CN109665409B - Ultra-deep vertical shaft double-channel large-load friction lifting system and stress fluctuation reducing method - Google Patents

Ultra-deep vertical shaft double-channel large-load friction lifting system and stress fluctuation reducing method Download PDF

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Publication number
CN109665409B
CN109665409B CN201811525385.8A CN201811525385A CN109665409B CN 109665409 B CN109665409 B CN 109665409B CN 201811525385 A CN201811525385 A CN 201811525385A CN 109665409 B CN109665409 B CN 109665409B
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container
counterweight
lifting
rope
steel wire
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CN109665409A (en
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曹国华
王可
朱真才
周公博
花纯利
刘善增
汤裕
贾玉斌
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China University of Mining and Technology CUMT
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China University of Mining and Technology CUMT
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B15/00—Main component parts of mining-hoist winding devices
    • B66B15/02—Rope or cable carriers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B15/00—Main component parts of mining-hoist winding devices
    • B66B15/02—Rope or cable carriers
    • B66B15/04—Friction sheaves; "Koepe" pulleys
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B17/00—Hoistway equipment
    • B66B17/12—Counterpoises
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B19/00—Mining-hoist operation
    • B66B19/02—Installing or exchanging ropes or cables
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B7/00—Other common features of elevators
    • B66B7/06—Arrangements of ropes or cables
    • B66B7/068—Cable weight compensating devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B7/00—Other common features of elevators
    • B66B7/06—Arrangements of ropes or cables
    • B66B7/10—Arrangements of ropes or cables for equalising rope or cable tension

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  • Lift-Guide Devices, And Elevator Ropes And Cables (AREA)
  • Jib Cranes (AREA)

Abstract

A double-channel large-load friction lifting system of an ultra-deep vertical shaft comprises a shaft, wherein even channels are arranged in the shaft and are arranged in parallel to form a front row and a rear row, a friction wheel is shared above each pair of front channels and rear channels, and lifting steel wire ropes on the friction wheels are uniformly divided into a front part and a rear part with the same number; the two sides of the front lifting steel wire rope and the two sides of the rear lifting steel wire rope between the friction wheel and the shaft are respectively wound between the two parallel guide wheels; the two ends of the front hoisting steel wire rope are connected with the front counterweight and the front container respectively, the two ends of the rear hoisting steel wire rope are connected with the rear container and the rear counterweight respectively, the front counterweight and the rear container and the rear counterweight and the front container pass through in a staggered mode in position, and the front counterweight and the lower end of the front container and the lower end of the rear counterweight are connected through the front balancing tail rope and the rear balancing tail rope respectively to form a closed system. The invention can realize the large-load friction lifting of double channels, reduce the stress fluctuation value of a lifting system to a certain extent and improve the ultra-deep lifting under large load.

Description

Ultra-deep vertical shaft double-channel large-load friction lifting system and stress fluctuation reducing method
Technical Field
The invention relates to a large-load lifting system, in particular to a double-channel large-load friction lifting system of an ultra-deep vertical shaft and a method for reducing stress fluctuation, belongs to the technical field of ultra-deep vertical shafts, and can also be applied to lifting systems of ultra-high-load traction mining elevators, high-speed elevators and the like.
Background
At present, an ultra-deep vertical shaft friction lifting system is widely applied to various deep mines, however, for the friction lifting system, great stress fluctuation can be generated due to the influence of the self-weight change of a load and a steel wire rope in the transportation of a large load, the safety production of the mine lifting system is seriously threatened, the limit value of the load which can be lifted by the ultra-deep vertical shaft lifting system in a certain lifting height is limited, and the production efficiency of the mine is influenced.
The existing friction lifting system with the counterweight, such as the lifting systems of the existing mining elevator, the high-speed elevator and the like, only has one container and the counterweight, does not have a method for reducing the fluctuation stress, and simultaneously influences the lifting efficiency.
Disclosure of Invention
In order to overcome the defects in the prior art, the invention provides a double-channel large-load friction lifting system of an ultra-deep vertical shaft and a method for reducing stress fluctuation, which can realize large-load friction lifting of double channels, reduce the stress fluctuation value of the lifting system to a certain extent and improve ultra-deep lifting under large load.
