Elevator state monitoring device, state monitoring method, state monitoring program, and recording medium

Abstract

In this elevator state monitoring device, a wear state estimation unit has a tension acquisition unit, a parameter acquisition unit, and a wear difference calculation unit. The tension acquisition unit acquires discrete tension data that is tension values for each rope at a plurality of different car positions. The parameter acquisition unit acquires a plurality of parameters. The wear difference calculation unit calculates a relative wear difference between a plurality of rope grooves on the basis of the discrete tension data and the plurality of parameters.

Description

Elevator status monitoring device, status monitoring method, status monitoring program, and recording medium

[0001] The present disclosure relates to an elevator status monitoring device, a status monitoring method, a status monitoring program, and a recording medium.

[0002] In a conventional method for detecting abnormalities in elevator equipment, a tension measuring device is used to measure the tension of multiple ropes, and a pulley abnormality is detected based on the change in the measured tension from a uniform tension state after the initial stretch of each rope (see, for example, Patent Document 1).

[0003] Patent No. 6341896

[0004] In the conventional elevator equipment anomaly detection method described above, the presence or absence of differential wear between multiple rope grooves provided on a pulley is detected from changes in the tension of each rope. However, no consideration is given to specifically calculating the differential wear, and there is a need to more specifically grasp the degree of wear of each rope groove.

[0005] The present disclosure has been made to solve the above-mentioned problems, and aims to provide an elevator status monitoring device, status monitoring method, status monitoring program, and recording medium that can more accurately estimate the degree of wear of rope grooves without directly measuring the depth of each rope groove in a pulley.

[0006] The elevator condition monitoring device according to the present disclosure includes a wear condition estimation unit that estimates the wear condition of multiple rope grooves in a pulley around which multiple ropes that suspend a car and a counterweight are wound, and the wear condition estimation unit includes a tension acquisition unit that acquires discrete tension data, which is the tension value of each rope at multiple different car positions, a parameter acquisition unit that acquires multiple parameters including the rope lengths at the multiple car positions, and a wear difference calculation unit that calculates the relative wear difference between the multiple rope grooves based on the discrete tension data and the multiple parameters. In addition, the elevator status monitoring device according to the present disclosure includes a wear state estimation unit that estimates the wear state of multiple rope grooves in a pulley around which multiple ropes that suspend a car and a counterweight are wound, and the wear state estimation unit includes a tension acquisition unit that acquires discrete tension data, which is the tension value of each rope at multiple different car positions, a parameter acquisition unit that acquires multiple parameters including the rope lengths at the multiple car positions, and a wear difference determination unit that calculates the tension gradient of each rope based on the discrete tension data and the multiple parameters, and compares the tension gradients to determine the relative wear difference state between the multiple rope grooves. In addition, the elevator condition monitoring method according to the present disclosure includes a wear condition estimation step of estimating the wear conditions of multiple rope grooves in a pulley around which multiple ropes that suspend a car and a counterweight are wound, and the wear condition estimation step includes a tension acquisition step of acquiring discrete tension data that is the tension value of each rope at multiple different car positions, a parameter acquisition step of acquiring multiple parameters including the rope lengths at the multiple car positions, and a wear difference calculation step of calculating the relative wear differences between the multiple rope grooves based on the discrete tension data and the multiple parameters.In addition, the elevator condition monitoring method according to the present disclosure includes a wear condition estimation step of estimating the wear condition of multiple rope grooves in a pulley around which multiple ropes that suspend a car and a counterweight are wound, and the wear condition estimation step includes a tension acquisition step of acquiring discrete tension data that is the tension value of each rope at multiple different car positions, a parameter acquisition step of acquiring multiple parameters including the rope lengths at the multiple car positions, and a wear difference determination step of calculating the tension gradient of each rope based on the discrete tension data and the multiple parameters, and comparing the tension gradients to determine the relative wear difference condition between the multiple rope grooves.

[0007] According to the present disclosure, the degree of wear of rope grooves can be more accurately estimated without directly measuring the depth of each rope groove in a pulley.

[0008] 1 is a schematic configuration diagram showing an elevator according to a first embodiment.

[0023] FIG. 1 is a cross-sectional view of a main portion of the drive sheave of FIG. 1.

