CA2973615C - A method of controlling transversal resonance in a catenary, a hoist drum control system and a mine drum hoist system - Google Patents
A method of controlling transversal resonance in a catenary, a hoist drum control system and a mine drum hoist system Download PDFInfo
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- CA2973615C CA2973615C CA2973615A CA2973615A CA2973615C CA 2973615 C CA2973615 C CA 2973615C CA 2973615 A CA2973615 A CA 2973615A CA 2973615 A CA2973615 A CA 2973615A CA 2973615 C CA2973615 C CA 2973615C
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- 238000000034 method Methods 0.000 title claims abstract description 31
- 238000004590 computer program Methods 0.000 claims abstract description 3
- 238000005259 measurement Methods 0.000 claims description 49
- 241001669573 Galeorhinus galeus Species 0.000 claims 1
- 230000010355 oscillation Effects 0.000 description 5
- 229910052500 inorganic mineral Inorganic materials 0.000 description 2
- 239000011707 mineral Substances 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- FWZTTZUKDVJDCM-CEJAUHOTSA-M disodium;(2r,3r,4s,5s,6r)-2-[(2s,3s,4s,5r)-3,4-dihydroxy-2,5-bis(hydroxymethyl)oxolan-2-yl]oxy-6-(hydroxymethyl)oxane-3,4,5-triol;iron(3+);oxygen(2-);hydroxide;trihydrate Chemical compound O.O.O.[OH-].[O-2].[O-2].[O-2].[O-2].[O-2].[O-2].[O-2].[O-2].[Na+].[Na+].[Fe+3].[Fe+3].[Fe+3].[Fe+3].[Fe+3].O[C@H]1[C@H](O)[C@@H](CO)O[C@@]1(CO)O[C@@H]1[C@H](O)[C@@H](O)[C@H](O)[C@@H](CO)O1 FWZTTZUKDVJDCM-CEJAUHOTSA-M 0.000 description 1
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
- B66B19/00—Mining-hoist operation
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
- B66B1/00—Control systems of elevators in general
- B66B1/24—Control systems with regulation, i.e. with retroactive action, for influencing travelling speed, acceleration, or deceleration
- B66B1/28—Control systems with regulation, i.e. with retroactive action, for influencing travelling speed, acceleration, or deceleration electrical
- B66B1/30—Control systems with regulation, i.e. with retroactive action, for influencing travelling speed, acceleration, or deceleration electrical effective on driving gear, e.g. acting on power electronics, on inverter or rectifier controlled motor
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
- B66B15/00—Main component parts of mining-hoist winding devices
-
- 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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- Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Mechanical Engineering (AREA)
- Control And Safety Of Cranes (AREA)
Abstract
The present disclosure relates to a method of controlling transversal resonance in a catenary of a mine drum hoist system (1) comprising a hoist drum (5) having Lebus grooves, a head sheave (7), a rope (9) having a catenary (9a) extending between the hoist drum (5) and the head sheave (7) and a vertical rope portion (9b), and a conveyance (11) attached to the vertical rope portion (9b). The method comprises a) determining a current payload of the conveyance (11), b) obtaining a hoist speed of the hoist drum (5), corresponding to a first speed of the conveyance (11), c) determining a transversal resonance position along the vertical rope portion (9b) at which transversal resonance is generated in the catenary (9a) when reached by the conveyance (11) with the current payload and first speed, wherein the transversal resonance position is determined based on the current payload and on the hoist speed, and d) reducing the first speed of the conveyance in a speed reduction zone which includes the transversal resonance position. This disclosure also relates to a computer program, a hoist drum control system (3), and a mine drum hoist system (1).
Description
A METHOD OF CONTROLLING TRANSVERSAL RESONANCE IN A
CATENARY, A HOIST DRUM CONTROL SYSTEM AND A MINE
DRUM HOIST SYSTEM
TECHNICAL FIELD
The present disclosure generally relates to mine drum hoist systems. In particular, it relates to control of a hoist drum of a mine drum hoist system.
BACKGROUND
Hoist drums which coil the rope in more than one layer normally have Lebus grooves in which the rope is laid. The grooves are parallel except in the cross-over sections in which the groove moves the rope in the axial direction of the drum a distance which is equal to half the rope diameter, to the next parallel grove. There are two cross-over sections on the circumference of the drum surface which means that after a full revolution the rope has been moved by the Lebus groove one rope diameter. Normally the cross-over sections are diametrical. This arrangement is called symmetric Lebus.
The drum is normally mounted near the ground surface. The rope runs from the drum to a head sheave in the head frame above the mine shaft. The rope angle between the drum and the head sheave is normally in the order of 45 degrees. After passing over the head sheave the rope runs vertically in the mine shaft. The rope end is connected to a conveyance for transport of personnel, mineral or equipment. The part of the rope that is between the hoist drum and the head sheave is called catenary.
The cross-over section pushes the rope over in a short time creating a near rectangular pulse-shaped "kick" on the rope in a direction perpendicular to the rope axis, also called transversal kick. The pulse wave can be converted to a fundamental sine wave with harmonics by means of Fourier transformation. If the kick is repeated, i.e. excited with a frequency that corresponds to the natural or resonance frequency of the catenary the amplitude of the transversal catenary oscillations will build up to large unacceptable values. High amplitudes will severely affect the rope life.
CATENARY, A HOIST DRUM CONTROL SYSTEM AND A MINE
DRUM HOIST SYSTEM
TECHNICAL FIELD
The present disclosure generally relates to mine drum hoist systems. In particular, it relates to control of a hoist drum of a mine drum hoist system.
BACKGROUND
Hoist drums which coil the rope in more than one layer normally have Lebus grooves in which the rope is laid. The grooves are parallel except in the cross-over sections in which the groove moves the rope in the axial direction of the drum a distance which is equal to half the rope diameter, to the next parallel grove. There are two cross-over sections on the circumference of the drum surface which means that after a full revolution the rope has been moved by the Lebus groove one rope diameter. Normally the cross-over sections are diametrical. This arrangement is called symmetric Lebus.
The drum is normally mounted near the ground surface. The rope runs from the drum to a head sheave in the head frame above the mine shaft. The rope angle between the drum and the head sheave is normally in the order of 45 degrees. After passing over the head sheave the rope runs vertically in the mine shaft. The rope end is connected to a conveyance for transport of personnel, mineral or equipment. The part of the rope that is between the hoist drum and the head sheave is called catenary.
The cross-over section pushes the rope over in a short time creating a near rectangular pulse-shaped "kick" on the rope in a direction perpendicular to the rope axis, also called transversal kick. The pulse wave can be converted to a fundamental sine wave with harmonics by means of Fourier transformation. If the kick is repeated, i.e. excited with a frequency that corresponds to the natural or resonance frequency of the catenary the amplitude of the transversal catenary oscillations will build up to large unacceptable values. High amplitudes will severely affect the rope life.
2 Moreover, high amplitudes can provide discomfort to personnel traveling with the conveyance.
It is known that by reducing the hoisting, i.e. rope speed when the rope pull is near a point where catenary resonance would be generated at that maximum speed, the resonance point will shift to another rope pull since at the reduced speed the excitation or kick frequency of the Lebus on the drum will be reduced.
For hoists which always run at nominal full speed and with constant load in the up direction and with zero payload in the down direction, which is the io case for production hoists, it is normally sufficient to have a pre-set distance in the mine shaft where the hoisting speed is reduced. However, this is not sufficient in case the payload and the speed of the conveyance vary.
SUMMARY
An object of the present disclosure is to solve, or at least mitigate, the problems of the prior art.