The technical scheme adopted by the invention for solving the technical problems is as follows:
a double-channel large-load friction lifting system of an ultra-deep vertical shaft comprises a shaft, wherein an even number of channels are arranged in the shaft and are arranged in parallel to form a front row and a rear row, a friction wheel is arranged above each pair of front channels and rear channels which are arranged in parallel, and a lifting steel wire rope on each friction wheel is uniformly divided into a front lifting steel wire rope and a rear lifting steel wire rope with the same number; two sides of all front lifting steel wire ropes and two sides of all rear lifting steel wire ropes between the friction wheel and the shaft are respectively wound between the front left guide wheel and the front right guide wheel and between the rear left guide wheel and the rear right guide wheel which are parallel; in the pair of front channel and rear channel, the two ends of all front lifting steel wire ropes are connected with the front counterweight and the front container respectively, the two ends of all rear lifting steel wire ropes are connected with the rear container and the rear counterweight respectively in an order opposite to that of the front lifting steel wire ropes, the front counterweight and the rear container and the rear counterweight and the front container pass through in a staggered mode in position, and the lower ends of the front counterweight and the front container and the lower ends of the rear container and the rear counterweight are connected through the front balance tail rope and the rear balance tail rope respectively to form a closed system.
A method for determining the weight of a counterweight and a balance tail rope for reducing stress fluctuation value of a dual-channel large-load friction hoisting system based on an ultra-deep vertical shaft is characterized in that under the premise of known load, hoisting rope weight and hoisting height, stress fluctuation values of four important sections of a hoisting rope and a rear hoisting rope are calculated according to the calculated weight of the hoisting rope and the calculated stress fluctuation values of four important sections of the hoisting rope, and the stress fluctuation values of the system caused by loading and unloading and rope length change of the hoisting rope in the whole hoisting cycle process are reduced to the maximum extent by changing the weight of the corresponding front counterweight, rear counterweight, front balance tail rope and rear balance tail rope, and the method comprises the following specific steps:
the maximum tension fluctuation value of the section just not wound on the friction wheel above the front container and the rear container is as follows:
(m+mZ+n2ρ2H)g-mZg＝(m+n2ρ2H)g
the maximum tension fluctuation value of the section just bypassing the friction wheel above the front container and the rear container is as follows:
(mV+n1ρ1H)g-mZg＝(mV-mZ+n1ρ1H)g
the maximum tension fluctuation value of the section just bypassing the friction wheel above the front counterweight and the rear counterweight is as follows:
(m+mZ+n1ρ1H)g-mVg＝(m+mZ-mV+n1ρ1H)g
the maximum tension fluctuation value of the section above the front counterweight and the rear counterweight, which is just not wound on the friction wheel, is as follows:
(mV+n2ρ2H)g-mVg＝n2ρ2gH
in order to ensure that the maximum stress fluctuation values of the two sections just bypassing the friction wheel above the front counterweight and the front container and above the rear counterweight and the rear container are the same in the lifting process, namely
(mV-mZ+n1ρ1H)g＝(m+mZ-mV+n1ρ1H)g
The weights of the front counterweight and the rear counterweight need to satisfy the following calculation formula:
mV＝mZ+0.5m
in order to ensure that the section just not winding around the friction wheel above the front container and the rear container is the same as the maximum stress fluctuation value of the section just winding around the friction wheel, namely
(m+n2ρ2H)g＝(mV-mZ+n1ρ1H)g
The weights of the front balance tail rope and the rear balance tail rope need to satisfy the following calculation formula:
Figure BDA0001904317890000031
wherein m isVFor balancing mass, mZIs the container mass, m is the loading mass, n1For lifting the number of wire ropes, n2To balance the number of tail ropes, p1For hoisting the mass per unit length of the wire rope, ρ2In order to balance the mass per unit length of the tail rope, H is the hoisting height.
