CN111252690B - Double drum linkage winding lifting system - Google Patents
Double drum linkage winding lifting system Download PDFInfo
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- CN111252690B CN111252690B CN202010239670.4A CN202010239670A CN111252690B CN 111252690 B CN111252690 B CN 111252690B CN 202010239670 A CN202010239670 A CN 202010239670A CN 111252690 B CN111252690 B CN 111252690B
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/26—Rope, cable, or chain winding mechanisms; Capstans having several drums or barrels
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/02—Driving gear
- B66D1/12—Driving gear incorporating electric motors
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/02—Driving gear
- B66D1/14—Power transmissions between power sources and drums or barrels
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/28—Other constructional details
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/28—Other constructional details
- B66D1/40—Control devices
- B66D1/48—Control devices automatic
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/54—Safety gear
- B66D1/58—Safety gear responsive to excess of load
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control And Safety Of Cranes (AREA)
Abstract
本发明公开了一种双滚筒联动缠绕式提升系统，包括第一提升滚筒和第二提升滚筒，所述第一提升滚筒和所述第二提升滚筒通过外圆周的啮合结构啮合联动或通过联动中间件联动；所述第一提升滚筒缠绕有第一提升绳，所述第二提升滚筒缠绕有第二提升绳，所述第一提升绳和第二提升绳相互不连接。本发明的双滚筒联动缠绕式提升系统，能提高超深井提升系统中的能效比。
The present invention discloses a double-drum linkage winding type hoisting system, comprising a first hoisting drum and a second hoisting drum, wherein the first hoisting drum and the second hoisting drum are meshed and linked through an outer circumferential meshing structure or through a linkage intermediate piece; the first hoisting drum is wound with a first hoisting rope, the second hoisting drum is wound with a second hoisting rope, and the first hoisting rope and the second hoisting rope are not connected to each other. The double-drum linkage winding type hoisting system of the present invention can improve the energy efficiency ratio in the ultra-deep well hoisting system.
Description
Technical Field
The invention relates to the field of mine equipment, in particular to a double-roller linkage winding type lifting system.
Background
There are two types of existing lifting systems, one is of the winding type and the other is of the friction type. For winding, in ultra-deep wells with a depth of more than 1200m, as the well depth increases, the proportion of the weight of the lifting rope in the lifting load increases rapidly, and the energy efficiency ratio of the lifting system is lower when the effective load of the lifting system is smaller. For friction type, the tail rope must be used, the tail rope is longer when the depth is deeper, the self weight of the tail rope is larger, when the mine depth is more than 1000m, the proportion of the self weight of the lifting rope in the lifting load is increased sharply, the torque output by the roller is almost used for bearing the weight of the tail rope, the effective load of lifting is reduced sharply, and the efficiency ratio is very low. Therefore, the existing lifting system cannot solve the problem of low energy efficiency ratio in the ultra-deep well lifting system.
Disclosure of Invention
In view of the foregoing, it is desirable to provide a dual-roller linkage wrap-around lifting system that can improve the energy efficiency ratio in ultra-deep well lifting systems.
In order to achieve the above object, the technical solution of the embodiment of the present invention is as follows:
the double-roller linkage winding type lifting system comprises a first lifting roller and a second lifting roller, wherein the first lifting roller and the second lifting roller are in meshing linkage through a meshing structure of the outer circumference or are in linkage through a linkage intermediate piece, the first lifting roller is wound with a first lifting rope, the second lifting roller is wound with a second lifting rope, and the first lifting rope and the second lifting rope are not connected with each other.
According to the scheme, the two axial ends of the first lifting roller and the second lifting roller are aligned and are linked through the linkage intermediate piece, the linkage intermediate piece is movably arranged at the linkage position between the first lifting roller and the second lifting roller, and when the linkage intermediate piece moves out of the linkage position, the first lifting roller and the second lifting roller are separated from linkage.
In the scheme, the linkage intermediate piece comprises a gear set, the gear set consists of one or more cylindrical gears, teeth meshed with the cylindrical gears in the gear set are arranged on the circumference of at least one end of the first lifting roller, and teeth meshed with the cylindrical gears in the gear set are arranged on the circumference of at least one end of the second lifting roller.
In the above scheme, the gear set at least comprises two mutually meshed cylindrical gears at one ends of the first lifting roller and the second lifting roller, one opposite sides of the two cylindrical gears are mutually meshed, and the other sides of the two cylindrical gears are respectively meshed with the first lifting roller and the second lifting roller.