Hence, according to a first aspect of the present disclosure there is provided a method of controlling transversal resonance in a catenary of a mine drum hoist system comprising a hoist drum having Lebus grooves, a head sheave, a rope having a catenary extending between the hoist drum and the head sheave and a vertical rope portion, and a conveyance attached to the vertical rope portion, wherein the method comprises: a) determining a current payload of the conveyance, b) obtaining a rotation speed of the hoist drum, corresponding to a first speed of the conveyance, c) determining a transversal resonance position along the vertical rope portion at which transversal resonance is generated in the catenary when reached by the conveyance with the current payload and first speed, wherein the transversal resonance position is determined based on the current payload and on the hoist speed, and d) reducing the first speed of the conveyance in a speed reduction zone which includes the transversal resonance position.
It is known that by reducing the hoisting, i.e. rope speed when the rope pull is near a point where catenary resonance would be generated at that maximum speed, the resonance point will shift to another rope pull since at the reduced speed the excitation or kick frequency of the Lebus on the drum will be reduced.
For hoists which always run at nominal full speed and with constant load in the up direction and with zero payload in the down direction, which is the io case for production hoists, it is normally sufficient to have a pre-set distance in the mine shaft where the hoisting speed is reduced. However, this is not sufficient in case the payload and the speed of the conveyance vary.
SUMMARY
An object of the present disclosure is to solve, or at least mitigate, the problems of the prior art.
Hence, according to a first aspect of the present disclosure there is provided a method of controlling transversal resonance in a catenary of a mine drum hoist system comprising a hoist drum having Lebus grooves, a head sheave, a rope having a catenary extending between the hoist drum and the head sheave and a vertical rope portion, and a conveyance attached to the vertical rope portion, wherein the method comprises: a) determining a current payload of the conveyance, b) obtaining a rotation speed of the hoist drum, corresponding to a first speed of the conveyance, c) determining a transversal resonance position along the vertical rope portion at which transversal resonance is generated in the catenary when reached by the conveyance with the current payload and first speed, wherein the transversal resonance position is determined based on the current payload and on the hoist speed, and d) reducing the first speed of the conveyance in a speed reduction zone which includes the transversal resonance position.
3 A technical effect obtainable by reducing the first speed of the conveyance in a speed reduction zone is that the resonance point is moved away from the transversal resonance point. As a result transversal resonance does not occur at the determined transversal resonance position. Moreover, since the first speed is maintained outside the speed reduction zone, a transversal resonance position that is moved due to speed reduction will never be realised, because it is moved to the originally determined transversal resonance position when the conveyance moves outside the speed reduction zone. Thus, transversal resonance in the catenary may essentially be avoided for any payload and any first speed of the conveyance. The payload and/or speed are thus allowed to vary each time the conveyance is hoisted in the mine shaft.
One embodiment comprises receiving a first force measurement from a first load cell of the head sheave and a second force measurement from a second load cell of the head sheave, wherein step a) involves determining a sum of force value by adding the first force measurement to the second force measurement, wherein the current payload is determined based on the sum of force value.
According to one embodiment the current payload is determined by subtracting the weight of the vertical rope portion, the weight of the conveyance and the weight of the head sheave from the sum of force value.
According to one embodiment in step c) the determining of the transversal resonance position is further based on a resonance frequency of the catenary, a diameter of the hoist drum, a frequency of an impulse in the rope occurring at cross-overs of the Lebus grooves, a length of the vertical rope portion from a centre axis of the head sheave to a mine shaft opening, a weight of the conveyance, a rope weight per length unit and the length of the catenary.
According to one embodiment in step c) the transversal resonance position is obtained from a look-up table which contains pre-calculated transversal
One embodiment comprises receiving a first force measurement from a first load cell of the head sheave and a second force measurement from a second load cell of the head sheave, wherein step a) involves determining a sum of force value by adding the first force measurement to the second force measurement, wherein the current payload is determined based on the sum of force value.
According to one embodiment the current payload is determined by subtracting the weight of the vertical rope portion, the weight of the conveyance and the weight of the head sheave from the sum of force value.
According to one embodiment in step c) the determining of the transversal resonance position is further based on a resonance frequency of the catenary, a diameter of the hoist drum, a frequency of an impulse in the rope occurring at cross-overs of the Lebus grooves, a length of the vertical rope portion from a centre axis of the head sheave to a mine shaft opening, a weight of the conveyance, a rope weight per length unit and the length of the catenary.
According to one embodiment in step c) the transversal resonance position is obtained from a look-up table which contains pre-calculated transversal
4 resonance positions for a plurality of different current payloads and first speed of the conveyance combinations.
According to one embodiment step d) of reducing the first speed of the conveyance involves reducing the hoist speed.
One embodiment comprises determining the speed reduction zone based on the hoist speed obtained in step b), wherein the determining of the speed reduction zone involves retrieving a speed reduction zone that has been determined for the transversal resonance position and which has been determined based on catenary side force values which are proportional to a difference between a first force measurement measured by a first load cell and a second force measurement measured by a second load cell.
According to a second aspect of the present disclosure there is provided a computer program product comprising computer-executable components which when executed by a processing system causes a hoist drum control system including the processing system to perform the method according to the first aspect.
According to a third aspect of the present disclosure there is provided a hoist drum control system configured to control transversal resonance in a catenary of a mine drum hoist system, wherein the hoist drum control system comprises a storage unit, and a processing system, wherein the storage unit comprises computer-executable components which when executed by the processing system causes the hoist drum control system to: determine a current payload of a conveyance, obtain a hoist speed of a hoist drum, corresponding to a first speed of the conveyance, determine a transversal resonance position along a vertical rope portion of a rope to which the conveyance is attached, at which transversal resonance position, at which transversal resonance position transversal resonance is generated in the catenary when reached by the conveyance with the current payload and first speed, wherein the transversal resonance position is determined based on the current payload and on the hoist speed, and reduce the first speed of the conveyance in a speed reduction zone which includes the transversal resonance position.
According to one embodiment the processing system is configured to receive a first force measurement from a first load cell of a head sheave and a second
According to one embodiment step d) of reducing the first speed of the conveyance involves reducing the hoist speed.
One embodiment comprises determining the speed reduction zone based on the hoist speed obtained in step b), wherein the determining of the speed reduction zone involves retrieving a speed reduction zone that has been determined for the transversal resonance position and which has been determined based on catenary side force values which are proportional to a difference between a first force measurement measured by a first load cell and a second force measurement measured by a second load cell.
According to a second aspect of the present disclosure there is provided a computer program product comprising computer-executable components which when executed by a processing system causes a hoist drum control system including the processing system to perform the method according to the first aspect.
According to a third aspect of the present disclosure there is provided a hoist drum control system configured to control transversal resonance in a catenary of a mine drum hoist system, wherein the hoist drum control system comprises a storage unit, and a processing system, wherein the storage unit comprises computer-executable components which when executed by the processing system causes the hoist drum control system to: determine a current payload of a conveyance, obtain a hoist speed of a hoist drum, corresponding to a first speed of the conveyance, determine a transversal resonance position along a vertical rope portion of a rope to which the conveyance is attached, at which transversal resonance position, at which transversal resonance position transversal resonance is generated in the catenary when reached by the conveyance with the current payload and first speed, wherein the transversal resonance position is determined based on the current payload and on the hoist speed, and reduce the first speed of the conveyance in a speed reduction zone which includes the transversal resonance position.
According to one embodiment the processing system is configured to receive a first force measurement from a first load cell of a head sheave and a second
5 force measurement from a second load cell of the head sheave, wherein the processing system is configured to determine a sum of force value adding the first force measurement to the second force measurement, and wherein the processing system is configured to determine the current payload based on the sum of force value.
According to one embodiment the processing system is configured to determine the current payload by subtracting the weight of the vertical rope portion, the weight of the conveyance and the weight of the head sheave from the sum of force value.