Compared with the prior art, the dual-channel large-load friction lifting system for the ultra-deep vertical shaft and the stress fluctuation reducing method comprise an even number of channels, the reduction of the stress fluctuation value in the friction lifting system is realized by reasonably setting the weight of the balance weight and reducing the unit rope weight of the balance tail rope, so that the limit value of the load is increased in a certain friction lifting height, the friction lifting height is increased under a certain load, the large-load lifting of the ultra-deep vertical shaft can be adapted, and the service life of the friction lifting system is prolonged.
Drawings
The invention is further illustrated with reference to the following figures and examples.
Fig. 1 is a front view of one embodiment 1 of the present invention.
Fig. 2 is a front view of a front passage position corresponding structure in embodiment 1 of the present invention.
Fig. 3 is a front view of a rear tunnel position correspondence structure in embodiment 1 of the present invention.
Fig. 4 is an enlarged top view of the application of embodiment 1 of the present invention to a two-pass four-hoist rope hoist, in which the guide wheel structure is omitted and partially represented in perspective and section lines.
Fig. 5 is an enlarged top view of an application of embodiment 1 of the present invention as a two-pass six-wire hoist, with the guide wheel structure omitted and partially represented in perspective and cross-sectional views.
Fig. 6 is a front view of another embodiment 2 of the present invention.
Fig. 7 is a front view of a front passage position corresponding structure in embodiment 2 of the present invention.
Fig. 8 is a front view of a rear tunnel position correspondence structure in embodiment 2 of the present invention.
Fig. 9 is an enlarged top view of a two-pass four hoist rope hoist according to example 2 of the present invention, with the guide wheel structure and friction wheels omitted and partially represented by hatching.
Fig. 10 is an enlarged top view of a two-pass six hoist rope hoist according to example 2 of the present invention, with the guide wheel structure and friction wheel omitted and partially represented by hatching.
Fig. 11 is an enlarged top view of an application of embodiment 2 of the present invention as a four-way six-wire hoist, wherein the guide wheel structure and friction wheel are omitted and partially represented by hatching.
In the figure, 110, 210, friction wheels, 121,221, front hoisting ropes, 122, 222, rear hoisting ropes, 131, 231, front left guide wheels, 132, 232, front right guide wheels, 133, 233, rear left guide wheels, 134, 234, rear right guide wheels, 141, 241, front weights, 142, 242, rear weights, 151, 251, front containers, 152, 252, rear containers, 160, 260, shaft, 151, 271, front balance tail ropes, 172, 272 and rear balance tail ropes.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are 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 step based on the embodiments of the present invention, belong to the scope of the present invention.
In embodiment 1 shown in fig. 1 to 5, fig. 1 to 3 are front views showing the structure of the friction lifting system of embodiment 1, in which each of the front container 151 and the rear container 152 is shaped as a hollow cube having a large cross-sectional area ("large" is compared with embodiment 2), and a through hole is opened in the middle thereof for passing the front weight 141 or the rear weight 142 therethrough, and each of the front left guide wheel 131 and the front right guide wheel 132, and the rear left guide wheel 133 and the rear right guide wheel 134 is symmetrical with respect to the vertical center line of the friction wheel 110; the front left guide wheel 131, the front right guide wheel 132, the rear left guide wheel 133 and the rear right guide wheel 134 are respectively arranged on a horizontal plane, and connection points of each hoisting steel wire rope bypassing each guide wheel, the front container, the rear container, the front counterweight and the rear counterweight are uniformly distributed in a vertical plane where gravity center suspension points of the front container, the rear container, the front counterweight and the rear counterweight are located, so that the front container 152, the rear container 152 and the front counterweight 142 can be vertically suspended; the front lifting steel wire rope 121, the front balance tail rope 171, the rear lifting steel wire rope 122 and the rear balance tail rope 172 are respectively arranged in the same vertical plane; the front counterweight 141 and the rear container 152 are at the same horizontal height, the rear counterweight 142 and the front container 151 are at the same horizontal height, so as to solve the problem that the container and the counterweight at the same side of the container may collide during the lifting process, both ends of the front lifting steel wire rope 121 are connected with the upper ends of the front counterweight 141 and the front container 151 respectively by bypassing the friction wheel 110 and the front left and right guide wheels 132, the lower ends of the front counterweight 141 and the front container 151 are connected by a front balance tail rope 171, both ends of the rear lifting steel wire rope 122 are connected with the upper ends of the rear container 152 and the rear counterweight 142 by bypassing the friction wheel 110 and the rear left and right guide wheels 134 respectively, the lower ends of the rear container 152 and the rear counterweight 142 are connected by a rear balance tail rope 172, thereby forming a closed lifting system, the front counterweight 141 and the rear container 152 are at the same horizontal height, the rear counterweight 142 and the front container 151 are at the same horizontal height, thereby ensuring the loading-lifting at one side of, unloading-lowering the other side.