In the scheme, the circumferences of the two ends of the first lifting roller are respectively provided with teeth meshed with the cylindrical gears in the gear sets, the circumferences of the two ends of the second lifting roller are respectively provided with teeth meshed with the cylindrical gears in the gear sets, the gear sets comprise two mutually meshed cylindrical gears at the two ends of the first lifting roller and the second lifting roller, one side of the two same ends, opposite to the cylindrical gears, is mutually meshed, and the other side of the same ends is respectively meshed with the first lifting roller and the second lifting roller.
In the above scheme, the first lifting roller and the second lifting roller both comprise an outer rotor permanent magnet motor, and the outer shell of the rotor of the outer rotor permanent magnet motor is the roller of the first lifting roller or the second lifting roller.
In the above scheme, the system further comprises a power supply device capable of respectively controlling the outer rotor permanent magnet motor of the first lifting roller and the outer rotor permanent magnet motor of the second lifting roller, and the power supply device is respectively connected with the outer rotor permanent magnet motor of the first lifting roller and the outer rotor permanent magnet motor of the second lifting roller.
In the scheme, the system further comprises a control device for controlling the operation of the system and a position monitoring device for monitoring the position of the lifting container, wherein the control device is arranged in a ground machine room, the position monitoring device is arranged on a derrick, and the control device is electrically connected with the power supply device and the position monitoring device.
In the above scheme, the system further comprises an overwinding protection device, and the overwinding protection device is installed on the derrick and is electrically connected with the control device.
In the above aspect, the system further comprises a braking device mounted on one side of the first lifting drum and/or the second lifting drum.
The double-roller linkage winding type lifting system comprises a first lifting roller and a second lifting roller, wherein the first lifting roller and the second lifting roller are in meshed linkage through a meshed structure of the outer circumference or are in linkage through a linkage middleware, a first lifting rope is wound on the first lifting roller, a second lifting rope is wound on the second lifting roller, the first lifting rope and the second lifting rope are not connected with each other, and the two lifting rollers are in linkage, so that the stress directions of the two lifting rollers are opposite, the total weight of the two lifting containers and the dead weight of most lifting ropes can be offset, and the energy efficiency ratio in the ultra-deep well lifting system is improved.
Other beneficial effects of embodiments of the present invention will be further described in the detailed description with reference to the specific technical solutions.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings that are required to be used in the description of the embodiments will be briefly described below. It is to be understood that the drawings described below are only a few of the embodiments of the present invention and that other drawings may be made from these drawings by one of ordinary skill in the art without the benefit of the present inventive effort.
FIG. 1 is a schematic diagram of an ultra-deep well double-roller linkage winding type lifting system provided by an embodiment of the invention;
Fig. 2 is a schematic structural diagram of an ultra-deep well double-roller linkage winding type lifting system provided by an embodiment of the invention;
Fig. 3 is a schematic diagram of a linkage intermediate piece in an ultra-deep well double-roller linkage winding type lifting system according to an embodiment of the present invention;
fig. 4 is a schematic diagram of load comparison between an ultra-deep well double-roller linkage winding type lifting system and a conventional non-linkage winding type lifting system according to an embodiment of the present invention.
Detailed Description
The embodiment of the invention provides a double-roller linkage winding type lifting system, which comprises a first lifting roller and a second lifting roller, wherein the first lifting roller and the second lifting roller are in meshing linkage through a meshing structure of the outer circumference or are in linkage through a linkage intermediate piece, the first lifting roller is wound with a first lifting rope, the second lifting roller is wound with a second lifting rope, and the first lifting rope and the second lifting rope are not connected with each other.
The lifting rollers are winding rollers, and the linkage refers to rotary linkage, namely that one lifting roller rotates and the other lifting roller synchronously rotates. For simplicity of description, the first and second lifting drums are collectively referred to as lifting drums.
According to the double-roller linkage winding type lifting system, the two lifting rollers are linked, and the stress directions of the two lifting rollers are opposite, so that the weight of the two lifting containers and the dead weight of most lifting ropes can be offset, and the energy efficiency ratio in the ultra-deep well lifting system is improved.