[0024] FIG. 2 is an explanatory diagram showing a state during a wear state inspection of the drive sheave in the elevator of FIG. 1.

[0025] FIG. 3 is a graph showing an example of the relationship between the car position and the tension of multiple main ropes.

[0026] FIG. 4 is a block diagram showing an elevator condition monitoring device according to a second embodiment.

[0027] FIG. 5 is an explanatory diagram showing an equivalent model of a rope passing over a pulley.

[0028] FIG. 6 is an explanatory diagram showing the equivalent model of FIG. 6 replaced with a model in a one-dimensional coordinate system.

[0029] FIG. 7 is an explanatory diagram showing the equivalent model of FIG. 6 divided into a winding-side portion and a paying-out side portion.

[0029] FIG. 8 is an explanatory diagram showing a model of the elevator of FIG. 1.

[0029] FIG. 9 is a graph showing the relationship between the tension of two main ropes and the car position when the depths of the two rope grooves are equal.

[0029] FIG. 10 is a graph showing the relationship between the tension of two main ropes and the car position when there is a 0.2 mm difference in the depths of the two rope grooves.

[0029] FIG. 11 is a graph showing a comparison of the relationship between the calculated tension of two main ropes and the car position with multiple measured values ​​when there is a 0.7 mm difference in the depths of the two rope grooves.

[0029] 22. is a block diagram showing an elevator state monitoring device according to embodiment 4. is a graph showing the relationship between car position and tension fluctuation when slippage occurs due to the tension ratio exceeding the limit traction ratio. is a flowchart showing the operation of the wear state estimating unit of FIG. 14. is a graph showing the relationship between car position and tension fluctuation when slippage occurs due to the tension ratio exceeding the limit traction ratio. is a block diagram showing an elevator state monitoring device according to embodiment 5. is a graph showing the relationship between tension and car position when the tensions of two main ropes are obtained at the same car position. is a graph showing the relationship between rope tension and car position when the tensions of two main ropes are obtained at different car positions. is a flowchart showing the operation of the wear state estimating unit of FIG. 18. is an explanatory diagram showing an example of the degree of wear of a plurality of rope grooves. is a graph showing the relationship between rope tension and car position corresponding to the degree of wear of FIG. 22. is an explanatory diagram showing the relationship between the wear state estimating unit and input / output data in embodiment 6. is a flowchart showing a part of the operation of the wear state estimating unit according to embodiment 6. is an explanatory diagram showing the relationship between the wear state estimating unit and input / output data in embodiment 7.10. A flowchart showing a part of the operation of the wear state estimating unit according to embodiment 8. A flowchart showing a part of the operation of the wear state estimating unit according to embodiment 9. An explanatory diagram showing the relationship between the wear state estimating unit and input / output data in embodiment 10. A configuration diagram showing a first example of a processing circuit that realizes each function of the condition monitoring devices according to embodiments 1 to 10. A configuration diagram showing a second example of a processing circuit that realizes each function of the condition monitoring devices according to embodiments 1 to 10.

[0009] Hereinafter, embodiments will be described with reference to the drawings. Embodiment 1. Fig. 1 is a schematic diagram showing an elevator according to embodiment 1. In the figure, a machine room 2 is provided above a hoistway 1. In the machine room 2, a hoisting machine 3 and an elevator control device 4 are installed.

[0010] The hoist 3 has a drive sheave 5 which is a pulley, a hoist motor (not shown), and a hoist brake (not shown). The hoist motor rotates the drive sheave 5. The hoist brake keeps the drive sheave 5 stationary. The hoist brake also brakes the rotation of the drive sheave 5.

[0011] A plurality of main ropes 6 are wound around the drive sheave 5. Only one main rope 6 is shown in Fig. 1. A car 7 is connected to first ends of the plurality of main ropes 6. A counterweight 8 is connected to second ends of the plurality of main ropes 6.

[0012] The car 7 and counterweight 8 are suspended by a plurality of main ropes 6 and move up and down in the elevator shaft 1 by rotating the drive sheave 5 .

[0013] The elevator control device 4 controls the operation of the car 7 by controlling the hoisting machine 3. The functions of the elevator control device 4 can be realized by a computer.