The specific lifting process is as follows:
when the front container 151 descends, the friction wheel 110 rotates counterclockwise, the front lifting wire rope 121 and the rear lifting wire rope 122 are together lowered along the left guide wheel (the front left guide wheel 131 and the rear left guide wheel 233) and raised along the right guide wheel (the front right guide wheel 132 and the rear right guide wheel 134), the front container 151 descends, the front counterweight 141 ascends, and when the two are staggered, the front counterweight 141 ascends through the hollow section of the front container 151; in contrast, the rear container 152 is raised, the rear weight 142 is lowered, and when the two are staggered, the rear weight 142 is lowered through the hollow section of the rear container 152;
when the front container 151 ascends, the friction wheel 110 rotates clockwise, the front lifting wire rope 121 and the rear lifting wire rope 122 ascend along the left guide wheels (the front left guide wheel 131 and the rear left guide wheel 233) together, descend along the right guide wheels (the front right guide wheel 132 and the rear right guide wheel 134), the front container 151 ascends, the front counterweight 141 descends, and when the front container 151 and the rear lifting wire rope are staggered, the front counterweight 141 descends by penetrating through the hollow section of the front container 151; in contrast, the rear container 152 is lowered, the rear weight 142 is raised, and when the two are staggered, the rear weight 142 is raised through the hollow section of the rear container 152.
Fig. 4 and 5 are enlarged views showing the top structure of the friction hoisting system of two passages in the shaft 160 shown in fig. 1, wherein the structure of the guide wheel is omitted, four hoisting cables are used for hoisting in each passage in fig. 4, and six hoisting cables are used for hoisting in each passage in fig. 5, and as can be seen from the figure, the hoisting cables are uniformly divided into a front part and a rear part for realizing that one side can be lifted up and the other side can be lowered down, and as can be seen from fig. 4 and 5, the through holes in the middle of the front container 151 and the rear part are just used for the normal passing of the front counterweight 141 and the rear counterweight 142 at the junction of the two parts.
In another embodiment shown in fig. 6-11, fig. 6-8 are front views of another structure of the friction lifting system of embodiment 2, in which the front weight 241 and the rear weight 242 are both solid cubic weight structures with small cross-sectional area and large height (the smaller and the larger are described below the cross-sectional width and the height), the front container 251 and the rear container 252 are both hollow cubic structures with small cross-sectional area (the smaller is compared with the container of embodiment 1) and no through-hole in the middle, the horizontal positions of the front left guide wheel 231 and the rear right guide wheel 234 contacting the front lifting wire rope 221 and the rear lifting wire rope 222 on the same side of the front container 251 and the rear container 252 correspond to the vertical center lines of the front container 251 and the rear lifting wire rope 222, respectively, and the horizontal positions of the rear left guide wheel 233 and the front right guide wheel 232 contacting the rear lifting wire rope 222 and the front lifting wire rope 221 on the same side of the rear weight 242 and the front weight 241 correspond to the horizontal positions of the rear left guide wheel and the rear guide wheel 233 The positions of the gravity center suspension points respectively correspond to the rear counterweight 242 and the front counterweight 241, the counterweight and the container are staggered at the intersection in the operation process, and the counterweight and the container can be staggered at the intersection in the operation process without collision.