In other embodiments of the present invention, the first lifting roller and the second lifting roller are aligned at both axial ends and are linked by a linking intermediate member movably mounted in a linking position between the first lifting roller and the second lifting roller, and the first lifting roller and the second lifting roller are out of the linkage when the linking intermediate member moves out of the linking position. Through the linkage of the linkage middleware, the beneficial effects in two aspects are:
The first lifting roller and the second lifting roller can be conveniently released from linkage, namely, when the linkage intermediate piece moves out of the linkage position, the linkage of the first lifting roller and the second lifting roller can be released, so that the position relation of lifting containers corresponding to the two lifting rollers can be conveniently adjusted, namely, when the positions of unloading points or loading points are not corresponding, the rope adjustment can be quickly and conveniently realized, and the method is a better implementation mode.
Secondly, the quantity of the linkage intermediate pieces can be adjusted, so that the rotation direction of the lifting roller is controlled, and the method is a better implementation mode. Since the direction of rotation of the lifting drums needs to be adjusted depending on the direction in which the lifting cords are led out from the lifting drums, for example, see fig. 1, the number of linkage middleware is suitable if the lifting cords of one of the lifting drums are led out from below, i.e. one less linkage middleware or one more linkage middleware needs to be added.
In other embodiments of the invention, the linkage intermediate comprises a gear set consisting of one or more spur gears, the first lifting roller being provided with teeth on at least one of its ends that mesh with the spur gears of the gear set, and the second lifting roller being provided with teeth on at least one of its ends that mesh with the spur gears of the gear set. The gears are rigidly linked, so that slipping and the like are avoided, the linear speed of the linkage is more uniform, the position of the lifting container does not need to be adjusted frequently, and the gear is a better implementation mode.
In other embodiments of the invention, the gear set includes two intermeshing cylindrical gears at least at one end of the first and second lifting drums, the two cylindrical gears intermeshing on opposite sides, the other side being in engagement with the first and second lifting drums, respectively. The two cylindrical gears enable the rotation directions of the first lifting roller and the second lifting roller to be opposite, and meet the requirements of a floor winding type lifting system, so that the floor winding type lifting system is a better implementation mode.
In other embodiments of the invention, the first lifting roller is provided with teeth on the circumference of both ends thereof which mesh with cylindrical gears in the gear set, the second lifting roller is provided with teeth on the circumference of both ends thereof which mesh with cylindrical gears in the gear set, the gear set comprises two mutually meshed cylindrical gears on both ends of the first lifting roller and the second lifting roller, one side of the two same ends opposite to the cylindrical gears is mutually meshed, and the other side is respectively meshed with the first lifting roller and the second lifting roller. That is, the gear set has four cylindrical gears in total, the four cylindrical gears are respectively fixed on two shafts, and the two gears of the same shaft are respectively arranged at two ends of the lifting roller, so that the teeth at two ends of the lifting roller and the gear set are meshed more stably, the received meshing reaction force is smaller, the service lives of the teeth of the lifting roller and the gear set are prolonged, and the gear set is a better implementation mode.
In other embodiments of the present invention, the first lifting roller and the second lifting roller each comprise an outer rotor permanent magnet motor, and the outer shell of the rotor of the outer rotor permanent magnet motor is the roller of the first lifting roller or the second lifting roller.
The outer rotor permanent magnet motor has the beneficial effects of ultralow-frequency starting, low-speed high-torque running and the like, and the rotor is also a roller, so that more transmission parts are not needed, starting power is further reduced, and the outer rotor permanent magnet motor is a better implementation mode.
In other embodiments of the present invention, the system further comprises a power supply device capable of controlling the outer rotor permanent magnet motor of the first lifting drum and the outer rotor permanent magnet motor of the second lifting drum, respectively, the power supply device being electrically connected with the outer rotor permanent magnet motor of the first lifting drum and the outer rotor permanent magnet motor of the second lifting drum, respectively.
Therefore, the lifting system can be controlled to select three working states according to different conditions by switching the power supply device, namely 1) only the first lifting roller actively rotates, the second lifting roller actively rotates in a linkage manner, 2) only the second lifting roller actively rotates, the first lifting roller actively rotates in a linkage manner, and 3) the first lifting roller and the second lifting roller actively rotate and are mutually linked. Therefore, the power can be adjusted according to the load condition, the energy is saved, meanwhile, the continuous working time of the driving device is shortened, and the service life is longer.