[0014] A control cable 9 is connected to the car 7. Power is supplied to the car 7 through the control cable 9. In addition, control signals are transmitted and received between the elevator control device 4 and the car 7 through the control cable 9.

[0015] A plurality of counter ropes 10 are suspended between the car 7 and the counter weight 8. Only one counter rope 10 is shown in Fig. 1. The counter ropes 10 compensate for the mass imbalance of the plurality of main ropes 6 on the car 7 side and the counter weight 8 side with respect to the hoisting machine 3.

[0016] A balancing wheel device (not shown) is provided at the bottom of the hoistway 1. The balancing wheel device applies tension to a plurality of balancing ropes 10.

[0017] Figure 2 is a cross-sectional view of a main portion of the drive sheave 5 of Figure 1. A plurality of rope grooves 5a are provided on the outer peripheral surface of the drive sheave 5. A corresponding main rope 6 is inserted into each rope groove 5a. The tension of the plurality of main ropes 6 is not necessarily uniform, but varies depending on the elongation of each main rope 6 itself, the wear state of the plurality of rope grooves 5a, etc.

[0018] If the tension difference between the multiple main ropes 6 becomes large, the strands constituting each main rope 6 may break or untwist, or the wires contained in each strand may wear or break, adversely affecting the life of each main rope 6. In addition, there is a risk that some of the multiple rope grooves 5a may wear out early.

[0019] Furthermore, if the difference in wear between the rope grooves 5a becomes large, a difference occurs in the amount of each main rope 6 that is let out relative to the rotation of the drive sheave 5, and the movement of the car 7 further increases the difference in tension between the multiple main ropes 6.

[0020] Therefore, it is important to detect and calculate the difference in wear between the rope grooves 5a early and accurately in order to extend the life of the drive sheave 5 and the main rope 6. However, depending on the installation state of the drive sheave 5, it may be difficult to directly measure the depth of each rope groove 5a while the main rope 6 is wound around it. It is also difficult to measure the average depth of each rope groove 5a as a whole.

[0021] In contrast to this, in the first embodiment, the difference in wear between the rope grooves 5a is calculated without directly measuring the depth of each rope groove 5a.

[0022] Figure 3 is an explanatory diagram showing a state during a wear state inspection of the drive sheave 5 in the elevator of Figure 1. In the wear state inspection, the tension of each main rope 6 is measured when the car 7 is stopped at a plurality of different positions. The tension of each main rope 6 is measured, for example, by an operator standing on the car 7 using a tension measuring device 11.

[0023] Methods for measuring tension include methods using temporary devices such as a hammering vibration method and a three-point bending method. Alternatively, a tension value measured by a tension measuring device permanently installed at the end of the main rope 6 may be used.

[0024] The multiple tension values ​​measured by the tension measuring device 11 are sent as discrete tension data to the condition monitoring device 21. The condition monitoring device 21 may be directly connected to the tension measuring device 11 or may be connected to the tension measuring device 11 via another device, for example, the elevator control device 4.

[0025] The status monitoring device 21 may also be installed remotely from the elevator, for example, in a server. In this case, the status monitoring device 21 may receive the discrete tension data via a communication network line.

[0026] The condition monitoring device 21 has, as a functional block, a wear state estimation unit 22. The wear state estimation unit 22 estimates the wear state of the drive sheave 5.

[0027] The wear state estimation unit 22 has, as functional blocks, a tension acquisition unit 23, a parameter acquisition unit 24, and a wear difference calculation unit 25. These functional blocks may be provided in one device or distributed across multiple devices. For example, only the tension acquisition unit 23 may be included in the elevator control device 4, and the other functions may be included in a server.

[0028] The tension acquisition unit 23 acquires discrete tension data. The parameter acquisition unit 24 acquires a plurality of parameters. The plurality of parameters includes the rope length, the specifications of the main rope 6, the pulley diameter, etc.

[0029] The rope length is the length of the main rope 6 at the car position where the tension of each main rope 6 was measured, i.e., the length of the portion of the entire length of the main rope 6 where the tension was measured. In the example of FIG. 3 , the rope length is the length from the portion of the main rope 6 that is withdrawn from the drive sheave 5 to the portion of the main rope 6 that is connected to the car 7. The rope length is measured, for example, using a laser distance meter or a steel ruler. The rope length can also be determined from design information and car position information.

