage chamber is filled with nitrogen, and the lower part with hydraulic oil. A #2 sealing ring seals the piston rod and cylinder body, and a #1 sealing ring seals the piston rod and sealing cap. The upper part of the outer truncated cone of the piston rod, the lower part of the sealing cap, and the interior of the cylinder body form an auxiliary chamber filled with hydraulic oil. The lower part of the truncated cone of the piston rod and the valve sleeve, along with the interior of the cylinder body, form the main chamber, also filled with hydraulic oil. When the #1 check valve opens, hydraulic oil flows from the auxiliary chamber to the main chamber; when the #2 check valve opens, hydraulic oil flows from the main chamber to the energy storage chamber. The auxiliary chamber and main chamber are connected to the upper and lower middle parts of the hydraulic rectifier bridge via hydraulic pipes. The middle parts of the first and second branches are connected to the outlet and inlet of the hydraulic motor via hydraulic pipes. The output shaft of the hydraulic motor is connected to the flywheel.

2. A novel vibration damper for deep well hoisting wire ropes according to claim 1, characterized in that: The throttling groove is a round or triangular or rectangular valve port.

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