In other embodiments of the invention, the system further comprises a control device for controlling the operation of the system and a position monitoring device for monitoring the position of the lifting container, wherein the control device is arranged on a ground machine room, the position monitoring device is arranged on a derrick, and the control device is electrically connected with the power supply device and the position monitoring device. Therefore, the control device can control the on-off of the power supply device according to the position of the position monitoring device, and further control the operation of the lifting roller, so that the lifting roller is a better implementation mode.
In other embodiments of the invention, the system further comprises an overwinding protection device mounted on the derrick and electrically connected to the control device. In this way, in the lifting process, the lifting container can be prevented from going upward after reaching the wellhead due to inertia of the lifting container, and facilities such as a derrick are damaged, so that the lifting container is a better implementation mode.
In other embodiments of the invention, the system further comprises a brake device mounted to one side of the first lifting drum and/or the second lifting drum. In this way, during lifting, in addition to the safety braking at the loading or unloading point each time under normal conditions, if there is an accident due to a fault or the like, the system can be braked by the braking device, and the operation of the system is safely stopped, which is a better embodiment. The brake device is mounted on one side of the first lifting drum and/or the second lifting drum, which means that the brake device can be mounted on one side of both lifting drums or on one side of only any lifting drum, because of the linkage.
The invention will be further described in detail with reference to the drawings and the specific examples. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the invention. Also, the embodiments described below are only some, but not all, embodiments of the present invention. All other embodiments, which can be obtained by a person skilled in the art, without any inventive effort, are within the scope of protection of the present invention.
The embodiment provides an ultra-deep well double-roller linkage winding type lifting system, which can be understood that mines with other depths can be used.
As shown in fig. 1 and 2, the system includes a first lifting roller 10, a second lifting roller 20, a linkage intermediate, a first lifting rope 101, a second lifting rope 201, a power supply device 40, a control device 50, a position monitoring device, an overwinding protection device 70, and a braking device 80.
The first lifting roller 10 and the second lifting roller 20 are linked through a linkage intermediate piece, the first lifting roller 10 is wound with a first lifting rope 101, the second lifting roller 20 is wound with a second lifting rope 201, and the first lifting rope 101 and the second lifting rope 201 are not connected with each other. Lifting containers 102 are respectively hung below the first lifting rope 101 and the second lifting rope 201, and the first lifting roller and the second lifting roller are respectively arranged on the roller base 105
The linkage intermediate piece is movably arranged at a linkage position between the first lifting roller 10 and the second lifting roller 20, and when the linkage intermediate piece moves out of the linkage position, the first lifting roller 10 and the second lifting roller 20 are out of linkage.
Specifically, referring to fig. 3, the linkage intermediate includes a linkage base 301 and a cylindrical gear 302, the linkage base 301 is mounted on a guide rail 303, a hydraulic cylinder 304 is disposed on the outer side of the guide rail 303, and a piston rod of the hydraulic cylinder 304 is connected to the linkage base 301, that is, through the hydraulic cylinder 304, translation of the linkage intermediate can be achieved, so as to release linkage of the first lifting drum 10 and the second lifting drum 20.
The linkage intermediate piece comprises four cylindrical gears 302, the four cylindrical gears 302 are respectively arranged on two shafts of the linkage base 301, two cylindrical gears on the same shaft are respectively arranged at two ends of the lifting roller, and teeth meshed with the cylindrical gears are arranged on circumferences of two ends of the first lifting roller 10 and the second lifting roller 20.
The first lifting roller 10 and the second lifting roller 20 each comprise an outer rotor permanent magnet motor, and the outer shell of the rotor of the outer rotor permanent magnet motor is the roller of the first lifting roller or the second lifting roller.
The system further comprises a power supply device 40 capable of respectively controlling the outer rotor permanent magnet motor of the first lifting roller 10 and the outer rotor permanent magnet motor of the second lifting roller 20, wherein the power supply device 40 is respectively electrically connected with the outer rotor permanent magnet motor of the first lifting roller 10 and the outer rotor permanent magnet motor of the second lifting roller 20. Specifically, the power supply device 40 is electrically connected to the outer rotor permanent magnet motor through an electric wire 401.
The system further comprises a control device 50 for controlling the operation of the system and a position monitoring device for monitoring the position of the lifting container, wherein the control device 50 is arranged in a ground machine room, the position monitoring device is arranged on a derrick 60, and the control device 50 is electrically connected with the power supply device 40 and the position monitoring device. In particular, the position monitoring device may comprise sensors (not shown in the figures), which may be mounted one in each of the loading and unloading positions, or may be mounted elsewhere as desired.