[0030] The pulley diameter is the initial value of the diameter of the portion of the pulley around which the main rope 6 is wound, in which the tension is measured, that is, the diameter before wear.

[0031] As described above, the parameter acquisition unit 24 can acquire each parameter by using elevator design information, measuring on-site using a measuring device, or the like.

[0032] The wear difference calculation unit 25 calculates the relative wear difference between the rope grooves 5a based on the discrete tension data acquired by the tension acquisition unit 23 and the plurality of parameters acquired by the parameter acquisition unit 24. The relative wear difference between the rope grooves 5a is the difference in depth of another rope groove 5a relative to the depth of a reference rope groove 5a.

[0033] When calculating the difference in wear between the rope grooves 5a, the car 7 is stopped and the tension of each main rope 6 is measured. The position of the car 7 at this time is represented by x １ Next, the car 7 is run, and x １ The tension of each main rope 6 is measured with the car 7 stopped at a position different from x. ２ The discrete tension data obtained by the above operations is sent to the tension acquisition unit 23.

[0034] Also, car position x １ The rope length at ２ The rope length at this point is measured by an operator and sent to the parameter acquisition unit 24. The parameter acquisition unit 24 also receives input of the specifications of the main rope 6, the pulley diameter R, etc.

[0035] The wear difference calculation unit 25 calculates the wear difference between the rope grooves 5a based on the discrete tension data and a plurality of parameters. For example, when the first rope groove 5a out of n rope grooves 5a is used as a reference, the wear difference ΔR between the first rope groove 5a and the mth rope groove 5a is ｍ is obtained by the following formula:

[0036] ΔR ｍ = (R / Δx ｃ ){f(T １ (x ２ ), T ｍ (x ２ ), k(x ２ ))-f(T １ (x １ ), T ｍ (x １ ), k(x １ ))}

[0037] More specifically, the wear difference ΔR ｍ is obtained by the following formula:

[0038] ΔR ｍ = (R / Δx ｃ )[{(T ｍ (x ２ )-T １ (x ２ )) / k(x ２ )}-{(T ｍ (x １ )-T １ (x １ )) / k(x １ )}]

[0039] In addition, T １ is the discrete tension data of the main rope 6 hung in the first rope groove 5a. ｍ is the discrete tension data of the main rope 6 wound in the m-th rope groove 5a. R is the diameter of the drive sheave 5 at the position of the rope groove 5a before it is worn. Δx ｃ is the car position x １ Empty car position x ２ k is the spring constant of the main rope 6 at each car position.

[0040] Hereinafter, the main rope 6 hung in the first rope groove 5 a will be simply referred to as the first main rope 6 , and the main rope 6 hung in the mth rope groove 5 a will be simply referred to as the mth main rope 6 .

[0041] 4 is a graph showing an example of the relationship between the car position and the tension of the multiple main ropes 6. The tension of each main rope 6 can be expressed as a linear function, a quadratic function, or the like of the car position x using discrete tension data obtained by the tension acquisition unit 23.

[0042] It is desirable to acquire the discrete tension data at two or more car positions. By increasing the number of discrete tension data, the accuracy of the calculation of the wear difference can be improved.

[0043] When the tension acquisition unit 23 acquires three or more points of discrete tension data, the acquired tension values ​​may be linearly interpolated, and the wear difference may be calculated using tension values ​​at two points on the interpolated line.

[0044] Furthermore, the car position at which the discrete tension data is acquired may be the same for all main ropes 6 or may be different for each main rope 6 .

[0045] The elevator condition monitoring method of the first embodiment includes a wear state estimation step of estimating the wear state of the plurality of rope grooves 5 a. The wear state estimation step includes a tension acquisition step, a parameter acquisition step, and a wear difference calculation step.

[0046] The tension acquisition step is a step of acquiring discrete tension data. The parameter acquisition step is a step of acquiring a plurality of parameters. The wear difference calculation step is a step of calculating the relative wear difference between the plurality of rope grooves 5 a based on the discrete tension data and the plurality of parameters.

[0047] In such a condition monitoring device 21 and condition monitoring method, the tension acquisition unit 23 acquires discrete tension data, and the parameter acquisition unit 24 acquires a plurality of parameters. Then, the wear difference calculation unit 25 calculates the relative wear difference between the plurality of rope grooves 5 a based on the discrete tension data and the plurality of parameters.