According to one embodiment the processing system is configured to determine the transversal resonance position based on a resonance frequency of the catenary, a diameter of the hoist drum, a frequency of an impulse in the rope occurring at cross-overs of Lebus grooves of a hoist drum, a length of the vertical rope portion from a centre axis of the head sheave to a mine shaft opening, a weight of the conveyance, a rope weight per length unit and the length of the catenary.
According to one embodiment the processing system is configured to obtain the transversal resonance position from a look-up table which contains pre-calculated transversal resonance positions for a plurality of different current payloads and hoist speed combinations.
According to one embodiment the processing system is configured to determine the speed reduction zone based on the hoist speed, wherein the processing system is configured to determine the speed reduction zone by retrieving a speed reduction zone that has been determined for the transversal resonance position and which has been determined based on catenary side force values which are proportional to a difference between a
According to one embodiment the processing system is configured to determine the current payload by subtracting the weight of the vertical rope portion, the weight of the conveyance and the weight of the head sheave from the sum of force value.
According to one embodiment the processing system is configured to determine the transversal resonance position based on a resonance frequency of the catenary, a diameter of the hoist drum, a frequency of an impulse in the rope occurring at cross-overs of Lebus grooves of a hoist drum, a length of the vertical rope portion from a centre axis of the head sheave to a mine shaft opening, a weight of the conveyance, a rope weight per length unit and the length of the catenary.
According to one embodiment the processing system is configured to obtain the transversal resonance position from a look-up table which contains pre-calculated transversal resonance positions for a plurality of different current payloads and hoist speed combinations.
According to one embodiment the processing system is configured to determine the speed reduction zone based on the hoist speed, wherein the processing system is configured to determine the speed reduction zone by retrieving a speed reduction zone that has been determined for the transversal resonance position and which has been determined based on catenary side force values which are proportional to a difference between a
6 first force measurement measured by a first load cell and a second force measurement measured by a second load cell.
According to a fourth aspect of the present disclosure there is provided a mine drum hoist system comprising: a hoist drum having Lebus grooves, a head sheave, a rope arranged to extend between the hoist drum and the head sheave to thereby define a catenary and a vertical rope portion, a conveyance arranged to be attached to the vertical rope portion, a motor arranged to operate the hoist drum, and a hoist drum control system according to the third aspect, arranged to control the motor.
Generally, all terms used in the description are to be interpreted according to their ordinary meaning in the technical field, unless explicitly defined otherwise herein. All references to "a/an/the element, apparatus, component, means, etc. are to be interpreted openly as referring to at least one instance of the element, apparatus, component, means, etc., unless explicitly stated otherwise.
BRIEF DESCRIPTION OF THE DRAWINGS
The specific embodiments of the inventive concept will now be described, by way of example, with reference to the accompanying drawings, in which:
Fig. 1 is a schematic example of a mine drum hoist system and a hoist drum control system;
Fig. 2 is a schematic front view of an example of a mine drum hoist system in Fig. 1;
Fig. 3a is a schematic side view of a detail of a head sheave in the mine drum hoist system in Fig. 1;
Fig- 3b is a schematic front view of a detail of the head sheave in Fig. 1;
Fig. 3c is a schematic front view of the hoist drum and the head sheave in Fig. 1;
According to a fourth aspect of the present disclosure there is provided a mine drum hoist system comprising: a hoist drum having Lebus grooves, a head sheave, a rope arranged to extend between the hoist drum and the head sheave to thereby define a catenary and a vertical rope portion, a conveyance arranged to be attached to the vertical rope portion, a motor arranged to operate the hoist drum, and a hoist drum control system according to the third aspect, arranged to control the motor.
Generally, all terms used in the description are to be interpreted according to their ordinary meaning in the technical field, unless explicitly defined otherwise herein. All references to "a/an/the element, apparatus, component, means, etc. are to be interpreted openly as referring to at least one instance of the element, apparatus, component, means, etc., unless explicitly stated otherwise.
BRIEF DESCRIPTION OF THE DRAWINGS
The specific embodiments of the inventive concept will now be described, by way of example, with reference to the accompanying drawings, in which:
Fig. 1 is a schematic example of a mine drum hoist system and a hoist drum control system;
Fig. 2 is a schematic front view of an example of a mine drum hoist system in Fig. 1;
Fig. 3a is a schematic side view of a detail of a head sheave in the mine drum hoist system in Fig. 1;
Fig- 3b is a schematic front view of a detail of the head sheave in Fig. 1;
Fig. 3c is a schematic front view of the hoist drum and the head sheave in Fig. 1;
7 Fig. 4 is a schematic diagram of a method of controlling transversal resonance in a catenary of the mine drum hoist system in Fig. 1; and Figs 5a-5c show graphs of catenary side force values.
DETAILED DESCRIPTION
The inventive concept will now be described more fully hereinafter with reference to the accompanying drawings, in which exemplifying embodiments are shown. The inventive concept may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein; rather, these embodiments are provided by way of example so that this disclosure will be thorough and complete, and will fully convey the scope of the inventive concept to those skilled in the art.
Like numbers refer to like elements throughout the description.
The present disclosure in general details how transversal resonance in a catenary may be avoided or at least reduced in a mine drum hoist system by determining a transversal resonance position along the vertical rope portion of a rope extending from the head sheave to a conveyance connected to the vertical rope portion, and by reducing the speed of the conveyance in a speed reduction zone that includes the transversal resonance position. The transversal resonance position is determined based on the current payload of the conveyance which is arranged to be hoisted in the mine shaft by means of a hoist drum, and on the desired speed at which the conveyance is to move in the mine shaft, in case the speed is pre-programmed, or on the actual current speed at which the conveyance moves in the mine shaft, in case the conveyance speed is operated manually.
By reducing the speed only in the speed reduction zone(s), in case there are several catenary transverse resonance points, the transversal resonance point(s) is/are moved away from the determined transversal resonance point(s).
This disclosure furthermore details which positions along the vertical rope portion should be categorised as transversal resonance positions in the
DETAILED DESCRIPTION
The inventive concept will now be described more fully hereinafter with reference to the accompanying drawings, in which exemplifying embodiments are shown. The inventive concept may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein; rather, these embodiments are provided by way of example so that this disclosure will be thorough and complete, and will fully convey the scope of the inventive concept to those skilled in the art.
Like numbers refer to like elements throughout the description.
The present disclosure in general details how transversal resonance in a catenary may be avoided or at least reduced in a mine drum hoist system by determining a transversal resonance position along the vertical rope portion of a rope extending from the head sheave to a conveyance connected to the vertical rope portion, and by reducing the speed of the conveyance in a speed reduction zone that includes the transversal resonance position. The transversal resonance position is determined based on the current payload of the conveyance which is arranged to be hoisted in the mine shaft by means of a hoist drum, and on the desired speed at which the conveyance is to move in the mine shaft, in case the speed is pre-programmed, or on the actual current speed at which the conveyance moves in the mine shaft, in case the conveyance speed is operated manually.
By reducing the speed only in the speed reduction zone(s), in case there are several catenary transverse resonance points, the transversal resonance point(s) is/are moved away from the determined transversal resonance point(s).
This disclosure furthermore details which positions along the vertical rope portion should be categorised as transversal resonance positions in the
8 control method, as there may be some transversal resonance positions that provide less significant transversal resonance in the catenary, where it is not necessary to reduce the speed of the conveyance. A tuning method in which the relevant transversal resonance point(s) is/are selected for the control method is therefore also disclosed herein. The tuning method also discloses how the speed reduction zone(s) is/are selected and how much the speed of the conveyance shall be reduced in the speed reduction zone(s).