Wherein the system further comprises an overwinding protection device 70, and the overwinding protection device 70 is arranged on the derrick 60 and is electrically connected with the control device 50. The over-wrap protection device 70 may be automatically activated if the lifting container exceeds a preset depth due to inertia or the like.
Wherein the system further comprises a braking device 80, said braking device 80 being mounted to one side of said first lifting drum 10 and said second lifting drum 20. In particular, the braking device 80 may cooperate with the position monitoring device. For example, when the lifting container reaches the loading position or the unloading position, the sensor will send a signal back to the control device 50, the control device 50 commanding the braking device 80 to act.
Specifically, the rollers of the two lifting rollers are provided with two winding areas, each winding area winds one lifting rope, namely, the first lifting rope 101 comprises two lifting ropes which are arranged in parallel, one end of each lifting rope is wound on the first lifting roller 10, the other end of each lifting rope winds around the head sheave 103 and then is connected to the lifting container, and finally, the lifting ropes are connected to the top of the same lifting container. Compared with single rope connection, the two lifting ropes can effectively reduce the maximum static tension born by the lifting ropes in deep well lifting, and the diameter of the lifting ropes and the diameter of the lifting roller can be reduced.
Similarly, the second lifting rope 201 also includes two lifting ropes, where the two lifting ropes are also arranged in parallel, one end of the two lifting ropes is wound on the second lifting drum 20, the other end of the two lifting ropes is connected to the lifting container after bypassing the head sheave 203, and the direction of rope winding is the same as the direction of rope winding of the first lifting rope 101 on the first lifting drum 10. More specifically, during operation, the second lifting drum 20 is electrified, the first lifting drum 10 is not electrified, and when the second lifting drum 20 rotates, torque is transmitted to the first lifting drum 10 through the linkage intermediate piece, because the two lifting drums transmit torque through the linkage intermediate piece, synchronous linkage between the two lifting drums is realized very conveniently, and when the first lifting rope 101 is released, the second lifting rope 201 is retracted, so that two lifting containers can be simultaneously in a well, namely one loading and one unloading, and the working efficiency of the ultra-deep well lifting system can be improved.
More importantly, in the lifting process, the two lifting rollers are connected through the linkage middleware, the rotation directions of the two lifting rollers are opposite, the rope winding directions are the same, the dead weights of the lifting containers and part of lifting ropes respectively wound on the two lifting rollers can be mutually offset according to the principle that the anticlockwise torque and the clockwise torque can be mutually offset, the load born by the lifting rollers is greatly reduced, the power consumption of a lifting system in each cycle process is almost completely converted into the lifted effective load, and the energy-saving effect is very remarkable.
It can be appreciated that in the above working process, the first lifting roller 10 is electrified, and the second lifting roller 20 is not electrified, so that the same energy saving effect is obtained.
In particular, the suspension device shown in fig. 2 is mounted on the lifting vessel, making the lifting vessel more balanced during lifting.
For a better understanding of the above-described situation of counteracting the dead weight of the lifting vessel and the majority of the lifting rope by linking the two lifting drums, reference is made to fig. 4, which illustrates that the lifting vessel has a mass of m=40t, the lifting material has a mass of m1=40t, the lifting rope has a mass per unit length of ρ=10kg/m, the lifting maximum height is l=1500m, and the gravitational acceleration g is 9.8m/s 2, for a complete lowering and lifting time period of 2T. When the lifting rollers work independently and are not linked through the linkage middleware, the lifting load of the lifter is minimum (m+m1) g, and the lifting load is maximum (m+m1) g+2ρgL; when the two lifting rollers are linked by adopting the linkage middleware, the mass of the two lifting containers is balanced, and the lifting load is m1g at the minimum and m1g+2ρgL at the maximum in the running process. The calculation result shows that when the linkage is not performed, the minimum load born by the single lifting roller is 784kN, when the linkage middleware is linked, the maximum load born by the whole lifting system is 686kN, namely, when the linkage is performed, the maximum load born by the whole system is even smaller than the minimum lifting load born by the single lifting roller when the linkage is not performed.