[0048] Therefore, it is possible to more accurately calculate the difference in wear between the rope grooves 5a without directly measuring the depth of each rope groove 5a in the drive sheave 5. In other words, it is possible to more accurately estimate the degree of wear of each rope groove 5a.

[0049] Furthermore, the multiple parameters include the rope length at the car position where the discrete tension data was measured, as well as the specifications of the multiple main ropes 6 and the pulley diameter. This allows for even more accurate calculation of the wear difference between the rope grooves 5a.

[0050] The status monitoring program of the first embodiment is a program that causes a computer to execute the above-described status monitoring method.

[0051] Furthermore, the program is generally stored in a readable format in a storage medium, such as the memory 202 in Fig. 31. The processing described in the program read from the storage medium is then executed by a computer. The recording medium of the first embodiment is a computer-readable recording medium that stores an elevator status monitoring program that causes a computer to execute the above-described status monitoring method.

[0052] 5 is a block diagram showing an elevator status monitoring device 21 according to embodiment 2. The wear difference calculation unit 25 of embodiment 2 has a correction unit 26. The correction unit 26 calculates a correction parameter for correcting a change in the amount of elongation of each main rope 6 caused by the drive sheave 5 winding and letting out each main rope 6.

[0053] The wear difference calculation unit 25 calculates the wear difference between the plurality of rope grooves 5a using the correction parameters. ｍ is expressed by adding the correction parameter α ｍ It can be calculated by adding

[0054] ΔR ｍ = (R / Δx ｃ ){f(T １ (x ２ ), T ｍ (x２ ), k(x ２ ))-f(T １ (x １ ), T ｍ (x １ ), k(x １ ))+α ｍ}

[0055] The correction unit 26 calculates a correction parameter α ｍ where E is the Young's modulus of the main rope 6, and A is the cross-sectional area of ​​the main rope 6.

[0056] α ｍ = ∫g(T １ (x), T ｍ (x), E, ​​A) dx

[0057] In the wear difference calculation step of the second embodiment, the correction parameter α ｍ Calculate the correction parameter α ｍ The other configurations and the state monitoring method in the second embodiment are the same as those in the first embodiment.

[0058] In the condition monitoring device 21 and the condition monitoring method, a correction parameter is calculated to correct for the change in the amount of elongation of the main rope 6 caused by the drive sheave 5 winding the main rope 6, and the correction parameter is used to calculate the wear difference. This makes it possible to calculate the wear difference with even greater accuracy.

[0059] The status monitoring program of the second embodiment is a program that causes a computer to execute the processing of the status monitoring method by the status monitoring device 21 of the second embodiment. The recording medium of the second embodiment is a computer-readable recording medium that records an elevator status monitoring program that causes a computer to execute the status monitoring method by the status monitoring device 21 of the second embodiment.

[0060] Consider the simplest model, in which one rope is wound around one pulley. Figure 6 is an explanatory diagram showing an equivalent model of the rope passing over the pulley. Figure 7 is an explanatory diagram showing the equivalent model of Figure 6 replaced with a model in a one-dimensional coordinate system.

[0061] A rope model 51 is wound around a pulley model 50. The pulley model 50 rotates counterclockwise in the figure. The direction of movement of the rope model 51 is determined according to the direction of rotation of the pulley model 50. In particular, in the model of the rope model 51 in a one-dimensional coordinate system shown in Figure 7, the winding side portion and the unwinding side portion of the rope model 51 move in the same direction according to the direction of rotation of the pulley model 50.

[0062] 6 and 7, the rope model 51 is made up of three parts: a winding-up part, a letting-out part, and a part that moves integrally with the pulley model 50. More precisely, the part that moves integrally with the pulley model 50 is a part that is on the pulley model 50 and can move integrally with the pulley model 50.

[0063] In the following figures, the subscript i is added to variables relating to the winding side of the rope model 51, indicating that the variables are input side codes. The winding side is the upstream part of the rope model 51 relative to the pulley model 50 in the movement direction of the rope model 51.