Fig.i depicts a mine drum hoist system 1 comprising a hoist drum 5, which is of Lebus type. The hoist drum 5 hence has a plurality of Lebus grooves 5a, as shown in Fig. 2. The Lebus grooves 5a have two cross-over sections per turn, as shown by means of the areas 5b and 5c in Fig. 2.Each cross-over section translates the Lebus grooves 5a for example half a rope diameter in the axial direction. In one turn each Lebus groove 5a is hence translated a rope diameter in the axial direction.
The drum hoist 5 may for example be a single drum hoist or a double drum hoists. Each of them can be equipped with one or two ropes that carry the conveyance.
The mine drum hoist system 1 further comprises a head sheave 7, a rope 9 and a conveyance ii. The rope 9 is coiled around the hoist drum 5, in one or more layers, for example three layers. The rope 9 extends from the hoist drum 5 to the head sheave 7. The rope 9 has a catenary 9a that extends between the hoist drum 5, about which the rope is coiled in the Lebus grooves 5a, and the head sheave 7. The rope 9 has a vertical rope portion 9b that runs from the head sheave 7 to the conveyance. The rope 9 is connected to or attached to the conveyance 11, so that when the hoist drum 5 is rotated and the rope 9 is coiled or uncoiled, the vertical position of the conveyance 11 is altered.
The mine drum hoist system 1 comprises a first load cell 7a and a second load cell 7b. The head sheave 7 is equipped with the first load cell 7a and the second load cell 7b. The first load cell 7a and the second load cell 7b are
Fig.i depicts a mine drum hoist system 1 comprising a hoist drum 5, which is of Lebus type. The hoist drum 5 hence has a plurality of Lebus grooves 5a, as shown in Fig. 2. The Lebus grooves 5a have two cross-over sections per turn, as shown by means of the areas 5b and 5c in Fig. 2.Each cross-over section translates the Lebus grooves 5a for example half a rope diameter in the axial direction. In one turn each Lebus groove 5a is hence translated a rope diameter in the axial direction.
The drum hoist 5 may for example be a single drum hoist or a double drum hoists. Each of them can be equipped with one or two ropes that carry the conveyance.
The mine drum hoist system 1 further comprises a head sheave 7, a rope 9 and a conveyance ii. The rope 9 is coiled around the hoist drum 5, in one or more layers, for example three layers. The rope 9 extends from the hoist drum 5 to the head sheave 7. The rope 9 has a catenary 9a that extends between the hoist drum 5, about which the rope is coiled in the Lebus grooves 5a, and the head sheave 7. The rope 9 has a vertical rope portion 9b that runs from the head sheave 7 to the conveyance. The rope 9 is connected to or attached to the conveyance 11, so that when the hoist drum 5 is rotated and the rope 9 is coiled or uncoiled, the vertical position of the conveyance 11 is altered.
The mine drum hoist system 1 comprises a first load cell 7a and a second load cell 7b. The head sheave 7 is equipped with the first load cell 7a and the second load cell 7b. The first load cell 7a and the second load cell 7b are
9 utilised for determining a current payload of the conveyance 11 and a catenary side force on the head sheave 7.
A number of vertical distances are depicted in Fig. 1. A first distance di is defined as the vertical distance from the head sheave axis A to the mine shaft opening 13 which is the upper landing level for the conveyance 11. This first distance di is fixed, and is a known parameter. A second distance d2 is defined as the vertical distance from the mine shaft opening 13 to the top of the conveyance 11. The second distance d2 is at its maximum value when the conveyance is at the bottom landing level. A third distance d3 is determined as the distance from the head sheave axis A to the top of the conveyance 11, i.e. the sum of the first distance di and the second distance d2. It is normally the second distance d2 that determines a transversal resonance position along the vertical rope portion 9b, which will be described in more detail in the following. A transversal resonance position is a position along the vertical rope portion 9b at which transversal resonance is generated in the catenary 9a when reached by the conveyance 11 with a particular payload and speed.
The mine drum hoist system 1 comprises a hoist drum control system 3 having a processing system 3a and a storage unit 3h. The storage unit 3b comprises computer-executable components which when run on the processing system 3a causes the hoist drum control system 3 to perform the methods disclosed herein. In particular, the hoist drum control system 3 is configured to determine a current payload of the conveyance 11. The hoist drum control system 3 may for example determine the current payload based on a first force measurement and a second force measurement carried out by the first load cell 7a and the second load cell 7b, respectively.
The hoist drum control system 3 is moreover configured to obtain a hoist speed of the hoist drum 5 in metres per second, which is the speed of the conveyance ii, termed the first speed herein. The hoist speed may be a pre-programmed parameter for operating the conveyance 11, or it may be a real-time value obtained for example by measuring the number of revolutions per time unit of the hoist drum 5.
The hoist drum control system 3 is furthermore configured to determine a transversal resonance position along the vertical rope portion 9b at which transversal resonance is generated in the catenary 9a when reached by the conveyance ii with the current payload and first speed, and to reduce the first 5 speed of the conveyance ii in a speed reduction zone which includes the transversal resonance position.
The transversal resonance position is determined by the hoist drum control system 3 based on the current payload and on the hoist speed. The transversal resonance position is equivalent to the second distance d2 for
A number of vertical distances are depicted in Fig. 1. A first distance di is defined as the vertical distance from the head sheave axis A to the mine shaft opening 13 which is the upper landing level for the conveyance 11. This first distance di is fixed, and is a known parameter. A second distance d2 is defined as the vertical distance from the mine shaft opening 13 to the top of the conveyance 11. The second distance d2 is at its maximum value when the conveyance is at the bottom landing level. A third distance d3 is determined as the distance from the head sheave axis A to the top of the conveyance 11, i.e. the sum of the first distance di and the second distance d2. It is normally the second distance d2 that determines a transversal resonance position along the vertical rope portion 9b, which will be described in more detail in the following. A transversal resonance position is a position along the vertical rope portion 9b at which transversal resonance is generated in the catenary 9a when reached by the conveyance 11 with a particular payload and speed.
The mine drum hoist system 1 comprises a hoist drum control system 3 having a processing system 3a and a storage unit 3h. The storage unit 3b comprises computer-executable components which when run on the processing system 3a causes the hoist drum control system 3 to perform the methods disclosed herein. In particular, the hoist drum control system 3 is configured to determine a current payload of the conveyance 11. The hoist drum control system 3 may for example determine the current payload based on a first force measurement and a second force measurement carried out by the first load cell 7a and the second load cell 7b, respectively.
The hoist drum control system 3 is moreover configured to obtain a hoist speed of the hoist drum 5 in metres per second, which is the speed of the conveyance ii, termed the first speed herein. The hoist speed may be a pre-programmed parameter for operating the conveyance 11, or it may be a real-time value obtained for example by measuring the number of revolutions per time unit of the hoist drum 5.
The hoist drum control system 3 is furthermore configured to determine a transversal resonance position along the vertical rope portion 9b at which transversal resonance is generated in the catenary 9a when reached by the conveyance ii with the current payload and first speed, and to reduce the first 5 speed of the conveyance ii in a speed reduction zone which includes the transversal resonance position.
The transversal resonance position is determined by the hoist drum control system 3 based on the current payload and on the hoist speed. The transversal resonance position is equivalent to the second distance d2 for
10 certain positions of the conveyance ii. By reducing the first speed of the conveyance 11 to a second speed in the speed reduction zone, by operating the hoist speed, the transversal resonance position is moved from that determined by the hoist drum control system 3 to a moved transversal resonance position. With moved transversal resonance position is meant the transversal resonance position to which the transversal resonance position is moved due to the reduction of the first speed. Catenary resonance will however not occur when the conveyance ii reaches the moved transversal resonance position because the first speed is only reduced in the speed reduction zone.