Further, when the ultra-deep well double-roller linkage winding type lifting system works, two working states can exist, one of the two lifting rollers actively rotates, the other lifting roller is in linkage rotation, namely, one lifting roller is electrified, the other lifting roller is not electrified, but is in a standby state, and the working state can be entered at any time, or the lifting roller is used for a main purpose and a standby purpose. The other state is that the two lifting rollers are all actively rotated, namely the two lifting rollers are all electrified, namely the two lifting rollers are all used mainly, and the two working states can be switched at any time. If the lifting roller which is being electrified fails, the power supply of the lifting roller can be cut off, the lifting roller is converted into a hot standby, and the lifting roller which is connected with the other hot standby generates torque, so that the lifting roller is converted into a main use. Therefore, the lifting system is ensured not to stop working due to the failure of one of the lifting rollers, so that the working efficiency of the lifting system is higher.
Here, the hot standby is a technical term corresponding to the cold standby, and refers to the operation of the hot standby together with the target equipment, when the target equipment fails or stops, the hot standby immediately bears the working task of the failed equipment, and the cold standby refers to the operation state that the cold standby equipment starts to have a stop waiting state to enter a starting operation state and bears the working task of the failed equipment after the target equipment fails or stops.
Further, after the two lifting drums are operated for a long time, the positions of the two lifting containers may not be matched, for example, when one lifting container reaches a loading point, the other lifting container may not reach an unloading point, and the two lifting containers can be independently rope by adjusting the position of the linkage middleware, so that the lifting machine is braked by the braking device, and the operation of the lifting machine is stopped. The hydraulic station 90 supplies oil to the hydraulic cylinder, and pushes the piston rod to move the supporting seat on the guide rail, so that the linkage intermediate piece is driven to be separated from engagement with the lifting roller. The two lifting drums are then activated again to adjust the respective lifting containers to the designated positions. Finally, the linkage intermediate piece is pushed to return to the previous linkage position again by the hydraulic cylinder. Thus, the rope adjusting of the two lifting rollers is conveniently and rapidly realized.
According to the ultra-deep well double-roller linkage winding type lifting system, as the lifting roller is driven by the permanent magnet motor, low-frequency stable starting of the lifting system can be realized, and during starting, the lifting machine is high in torque, low in power and stable in torque, so that stable and reliable starting of the lifting machine under heavy load is ensured, the problem that the asynchronous motor is low in torque during starting and depends on overload starting is solved, the phenomenon that a high-power motor starting method is frequently selected during starting of the asynchronous motor is avoided, and the phenomenon of 'large horse-drawing trolley' is avoided.
For better understanding, for example, assume that a mine lifting height is 1200m, lifting containers are connected by two lifting ropes, the unit mass of the lifting ropes is 6.8kg/m, the lifting speed is 3m/s, the mass of the lifting containers is 30t, the diameter of a roller is 5m, and the power required for starting by adopting the ultra-deep well double-roller linkage winding type lifting system and the common non-linkage asynchronous motor lifting system in the embodiment of the invention is calculated respectively when the lifting materials are 10t,20t,30t and 40t respectively, and the rotating speed of the asynchronous motor is 348r/min.
Starting power of the non-linkage asynchronous motor:
wherein c is an asynchronous motor current influencing factor, the value is 2, ne is an asynchronous motor rotating speed, md is a motor dragging torque, i is a speed reducer transmission ratio, D is a reel diameter, F is a maximum static tension of a lifting rope end, eta is transmission efficiency, the value of the coefficient in the formula is 0.92, and the value of the coefficient in the formula can be checked through a standard in the aspect of motor design.
Starting power of ultra-deep well double-roller linkage winding type lifting system:
Wherein c is a factor 1.6 of low-frequency starting current of the permanent magnet motor, k is a margin coefficient 1.1 of the motor, eta is transmission efficiency, 1;V is lifting speed of the permanent magnet motor, rho is an influence coefficient of heating and the like during acceleration and deceleration of the motor, 1 is taken, and the value of the coefficient in the formula can be checked through a standard in the aspect of motor design.
The starting power of the ultra-deep well double-roller linkage winding type lifting system is calculated by formulas (1) and (2), and compared with the starting power, the data in the following table 1 are obtained, so that the starting power of the ultra-deep well double-roller linkage winding type lifting system is smaller, and the starting is smoother. Specifically, the lifting rope is a steel wire rope.
Further, the whole lifting process can be monitored in the control device 50, and the control device 50 is connected with the power supply device 40, the hydraulic station 90 and the upper computer 501. The control device 50 is provided with the functions of monitoring and recording the working state and running real-time data of the whole lifting system, generating, storing and printing a system report and configuring a power supply system. The configuration comprises a high-voltage power distribution system, a low-voltage power distribution system and the like, wherein the control device 50 is provided with a monitor which can display the state of a gate system and a shaft switch, the rotation speed of a roller is improved, the position of a container is improved, the current of a motor is improved, a dynamic curve is improved and the like.