[0064] Furthermore, the subscript o is added to the variables relating to the payout side portion of the rope model 51, signifying that they are codes on the output side. The payout side portion of the rope model 51 is the portion of the rope model 51 that is downstream of the pulley model 50 in the movement direction of the rope model 51.

[0065] When the rope model 51 is wound by a small amount Δx due to a small rotation of the pulley model 50, the amount Δx is expressed as the sum of the rope free length ΔLi and the rope elongation Δui. The rope free length ΔLi is the length when no tension is applied.

[0066] That is, the reeling amount Δx corresponds to the rope displacement amount when tension is applied, and is the sum of the rope free length ΔLi, which is the rope displacement amount when tension is not applied, and the rope elongation amount due to tension. As shown in Figure 7, the rope displacement amounts when tension is not applied for the reeling side portion, the unreeling side portion, and the portion that moves integrally with the pulley are all the same free rope length ΔLi.

[0067] Δx=ΔLi+Δui (1.1)

[0068] The rope elongation Δui in the winding-side portion can be calculated from the tension Ti in the winding-side portion. On the other hand, since the tension To in the unwinding-side portion is To, the rope elongation Δuo in the unwinding-side portion is different from the rope elongation Δui in the winding-side portion.

[0069] Therefore, the creep amount Δcr, which is the minute amount of slippage of the rope model 51 on the pulley model 50, is the rope elongation difference Δuo−Δui with respect to the rope free length ΔLi.

[0070] Δx+Δcr=(ΔLi+Δui)+(Δuo−Δui)=ΔLi+Δuo (1.2)

[0071] It has been experimentally confirmed using an actual machine that the lower end of the winding-side section and the lower end of the unwinding-side section exhibit the following behavior in relation to the handling of the rope elongation. In Figure 6, xi indicates the displacement of the lower end of the winding-side section, and xo indicates the displacement of the lower end of the unwinding-side section.

[0072] The lower end of the winding-side portion rises by an amount equal to the winding amount Δx of the rope model 51 on the pulley model 50. The lower end of the unwinding-side portion generally falls by an amount different from the winding amount Δx on the pulley model 50.

[0073] The minute winding amount Δx can be separated into the rope free length ΔLi and the rope stretch amount Δui. If the spring constant determined by the length of the winding side portion before winding is ki, after winding the length of the winding side portion becomes shorter by Δx, so the spring constant after winding changes to k'i. In this case, k'i > ki. In the following explanation, the spring constant may also be referred to as rope stiffness.

[0074] Figure 8 is an explanatory diagram showing the equivalent model of Figure 6 divided into a winding-side portion and a supply-side portion. In Figure 8, the winding-side portion and the supply-side portion are modeled as independent springs. This makes it possible to consider the balance of force with respect to the spring force, i.e., tension, determined by the difference in displacement between the two ends of each spring.

[0075] In Figure 8, yi represents the displacement of the upper end of the winding-side portion, and yo represents the displacement of the upper end of the unwinding-side portion. The relational expression for the winding-side portion when stationary, i.e., before winding, is given by the following equation:

[0076] Ti=ki(yi-xi)=(EA / Li)(0-x'i) (1.3)

[0077] Here, ki is the rope stiffness of the winding side portion, yi is the displacement of the upper end of the winding side portion, xi is the displacement of the lower end of the winding side portion, Li is the length of the winding side portion, E is the Young's modulus of the rope model 51, and A is the cross-sectional area of ​​the cross section perpendicular to the longitudinal direction of the rope model 51.

[0078] Furthermore, x'i is the initial elongation of the lower end of the take-up side section, which is a negative value. In this case, the coordinate system is defined such that upward displacement is positive. The rope stiffness ki of the take-up side section is a function of Young's modulus E, cross-sectional area A, and the length Li of the take-up side section.

[0079] The winding-side portion is wound around the pulley model 50 while being subjected to tension Ti, and the following relational expression is obtained:

[0080] Ti=(EA / ΔLi)Δui (1.4)

[0081] When the take-up side portion is wound up by a small amount Δx on the pulley model 50, the bottom end of the take-up side portion rises by Δx, as shown in Figure 7, regardless of the rope stiffness. Therefore, the balance of forces after the rope has been wound up by Δx is given by the following equation.