The mine drum hoist system 1 may comprise a motor M and a drive unit 15.
The hoist drum control system 3 may be configured to operate the motor M, e.g. via the drive unit 15 to thereby control the coiling speed and uncoiling speed of the rope 9, i.e. the hoist speed, from the hoist drum 5. As a result the speed of the conveyance ii may be controlled.
Fig. 3a schematically shows a side view of the head sheave 7, one of the load cells, in this example the first load cell 7a, the catenary 9a and the vertical rope portion 9b. The total force, a sum of force value Ftot, measured by the first load cell 7a and the second load cell 7b is the sum of the force provided by the weight of the head sheave 7 and the vector sum of the rope pull force, i.e. the vertical component FR and the catenary component FR, which seen as
The mine drum hoist system 1 may comprise a motor M and a drive unit 15.
The hoist drum control system 3 may be configured to operate the motor M, e.g. via the drive unit 15 to thereby control the coiling speed and uncoiling speed of the rope 9, i.e. the hoist speed, from the hoist drum 5. As a result the speed of the conveyance ii may be controlled.
Fig. 3a schematically shows a side view of the head sheave 7, one of the load cells, in this example the first load cell 7a, the catenary 9a and the vertical rope portion 9b. The total force, a sum of force value Ftot, measured by the first load cell 7a and the second load cell 7b is the sum of the force provided by the weight of the head sheave 7 and the vector sum of the rope pull force, i.e. the vertical component FR and the catenary component FR, which seen as
11 vector components have different directions, but they both have the same magnitude, FR.
According to one variation, the hoist drum control system 3 is arranged to determine the sum of force value by adding the first force measurement FLa to the second force measurement FLb, shown in Fig. 3b. The hoist drum control system 3 is according to one variation configured to determine the current payload based on the sum of force value Ftot, which is the absolute value of the vector addition of the first force measurement FLa and the second force measurement FLb. The current payload may be determined by subtracting the weight of the vertical rope portion 9b, the weight of the conveyance ii, and the weight of the head sheave 7 from the sum of force value Ft.t. The catenary resonance frequency fc, in particular the fundamental resonance frequency, may be expressed as 1 . ,\I FR
(1) 2.Lc mr where Lc is the length of the catenary 9a and mr is the weight of the rope in mass/length unit, e.g. kg/m. A transversal resonance in the catenary is obtained when an integer multiple of the fundamental rope kick frequency fexe is equal to the catenary resonance frequency fc. The fundamental rope kick frequency may be expressed as , V
fexc = L ' ¨
n=D (2) where v is the hoist speed in metres/second, and D is the diameter of the hoist drum 5. In case there are several layers of rope coiled onto the hoist drum 5, these are also taken into account when calculating the fundamental rope kick frequency fexe.
The rope pull force value may be expressed as FR=(mc-Fmi+d3*mr)*g, where mc is the weight of the conveyance ii and mi is the current payload, the third
According to one variation, the hoist drum control system 3 is arranged to determine the sum of force value by adding the first force measurement FLa to the second force measurement FLb, shown in Fig. 3b. The hoist drum control system 3 is according to one variation configured to determine the current payload based on the sum of force value Ftot, which is the absolute value of the vector addition of the first force measurement FLa and the second force measurement FLb. The current payload may be determined by subtracting the weight of the vertical rope portion 9b, the weight of the conveyance ii, and the weight of the head sheave 7 from the sum of force value Ft.t. The catenary resonance frequency fc, in particular the fundamental resonance frequency, may be expressed as 1 . ,\I FR
(1) 2.Lc mr where Lc is the length of the catenary 9a and mr is the weight of the rope in mass/length unit, e.g. kg/m. A transversal resonance in the catenary is obtained when an integer multiple of the fundamental rope kick frequency fexe is equal to the catenary resonance frequency fc. The fundamental rope kick frequency may be expressed as , V
fexc = L ' ¨
n=D (2) where v is the hoist speed in metres/second, and D is the diameter of the hoist drum 5. In case there are several layers of rope coiled onto the hoist drum 5, these are also taken into account when calculating the fundamental rope kick frequency fexe.
The rope pull force value may be expressed as FR=(mc-Fmi+d3*mr)*g, where mc is the weight of the conveyance ii and mi is the current payload, the third
12 distance d3=di+d2, and g is the gravitational acceleration. Thus from the relation fexc=fC it can be deduced that ((4-v=Lc)2.7nr/g-n1C-Inl) d 2 = 7C'D dl (3) mr In view of equation (3), according to one variation the hoist drum control system 3 may hence be configured to determine the transversal resonance position, in addition to the payload and the hoist speed, based on the resonance frequency of the catenary 9a, the diameter D of the hoist drum 5, the frequency of an impulse in the rope occurring at cross-overs of the Lebus grooves, i.e. the rope kick frequency f -exc, the length of the vertical rope io portion from a centre axis of the head sheave, i.e. head sheave axis A, to the mine shaft opening 13, i.e. the first distance di, the length of the catenary, the weight of the conveyance mc, and the rope weight per length unit mr.
A method of controlling transversal resonance in the catenary 9a of the mine drum hoist system i by means of the hoist drum control system 3 will now be described with reference to Fig. 4.
In a step a) a current payload mi of the conveyance 11 is determined by means of the processing system 3a of the hoist drum control system 3. The current payload may thus for example be determined in the manner described hereabove.
As has been previously mentioned, step a) may include receiving a first force measurement from the first load cell 7a of the head sheave 7 and a second force measurement from a second load cell 7b of the head sheave 7. In this case step a) involves determining a sum of force value by adding the first force measurement to the second force measurement, wherein the current payload is determined based on the sum of the force value Ft.t. In particular, the current payload may be determined by subtracting the weight of the conveyance 11, the weight of the vertical rope portion 9b and the head sheave 7 from the sum of force value Ft.t.
A method of controlling transversal resonance in the catenary 9a of the mine drum hoist system i by means of the hoist drum control system 3 will now be described with reference to Fig. 4.
In a step a) a current payload mi of the conveyance 11 is determined by means of the processing system 3a of the hoist drum control system 3. The current payload may thus for example be determined in the manner described hereabove.
As has been previously mentioned, step a) may include receiving a first force measurement from the first load cell 7a of the head sheave 7 and a second force measurement from a second load cell 7b of the head sheave 7. In this case step a) involves determining a sum of force value by adding the first force measurement to the second force measurement, wherein the current payload is determined based on the sum of the force value Ft.t. In particular, the current payload may be determined by subtracting the weight of the conveyance 11, the weight of the vertical rope portion 9b and the head sheave 7 from the sum of force value Ft.t.
13 In a step b) a hoist speed v of the hoist drum 5 is obtained. The hoist speed v, which is proportional to the first speed of the conveyance 11, may be a proportional to a desired maximum speed of the conveyance, i.e. a pre-programmed parameter, or it may be determined in real-time.
It should be noted that it is not necessary for steps a) and b) to be performed in the above order; their order may be interchanged.
In a step c) a transversal resonance position, which is a certain second distance d2, along the vertical rope portion 9b is determined. The transversal resonance position is determined based on the current payload mi and on the hoist speed v. The transversal resonance position may according to one variation be determined by means of equation (3). Alternatively the transversal resonance position may be retrieved from a look-up table in which a plurality of combinations of hoist speed and current payload are stored.
According to one variation in step c) the determining of the transversal resonance position is further based on a resonance frequency fc of the catenary, a diameter d of the hoist drum 5, the frequency f -exe of an impulse in the rope 9 occurring at cross-overs of the Lebus grooves 5b, the length, i.e.
the first distance di, of the vertical rope portion 9b from a centre axis, i.e.
head sheave axis A, of the head sheave 7 to a mine shaft opening 13, the weight of the conveyance mc, the length of the catenary 9a and the rope weight mr per length unit.