Further, a frequency conversion component is arranged beside the power supply device 40, when the motor is started, the frequency is reduced, and the motor is started at a low speed, so that the starting power of the ultra-deep well double-roller linkage winding type lifting system is much smaller than that of a lifting system of a common asynchronous motor.
The hydraulic station 90 is configured to provide hydraulic power to the hydraulic cylinder 304.
In describing embodiments of the present invention, unless otherwise indicated and limited thereto, the term "coupled" should be construed broadly, for example, as electrical connection, communication between two elements, direct connection, or indirect connection via an intermediary, and the specific meaning of the term will be understood by those skilled in the art based on the specific circumstances.
The term "first\second\third" in the embodiments of the present invention is merely to distinguish similar objects, and does not represent a specific order for the objects, it being understood that the "first\second\third" may interchange a specific order or sequence, where allowed.
It should be appreciated that reference throughout this specification to "one embodiment" or "some embodiments" means that a particular feature, structure or characteristic described in connection with the embodiment is included in at least one embodiment of the present invention. Thus, the appearances of the phrases "in one embodiment" or "in some embodiments" in various places throughout this specification are not necessarily all referring to the same embodiment. Furthermore, the particular features, structures, or characteristics may be combined in any suitable manner in one or more embodiments. It should be understood that, in various embodiments of the present invention, the sequence numbers of the foregoing processes do not mean the order of execution, and the order of execution of the processes should be determined by the functions and internal logic thereof, and should not constitute any limitation on the implementation process of the embodiments of the present invention. The foregoing embodiment numbers of the present invention are merely for the purpose of description, and do not represent the advantages or disadvantages of the embodiments.
The above description is not intended to limit the scope of the invention, but is intended to cover any modifications, equivalents, and improvements within the spirit and principles of the invention.
Claims (8)
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010239670.4A CN111252690B (en) | 2020-03-30 | 2020-03-30 | Double drum linkage winding lifting system |
| AU2020202801A AU2020202801B1 (en) | 2020-03-30 | 2020-04-28 | Double-drum linkage winding type hoisting system with permanent magnet outer rotor drive |
| US16/874,744 US11299378B2 (en) | 2020-03-30 | 2020-05-15 | Double-drum intermediate gear linkage winding type hoisting system |
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| JP2003136669A (en) * | 2001-11-02 | 2003-05-14 | Mitsubishi Heavy Ind Ltd | Apparatus for driving cylinder of offset perfecting press |
| CN106904517A (en) * | 2017-04-06 | 2017-06-30 | 中国矿业大学 | A kind of extra deep shaft elevator and method for improving |
| CN212475924U (en) * | 2020-03-30 | 2021-02-05 | 太原理工大学 | Double drum linkage winding lifting system |
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| AT194104B (en) * | 1956-02-10 | 1957-12-27 | Rudolf Gantner | Double drum winch |
| CN204490392U (en) * | 2014-12-26 | 2015-07-22 | 河南省三力机械制造有限公司 | A kind of driving device and use winch and the long-spiral drilling machine of this device |
| DE202015006083U1 (en) * | 2015-07-03 | 2016-10-06 | Liebherr-Components Biberach Gmbh | Hubwindenanordnung |
| CN106927347B (en) * | 2017-04-06 | 2019-11-05 | 中国矿业大学 | A kind of depth vertical is restricted winding hoisting machine and winding method more |
| CN108017002B (en) * | 2017-12-30 | 2019-11-12 | 永嘉俊腾机械科技有限公司 | A kind of anti-disorder cable swing hoist engine |
| CN209065320U (en) * | 2018-11-12 | 2019-07-05 | 安徽甜歌智能家居科技有限公司 | A kind of clothes airing machine winder |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP2003136669A (en) * | 2001-11-02 | 2003-05-14 | Mitsubishi Heavy Ind Ltd | Apparatus for driving cylinder of offset perfecting press |
| CN106904517A (en) * | 2017-04-06 | 2017-06-30 | 中国矿业大学 | A kind of extra deep shaft elevator and method for improving |
| CN212475924U (en) * | 2020-03-30 | 2021-02-05 | 太原理工大学 | Double drum linkage winding lifting system |
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