Fig. 9 and 10 are enlarged views showing the top structure of the friction lifting system with two channels in the shaft 260 shown in fig. 6, wherein the guide wheel structure and the friction wheel 210 are omitted, four hoisting cables are used for lifting in each channel of fig. 9, and six hoisting cables are used for lifting in each channel of fig. 10, and it can be seen from the figures that the sections of the front counterweight 241 and the front container 251, and the sections of the rear counterweight 242 and the rear container 252 are relatively staggered, so that the sectional space of the shaft 260 can be effectively utilized.
Fig. 11 is an enlarged view of a top view of the friction lifting system with four channels in the shaft 260 shown in fig. 6, wherein the guide wheel structure and the friction wheel 210 are omitted, and each channel is lifted by using six steel cables, so that the cross-sectional utilization rate of the shaft 260 is increased, and the lifted load limit value can be increased to a certain extent.
In both embodiments, the number of hoisting ropes on the one friction wheel 210 is even, and may range from 2 to 12. The weight of the balance weight and the density of the tail rope are changed to ensure that the fluctuation stress of each section of the hoisting steel wire rope in the whole hoisting circulation process of the system is minimum.
The method for determining the weight of the balance weight and the balance tail rope comprises the following steps:
under the premise of known load, hoisting rope weight and hoisting height, according to the calculated stress fluctuation values of four important sections of the front hoisting ropes 121 and 221 and the rear hoisting ropes 122 and 222, by changing the weights of the corresponding front counterweights 141 and 241, the rear counterweights 142 and 242 and the front balance tail ropes 271 and the rear balance tail ropes 172 and 272, the stress fluctuation value of the system caused by loading and unloading and the change of the rope length of the hoisting ropes in the whole hoisting cycle is reduced to the maximum extent, and the method comprises the following specific steps:
the maximum tension fluctuation value of the cross section just above the front container 151, 251 and the rear container 152, 252 not to be wound on the friction wheel 110, 210 is:
(m+mZ+n2ρ2H)g-mZg＝(m+n2ρ2H)g
the maximum tension fluctuation over the cross-section just around the friction wheel 110, 210 above the front 151, 251, rear 152, 252 containers is:
(mV+n1ρ1H)g-mZg＝(mV-mZ+n1ρ1H)g
the maximum tension fluctuation over the front and rear counterweights 141, 142, 242 just about the cross-section of the friction wheels 110, 210 is:
(m+mZ+n1ρ1H)g-mVg＝(m+mZ-mV+n1ρ1H)g
the maximum tension fluctuation value of the section just above the front counterweight 141, 241 and the rear counterweight and not wound on the friction wheel 110, 210 is as follows:
(mV+n2ρ2H)g-mVg＝n2ρ2gH
to ensure that the maximum stress fluctuation values over the front counterweight 141, 241 and the front container 151, 251, the rear counterweight 142, 242 and the rear container 152, 252 just around the two sections of the friction wheel 110, 210 during lifting are the same, i.e. the maximum stress fluctuation values are the same
(mV-mZ+n1ρ1H)g＝(m+mZ-mV+n1ρ1H)g
It is necessary that the weights of front weights 141, 241 and rear weights 142, 242 satisfy the following calculation formula:
mV＝mZ+0.5m
in order to ensure that the cross section just above the front container 151, 251 and the rear container 152, 252, which does not wrap around the friction wheel 110, 210, is the same as the maximum stress fluctuation value just around the cross section of the friction wheel 110, 210, i.e. (m + n)2ρ2H)g＝(mV-mZ+n1ρ1H)g
The weights of the front balancing tail ropes 171 and 271 and the rear balancing tail ropes 172 and 272 need to satisfy the following calculation formula:
Figure BDA0001904317890000091
wherein m isVFor balancing mass, mZIs the container mass, m is the loading mass, n1For lifting the number of wire ropes, n2To balance the number of tail ropes, p1For hoisting the mass per unit length of the wire rope, ρ2In order to balance the mass per unit length of the tail rope, H is the hoisting height.
The invention realizes the friction lifting of the double channels under large load by arranging the counter weight at the opposite side of the container, simultaneously changing the structure of the container, and changing the weight of the counter weight and the unit rope weight of the balance tail rope, reduces the stress fluctuation value of a lifting system to a certain extent, and improves the ultra-deep lifting under large load. The method has the following advantages:
1) by changing the unit rope weight of the balance weight and the balance tail rope, the stress fluctuation value in the operation process of the lifting system can be reduced to a certain extent, and the service life of the friction lifting system is prolonged.