In a step d) the first speed of the conveyance 11 is reduced by the hoist drum control system 3 by reducing the hoist speed in a speed reduction zone which includes the transversal resonance position. The reduction of the first speed may thus for example be obtained by the hoist drum control system 3 controlling the drive unit 15, which in turn operates the motor M that drives the hoist drum 5.
The speed reduction zone may be determined by retrieving a speed reduction zone that has been determined for the transversal resonance position during
It should be noted that it is not necessary for steps a) and b) to be performed in the above order; their order may be interchanged.
In a step c) a transversal resonance position, which is a certain second distance d2, along the vertical rope portion 9b is determined. The transversal resonance position is determined based on the current payload mi and on the hoist speed v. The transversal resonance position may according to one variation be determined by means of equation (3). Alternatively the transversal resonance position may be retrieved from a look-up table in which a plurality of combinations of hoist speed and current payload are stored.
According to one variation in step c) the determining of the transversal resonance position is further based on a resonance frequency fc of the catenary, a diameter d of the hoist drum 5, the frequency f -exe of an impulse in the rope 9 occurring at cross-overs of the Lebus grooves 5b, the length, i.e.
the first distance di, of the vertical rope portion 9b from a centre axis, i.e.
head sheave axis A, of the head sheave 7 to a mine shaft opening 13, the weight of the conveyance mc, the length of the catenary 9a and the rope weight mr per length unit.
In a step d) the first speed of the conveyance 11 is reduced by the hoist drum control system 3 by reducing the hoist speed in a speed reduction zone which includes the transversal resonance position. The reduction of the first speed may thus for example be obtained by the hoist drum control system 3 controlling the drive unit 15, which in turn operates the motor M that drives the hoist drum 5.
The speed reduction zone may be determined by retrieving a speed reduction zone that has been determined for the transversal resonance position during
14 a tuning/calibration procedure. The speed reduction zone may during the tuning procedure be determined based on catenary side force values Fc which are proportional to a difference between a first force measurement FLa measured by the first load cell 7a and the second force measurement FLb measured by the second load cell 7b. This procedure will be described in more detail in the following.
The tuning of the control procedure for the hoist drum control system 3 is of importance to be able to determine relevant transversal resonance positions, to thereby obtain efficient equipment, mineral and personnel transportation by means of the conveyance ii. Thus, prior to commissioning of the mine drum hoist system 1 and of the hoist drum control system 3, hoist drum control may be tuned or calibrated. The tuning procedure will be described in the following.
Turning to Fig. 3e, this illustration schematically shows a front view of the hoist drum 5, the head sheave 7, the first load cell 7a and the second load cell 7b. As may be seen in Fig. 3c, a fleet angle a between a vertical central axis defined by the head sheave and the catenary 9a is shown in two extreme positions. The fleet angle a depends on how much rope 9 has been uncoiled from the hoist drum 5, as the catenary moves between left and right along the axial direction of the hoist drum 5 during coiling operations.
According to one variation the hoist drum control system 3 is configured to determine a theoretical catenary side force value Fci by determining the catenary component FR, which is the rope pull, by means of the first force measurement FLa with the first load cell 7a and the second load measurement FLb the second load cell 7b, as has been described previously, and by multiplying the rope pull with sinus a, i.e. Fesin(a), where a is the fleet angle. The theoretical side force value Fci, as shown for a number of second distances d2 is shown in the plot in Fig. 5a. The tuning procedure hence utilises first force measurements of the first load cell 7a and second force measurements of the second load cell 7b, measured along the entire mine shaft in which the conveyance ii is to be transported vertically. It can be seen that the theoretical catenary side force value Fci changes as the conveyance moves along the vertical axis in the mine shaft, i.e. as the second distance d2 changes. In reality, the plot looks more like the example shown in Fig. 5b, where catenary oscillation forces due to transversal kicks which increase 5 largely at resonance in the catenary 9a are superimposed onto the catenary side force value Fci. A plot with catenary side force values Fc is thus obtained.
Each area with increased catenary oscillations in a plot like then one shown in Fig. 5b corresponds to a transversal resonance position. Each catenary side force value Fc is proportional to the difference between the first force 10 measurement FLa from the second force measurement FLb. The catenary side force values Fc may thus be determined based on the difference between the first force measurement FL, and the second force measurement FLb at each measurement point.
The magnitude of these catenary oscillation forces in the plot in Fig. 5b may
The tuning of the control procedure for the hoist drum control system 3 is of importance to be able to determine relevant transversal resonance positions, to thereby obtain efficient equipment, mineral and personnel transportation by means of the conveyance ii. Thus, prior to commissioning of the mine drum hoist system 1 and of the hoist drum control system 3, hoist drum control may be tuned or calibrated. The tuning procedure will be described in the following.
Turning to Fig. 3e, this illustration schematically shows a front view of the hoist drum 5, the head sheave 7, the first load cell 7a and the second load cell 7b. As may be seen in Fig. 3c, a fleet angle a between a vertical central axis defined by the head sheave and the catenary 9a is shown in two extreme positions. The fleet angle a depends on how much rope 9 has been uncoiled from the hoist drum 5, as the catenary moves between left and right along the axial direction of the hoist drum 5 during coiling operations.
According to one variation the hoist drum control system 3 is configured to determine a theoretical catenary side force value Fci by determining the catenary component FR, which is the rope pull, by means of the first force measurement FLa with the first load cell 7a and the second load measurement FLb the second load cell 7b, as has been described previously, and by multiplying the rope pull with sinus a, i.e. Fesin(a), where a is the fleet angle. The theoretical side force value Fci, as shown for a number of second distances d2 is shown in the plot in Fig. 5a. The tuning procedure hence utilises first force measurements of the first load cell 7a and second force measurements of the second load cell 7b, measured along the entire mine shaft in which the conveyance ii is to be transported vertically. It can be seen that the theoretical catenary side force value Fci changes as the conveyance moves along the vertical axis in the mine shaft, i.e. as the second distance d2 changes. In reality, the plot looks more like the example shown in Fig. 5b, where catenary oscillation forces due to transversal kicks which increase 5 largely at resonance in the catenary 9a are superimposed onto the catenary side force value Fci. A plot with catenary side force values Fc is thus obtained.
Each area with increased catenary oscillations in a plot like then one shown in Fig. 5b corresponds to a transversal resonance position. Each catenary side force value Fc is proportional to the difference between the first force 10 measurement FLa from the second force measurement FLb. The catenary side force values Fc may thus be determined based on the difference between the first force measurement FL, and the second force measurement FLb at each measurement point.
The magnitude of these catenary oscillation forces in the plot in Fig. 5b may
15 be utilised by for example a commissioning engineer to determine whether a transversal resonance position is large enough to motivate a speed reduction of the conveyance and thus whether to determine a speed reduction zone around such a transversal resonance position. The commissioning engineer may for example calculate the difference between the maximum and minimum of a number of values over a period of time for this purpose. By means of studying the area in which a transversal resonance position occurs, the speed reduction zone may also be determined, i.e. how far before a transversal resonance position and how far after a transversal resonance position a speed reduction zone is to be defined. The speed reduction zone may for example in a first step be determined or obtained by a qualified guess by the commissioning engineer when studying a plot like then one presented in Fig. 5b. The conveyance 11 may afterwards be subjected to a test drive utilising the determined speed reduction zone. The catenary side force values Fc are then once again determined by means of the proportionality to the difference between the first force measurement FL, and the second force measurement FLb at each measurement point. It can then be verified whether the determined/guessed speed reduction zone is sufficient for reducing or
16 eliminating the catenary oscillations at a transversal resonance position, or whether the speed reduction zone must be modified. This procedure may be repeated/iterated until a satisfactory result has been obtained. A thus determined speed reduction zone for a plurality of transversal resonance positions may then be stored by the hoist drum control system 3. Thus, when the hoist drum control system 3 at a later time, for the purpose of controlling transversal resonance in the catenary 9a, as described above, determines a transversal resonance position for a certain payload, the hoist drum control system 3 may be configured to determine the speed reduction zone for that transversal resonance position by retrieving a suitable speed reduction zone for that transversal resonance position during tuning/calibration.
Furthermore, the second speed, i.e. the reduced speed may also be determined by the commissioning engineer. The method of controlling transversal resonance in a catenary 9a may thus be tuned/calibrated.
Fig. 5c shows a plot in which the values in Fig. 5a have been subtracted from the measurement values in Fig. 5b, i.e. Fc2=Fc-F1, to obtain an adjusted catenary side force values Fc2. The adjusted catenary side force values Fc2 provide better supervision of the tuning since the graph extends parallel to the x-axis. The maximum and minimum limits can in a simpler manner be defined and supervised. According to one variation, the hoist drum control system 3 is configured to determine the difference between the maximum and minimum of a number of values over a period of time of the catenary side force values Fc or the adjusted catenary side force values Fcs.
The inventive concept has mainly been described above with reference to a few examples. However, as is readily appreciated by a person skilled in the art, other embodiments than the ones disclosed above are equally possible within the scope of the inventive concept, as defined by the appended claims.
Furthermore, the second speed, i.e. the reduced speed may also be determined by the commissioning engineer. The method of controlling transversal resonance in a catenary 9a may thus be tuned/calibrated.
Fig. 5c shows a plot in which the values in Fig. 5a have been subtracted from the measurement values in Fig. 5b, i.e. Fc2=Fc-F1, to obtain an adjusted catenary side force values Fc2. The adjusted catenary side force values Fc2 provide better supervision of the tuning since the graph extends parallel to the x-axis. The maximum and minimum limits can in a simpler manner be defined and supervised. According to one variation, the hoist drum control system 3 is configured to determine the difference between the maximum and minimum of a number of values over a period of time of the catenary side force values Fc or the adjusted catenary side force values Fcs.
The inventive concept has mainly been described above with reference to a few examples. However, as is readily appreciated by a person skilled in the art, other embodiments than the ones disclosed above are equally possible within the scope of the inventive concept, as defined by the appended claims.
Claims (15)
1. A method of controlling transversal resonance in a catenary of a mine drum hoist system comprising a hoist drum having Lebus grooves, a head sheave, a rope having a catenary extending between the hoist drum and the head sheave and a vertical rope portion, and a conveyance attached to the vertical rope portion, wherein the method comprises:
a) determining a current payload of the conveyance;
b) obtaining a hoist speed of the hoist drum, corresponding to a first speed of the conveyance;
c) determining a transversal resonance position along the vertical rope portion at which transversal resonance is generated in the catenary when reached by the conveyance with the current payload and first speed, wherein the transversal resonance position is determined based on the current payload and on the hoist speed; and d) reducing the first speed of the conveyance in a speed reduction zone which includes the transversal resonance position.
a) determining a current payload of the conveyance;
b) obtaining a hoist speed of the hoist drum, corresponding to a first speed of the conveyance;
c) determining a transversal resonance position along the vertical rope portion at which transversal resonance is generated in the catenary when reached by the conveyance with the current payload and first speed, wherein the transversal resonance position is determined based on the current payload and on the hoist speed; and d) reducing the first speed of the conveyance in a speed reduction zone which includes the transversal resonance position.
2. The method as claimed in claim 1, comprising:
receiving a first force measurement (F La) from a first load cell of the head sheave and a second force measurement (F Lb) from a second load cell of the head sheave, wherein step a) involves determining a sum of force value by adding the first force measurement to the second force measurement, wherein the current payload is determined based on the sum of force value.
receiving a first force measurement (F La) from a first load cell of the head sheave and a second force measurement (F Lb) from a second load cell of the head sheave, wherein step a) involves determining a sum of force value by adding the first force measurement to the second force measurement, wherein the current payload is determined based on the sum of force value.
3. The method as claimed in claim 2, wherein the current payload is determined by subtracting the weight of the vertical rope portion, the weight of the conveyance and the weight of the head sheave from the sum of force value.
4. The method as claimed in any one of claims 1 to 3, wherein in step c) the determining of the transversal resonance position is further based on a resonance frequency of the catenary, a diameter (D) of the hoist drum, a frequency of an impulse in the rope occurring at cross-overs of the Lebus grooves, a length of the vertical rope portion from a centre axis (A) of the head sheave to a mine shaft opening, a weight of the conveyance, a rope weight per length unit, and the length of the catenary.
5. The method as claimed in any one of claims 1 to 3, wherein in step c) the transversal resonance position is obtained from a look-up table which contains pre-calculated transversal resonance positions for a plurality of different current payloads and hoist speed combinations.
6. The method as claimed in any one of claims 1 to 5, wherein step d) of reducing the first speed of the conveyance involves reducing the hoist speed.
7. The method as claimed in any one of claims 1 to 6, comprising:
determining the speed reduction zone based on the hoist speed obtained in step b), wherein the determining of the speed reduction zone involves retrieving a speed reduction zone that has been determined for the transversal resonance position and which has been determined based on catenary side force values (Fc) which are proportional to a difference between a first force measurement (F La) measured by a first load cell and a second force measurement (F Lb) measured by a second load cell.
determining the speed reduction zone based on the hoist speed obtained in step b), wherein the determining of the speed reduction zone involves retrieving a speed reduction zone that has been determined for the transversal resonance position and which has been determined based on catenary side force values (Fc) which are proportional to a difference between a first force measurement (F La) measured by a first load cell and a second force measurement (F Lb) measured by a second load cell.
8. A computer program product comprising computer-executable components which when executed by a processing system causes a hoist drum control system including the processing system to perform a method as defined in any one of claims 1 to 7.
9. A hoist drum control system configured to control transversal resonance in a catenary of a mine drum hoist system comprising a hoist drum having Lebus grooves, a head sheave, a rope having a catenary extending between the hoist drum and the head sheave and a vertical rope portion, and a conveyance attached to the vertical rope portion, wherein the hoist drum control system comprises:
a storage unit; and a processing system;
wherein the storage unit comprises computer-executable components which when executed by the processing system causes the hoist drum control system to:
determine a current payload of the conveyance;
obtain a hoist speed of the hoist drum, corresponding to a first speed of the conveyance;
determine a transversal resonance position along the vertical rope portion of the rope to which the conveyance is attached, at which transversal resonance position transversal resonance is generated in the catenary when reached by the conveyance with the current payload and first speed, wherein the transversal resonance position is determined based on the current payload and on the hoist speed; and reduce the first speed of the conveyance in a speed reduction zone which includes the transversal resonance position.
a storage unit; and a processing system;
wherein the storage unit comprises computer-executable components which when executed by the processing system causes the hoist drum control system to:
determine a current payload of the conveyance;
obtain a hoist speed of the hoist drum, corresponding to a first speed of the conveyance;
determine a transversal resonance position along the vertical rope portion of the rope to which the conveyance is attached, at which transversal resonance position transversal resonance is generated in the catenary when reached by the conveyance with the current payload and first speed, wherein the transversal resonance position is determined based on the current payload and on the hoist speed; and reduce the first speed of the conveyance in a speed reduction zone which includes the transversal resonance position.