2) Under the prerequisite that does not increase the well cross-sectional area, can realize the promotion and the transferring of two containers or four containers, increase space utilization, promote work efficiency.
3) Under the condition that the transported load value is constant, the maximum lifting height which can be realized by the friction lifting system can be improved under the condition of ensuring the minimum fluctuating stress according to the relation between the balance rope weight and the balance weight.
The above description is only a preferred embodiment of the present invention, and is not intended to limit the present invention in any way, and all simple modifications and equivalent variations of the above embodiment according to the technical spirit of the present invention are included in the protection scope of the present invention.

Claims (6)

1. A double-channel heavy-load friction lifting system of an ultra-deep vertical shaft comprises a shaft (160, 260), and is characterized in that: an even number of channels are arranged in the shaft (160, 260) and are parallel to form a front row and a rear row, a friction wheel (110, 210) is arranged above each pair of front channels and rear channels which are parallel to each other, and the hoisting steel wire rope on each friction wheel (110, 210) is uniformly divided into a front hoisting steel wire rope (121,221) and a rear hoisting steel wire rope (122, 222) with the same number of front and rear parts; firstly, the two sides of all front hoisting steel ropes (121,221) and the two sides of all rear hoisting steel ropes (122, 222) between the friction wheels (110, 210) and the shaft (160, 260) are respectively and jointly wound between the parallel front left guide wheels (131, 231) and the front right guide wheels (132, 232) and between the rear left guide wheels (133, 233) and the rear right guide wheels (134, 234); in the pair of front channel and rear channel, two ends of all front lifting steel wire ropes (121,221) are respectively connected with a front counterweight (141, 241) and a front container (151, 251) together, two ends of all rear lifting steel wire ropes (122, 222) are respectively connected with a rear container (152, 252) and a rear counterweight (142, 242) together in an order opposite to that of the front lifting steel wire ropes (121,221), the front counterweight (141, 241) and the rear container (152, 252) and the rear counterweight (142, 242) and the front container (151, 251) pass through in a staggered mode in position, and the front counterweight (141, 241) and the lower end of the front container (151, 251), the rear container (152, 252) and the lower end of the rear counterweight (142, 242) are respectively connected through a front balancing tail rope (171, 271) and a rear balancing tail rope (172, 272) to form a closed system; the front container (151, 251) and the rear container (152) are both hollow cubes with larger cross-sectional areas and through holes for the front counterweight (141) or the rear counterweight (142) to pass through in the middle, the front left guide wheel (131), the front right guide wheel (132), the rear left guide wheel (133) and the rear right guide wheel (134) are respectively arranged on a horizontal plane, and the connecting points of each lifting steel wire rope bypassing the guide wheels, the front container (152), the rear container (152) and the front counterweight (142) are uniformly distributed in the vertical plane where the gravity center suspension points of the front container (152), the rear container (152) and the front counterweight (142) are located; the front lifting steel wire rope (121), the front balance tail rope (171), the rear lifting steel wire rope (122) and the rear balance tail rope (272) are respectively arranged in the same vertical plane; the front counterweight (141) and the rear container (152) are at the same level, and the rear counterweight (142) and the front container (151) are at the same level.
2. The dual-channel heavy-load friction lifting system of the ultra-deep vertical shaft as claimed in claim 1, wherein: the front container (251) and the rear container (252) are both hollow cubic structures with larger cross section area and larger height, the front counterweight (241) and the rear counterweight (242) are both solid cubic counterweight body structures with smaller cross section area, and the counterweight and the containers are staggered at the junction in the operation process.