10. A hoist drum control system as claimed in claim 9, wherein the processing system is configured to receive a first force measurement (F La) from a first load cell of a head sheave and a second force measurement (F Lb) from a second load cell of the head sheave, wherein the processing system is configured to determine a sum of force value by adding the first force measurement to the second force measurement, and wherein the processing system is configured to determine the current payload based on the sum of force value.
11. The hoist drum control system as claimed in claim 9, wherein the processing system is configured to determine the current payload is by subtracting the weight of the vertical rope portion, the weight of the conveyance and the weight of the head sheave from the sum of force value.
12. The hoist drum control system as claimed in any one of claims 9 to 11, wherein the processing system is configured to determine the transversal resonance position based on a resonance frequency of the catenary, a diameter (D) of the hoist drum, a frequency of an impulse in the rope occurring at cross-overs of Lebus grooves of a hoist drum, a length of the vertical rope portion from a centre axis (A) of the head sheave to a mine shaft opening, a weight of the conveyance, a rope weight per length unit, and the length of the catenary.
13. The hoist drum control system as claimed in any one of claims 10 to 12, wherein the processing system is configured to obtain the transversal resonance position from a look-up table which contains pre-calculated transversal resonance positions for a plurality of different current payloads and hoist speed combinations.
14. The hoist drum control system as claimed in any one of claims 10 to 13, wherein the processing system is configured to determine the speed reduction zone based on the hoist speed, wherein the processing system is configured to determine the speed reduction zone by retrieving a speed reduction zone that has been determined for the transversal resonance position and which has been determined based on catenary side force values which are proportional to a difference between a first force measurement measured by a first load cell and a second force measurement measured by a second load cell.
15. A mine drum hoist system comprising:
a hoist drum having Lebus grooves;
a head sheave;
a rope arranged to extend between the hoist drum and the head sheave to thereby define a catenary and a vertical rope portion;
a conveyance arranged to be attached to the vertical tope portion;
a motor (M) arranged to operate the hoist drum; and a hoist drum control system as defined in any of claims 10 to 14, arranged to control the motor (M).
a hoist drum having Lebus grooves;
a head sheave;
a rope arranged to extend between the hoist drum and the head sheave to thereby define a catenary and a vertical rope portion;
a conveyance arranged to be attached to the vertical tope portion;
a motor (M) arranged to operate the hoist drum; and a hoist drum control system as defined in any of claims 10 to 14, arranged to control the motor (M).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP15151282.9 | 2015-01-15 | ||
| EP15151282.9A EP3045415A1 (en) | 2015-01-15 | 2015-01-15 | A method of controlling transversal resonance in a catenary, a hoist drum control system and a mine drum hoist system |
| PCT/EP2015/080026 WO2016113064A1 (en) | 2015-01-15 | 2015-12-16 | A method of controlling transversal resonance in a catenary, a hoist drum control system and a mine drum hoist system |
Publications (2)
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| CA2973615A1 CA2973615A1 (en) | 2016-07-21 |
| CA2973615C true CA2973615C (en) | 2018-03-13 |
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| CA2973615A Active CA2973615C (en) | 2015-01-15 | 2015-12-16 | A method of controlling transversal resonance in a catenary, a hoist drum control system and a mine drum hoist system |
Country Status (9)
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| EP (2) | EP3045415A1 (en) |
| CN (1) | CN107001000B (en) |
| AU (1) | AU2015377923B2 (en) |
| CA (1) | CA2973615C (en) |
| PE (1) | PE20171116A1 (en) |
| PL (1) | PL3245153T3 (en) |
| RU (1) | RU2695755C2 (en) |
| WO (1) | WO2016113064A1 (en) |
| ZA (1) | ZA201702563B (en) |
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| CN107973195A (en) * | 2017-12-12 | 2018-05-01 | 中国矿业大学 | A kind of method that lifting system load-carrying is confirmed based on image recognition |
| CN110127502B (en) * | 2019-06-19 | 2023-10-27 | 重庆大学 | Transition device for rope winding and application method thereof |
| FI3922812T3 (en) * | 2020-06-10 | 2024-02-19 | Abb Schweiz Ag | Method of operating a mining hoist |
Family Cites Families (15)
| Publication number | Priority date | Publication date | Assignee | Title |
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| BE796461A (en) * | 1973-03-08 | 1973-09-10 | Inst Geotekhnicheskoi Mek Akad | DEVICE FOR PREVENTING THE BEAT OF BALANCING CABLES IN MINE EXTRACTION MACHINES |
| RU2072315C1 (en) * | 1990-09-18 | 1997-01-27 | Англо-Американ Корпорейшн ОФ САУТ Африка Лимитед | Drive motor control system of mine hoist cable drum and cable system |
| JPH06183654A (en) * | 1992-12-21 | 1994-07-05 | Nippon Otis Elevator Co | Speed controller of linear elevator |
| JPH07125945A (en) * | 1993-11-08 | 1995-05-16 | Mitsubishi Electric Corp | Control device for elevator |
| SE503754C2 (en) * | 1995-01-30 | 1996-08-26 | Asea Brown Boveri | Procedure and device for emergency stop of mining to prevent the occurrence of vertical oscillations |
| JPH10279201A (en) * | 1997-04-11 | 1998-10-20 | Hitachi Ltd | Damping control device for linear motor elevator |
| JP4716669B2 (en) * | 2004-05-12 | 2011-07-06 | 東芝エレベータ株式会社 | Elevator operation control device |
| JP4800793B2 (en) * | 2006-02-24 | 2011-10-26 | 三菱電機ビルテクノサービス株式会社 | Elevator control device |
| US7784590B2 (en) * | 2006-03-01 | 2010-08-31 | Mitsubishi Denki Kabushiki Kaisha | Elevator operation control device |
| CN101563285A (en) * | 2006-12-20 | 2009-10-21 | 奥蒂斯电梯公司 | Sway mitigation in an elevator system |
| CN101977835B (en) * | 2008-03-17 | 2014-09-10 | 奥蒂斯电梯公司 | Elevator dispatching control for sway mitigation |
| JP5842135B2 (en) * | 2011-12-15 | 2016-01-13 | パナソニックＩｐマネジメント株式会社 | Elevating device and elevating lighting apparatus provided with the same |
| FI123182B (en) * | 2012-02-16 | 2012-12-14 | Kone Corp | Method for controlling the lift and lift |
| US9828211B2 (en) * | 2012-06-20 | 2017-11-28 | Otis Elevator Company | Actively damping vertical oscillations of an elevator car |
| JP5791645B2 (en) * | 2013-02-14 | 2015-10-07 | 三菱電機株式会社 | Elevator device and rope swing suppression method thereof |
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- 2015-12-16 EP EP15813810.7A patent/EP3245153B1/en active Active
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- 2015-12-16 PL PL15813810T patent/PL3245153T3/en unknown
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Also Published As
| Publication number | Publication date |
|---|---|
| RU2017128819A3 (en) | 2019-02-15 |
| EP3045415A1 (en) | 2016-07-20 |
| AU2015377923A1 (en) | 2017-04-20 |
| PL3245153T3 (en) | 2019-10-31 |
| EP3245153A1 (en) | 2017-11-22 |
| AU2015377923B2 (en) | 2018-05-31 |
| EP3245153B1 (en) | 2019-04-17 |
| CN107001000B (en) | 2019-05-31 |
| CA2973615A1 (en) | 2016-07-21 |
| RU2017128819A (en) | 2019-02-15 |
| RU2695755C2 (en) | 2019-07-25 |
| ZA201702563B (en) | 2022-05-25 |
| PE20171116A1 (en) | 2017-08-07 |
| CN107001000A (en) | 2017-08-01 |
| WO2016113064A1 (en) | 2016-07-21 |
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