3. The dual-channel heavy-load friction lifting system of the ultra-deep vertical shaft as claimed in claim 2, wherein: horizontal positions, in contact with the front lifting steel wire rope (221) and the rear lifting steel wire rope (222), of the front left guide wheel (231) and the rear right guide wheel (234) which are located above the same side of the front container (251) and the rear container (252) respectively correspond to gravity center suspension points of the front container (251) and the rear container (252), and horizontal positions, in contact with the rear lifting steel wire rope (222) and the front lifting steel wire rope (221), of the rear left guide wheel (233) and the front right guide wheel (232) which are located above the same side of the rear counterweight (242) and the front counterweight (241) respectively correspond to gravity center suspension points of the rear counterweight (242) and the front counterweight (241).
4. The double-channel heavy-load friction lifting system of the ultra-deep vertical shaft according to claim 1 or 2, which is characterized in that: the number of the lifting steel ropes on each friction wheel (110, 210) is even.
5. The dual-channel heavy-load friction lifting system of the ultra-deep vertical shaft as claimed in claim 4, wherein: the number of the hoisting steel wire ropes is 2-12.
6. A method for determining the weight of a counterweight and a balance tail rope for reducing the stress fluctuation value based on the double-channel large-load friction hoisting system of the ultra-deep vertical shaft is characterized by comprising the following steps:
under the premise of known load, hoisting rope weight and hoisting height, according to the calculated stress fluctuation values of the hoisting system caused by loading and unloading and rope length changes of the hoisting rope in the whole hoisting cycle process are reduced to the maximum extent by changing the corresponding front counter weight (141, 241), rear counter weight (142, 242), front balance tail rope (171, 271) and rear balance tail rope (172, 272) according to the calculated stress fluctuation values of the front hoisting rope (121,221), the front container (151, 251) of the rear hoisting rope (122, 222), the section which is just not wound around the friction wheel above the rear container (152, 252), the section which is just wound around the friction wheel above the rear container (152, 251) and the front counter weight (141, 241) and the section which is just wound around the friction wheel above the rear counter weight (142, 242) and the front balance tail rope (171, 271) and the rear balance tail rope (172, 272), the method comprises the following specific steps:
the maximum tension fluctuation value of the section just not winding on the friction wheel (110, 210) above the front container (151, 251) and the rear container (152, 252) is as follows:
(m+mZ+n2ρ2H)g-mZg＝(m+n2ρ2H)g
the maximum tension fluctuation value of the cross section just bypassing the friction wheel (110, 210) above the front container (151, 251) and the rear container (152, 252) is as follows:
(mV+n1ρ1H)g-mZg＝(mV-mZ+n1ρ1H)g
the maximum tension fluctuation value of the cross section just passing around the friction wheel (110, 210) above the front counterweight (141, 241) and the rear counterweight (142, 242) is as follows:
(m+mZ+n1ρ1H)g-mVg＝(m+mZ-mV+n1ρ1H)g
the maximum tension fluctuation value of the section just not wound on the friction wheel (110, 210) above the front counterweight (141, 241) and the rear counterweight (142, 242) is as follows:
(mV+n2ρ2H)g-mVg＝n2ρ2gH
to ensure that the maximum stress fluctuation values of two sections just bypassing the friction wheel (110, 210) above the front counterweight (141, 241) and the front container (151, 251) and the rear counterweight (142, 242) and the rear container (152, 252) are the same during lifting, namely the maximum stress fluctuation values are the same
(mV-mZ+n1ρ1H)g＝(m+mZ-mV+n1ρ1H)g
The weights of the front counterweight (141, 241) and the rear counterweight (142, 242) are required to satisfy the following calculation formula:
mV＝mZ+0.5m
in order to ensure that the section just above the front container (151, 251) and the rear container (152, 252) not winding around the friction wheel (110, 210) is the same as the maximum stress fluctuation value just winding around the section of the friction wheel (110, 210), namely
(m+n2ρ2H)g＝(mV-mZ+n1ρ1H)g
The weights of the front balance tail ropes (171, 271) and the rear balance tail ropes (172, 272) are required to satisfy the following calculation formula:
Figure FDA0002779843650000031
wherein m isVFor balancing mass, mZIs the container mass, m is the loading mass, n1For lifting the number of wire ropes, n2To balance the number of tail ropes, p1For hoisting the mass per unit length of the wire rope, ρ2In order to balance the mass per unit length of the tail rope, H is the hoisting height.
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