[0082] Ti=(EA / (Li-ΔLi))(yi-xi) =(EA / (Li-ΔLi)){yi-(x'i+Δx)} (1.5)

[0083] The tension Ti in the take-up side portion is calculated from the difference in displacement yi-xi between the upper and lower ends of the take-up side portion. From this equation, a relational expression that must be satisfied by the displacement yi of the upper end of the take-up side portion is obtained.

[0084] yi=(Ti / EA)(Li-ΔLi)+x'i+Δx (1.6)

[0085] By rearranging the above equation using equations (1.1), (1.3), and (1.4), the following equation is obtained.

[0086] yi=(Ti / EA)(Li-ΔLi)-(Ti / EA)Li+ΔLi+Δui =-(Ti / EA)ΔLi+ΔLi+Δui =-Δui+ΔLi+Δui=ΔLi (1.7)

[0087] Therefore, the displacement yi of the upper end of the winding side portion during minute winding is not the winding amount Δx, i.e., ΔLi + Δui, but needs to be the rope free length ΔLi of the winding amount Δx. As a result, the displacement xi of the lower end of the winding side portion becomes the winding amount Δx.

[0088] Next, consider the behavior of two winding-side sections that are subjected to different tensions. In an actual elevator, the lower ends of the two winding-side sections are connected to the car 7 or the counterweight 8, and the displacement amounts are the same. Therefore, the winding-side section that is subjected to tension Ti1, which is smaller than tension Ti2, has its lower end pulled up excessively, causing slack and a decrease in tension. On the other hand, the winding-side section that is subjected to tension Ti2 has its lower end pulled down, increasing tension.

[0089] In the model used in this study, the amount of lift at the upper ends of the two take-up side sections is not a uniform Δx, but is different from each other, being the free rope lengths ΔLi1 and ΔLi2 on the pulley model 50 according to the tension. By correcting this amount of lift, the amount of displacement at the lower ends of the two take-up side sections is both Δx.

[0090] Next, the feed-side portion will be described. From FIG. 8, the relational expression for the feed-side portion when stationary is as follows:

[0091] To=ko(yo-xo)=(EA / Lo)(0-x'o) (1.8)

[0092] Here, ko is the rope stiffness of the reeling side portion, yo is the displacement of the upper end of the reeling side portion, xo is the displacement of the lower end of the reeling side portion, Lo is the length of the reeling side portion, E is the Young's modulus of the rope model 51, and A is the cross-sectional area of ​​the cross section perpendicular to the longitudinal direction of the rope model 51.

[0093] Furthermore, x'o is the initial elongation amount of the lower end of the payout side portion, and is a negative value. The rope stiffness ko of the payout side portion is a function of Young's modulus E, cross-sectional area A, and length Lo of the payout side portion.

[0094] When the winding-side portion is wound by Δx, the feeding-side portion becomes longer by the free length ΔLi of the rope on the pulley model 50. Also, due to the tension To of the feeding-side portion, the free length ΔLi of the rope of the feeding-side portion is extended by Δuo.

[0095] To=(EA / ΔLi)Δuo (1.9)

[0096] Therefore, when the rope model 51 is wound up slightly by Δx on the pulley model 50, the lower end of the payout side portion is displaced downward by ΔLi+Δuo. The balance of forces in the payout side portion after being wound up by Δx is given by the following equation.

[0097] To=(EA / (Lo+ΔLi))(yo-xo) =(EA / (Lo+ΔLi)){ yo-(x'o-ΔLi-Δuo)} (1.10)

[0098] The tension To of the payout side portion is calculated from the difference in displacement between the upper and lower ends of the payout side portion (y-x). From this equation, a relational expression that must be satisfied by the displacement yo of the upper end of the payout side portion is obtained.

[0099] yo=(To / EA)(Lo+ΔLi)+x'o−ΔLi−Δuo (1.11)

[0100] The above equation is rearranged using equations (1.11), (1.8), and (1.9).

[0101] yo=(To / EA)(Lo+ΔLi)-(To / EA)Lo-ΔLi-Δuo =(To / EA)ΔLi-ΔLi-Δuo =Δuo-ΔLi-Δuo=-ΔLi (1.12)

[0102] From this equation, the displacement yo of the upper end given to the rope stiffness ko of the payout side portion needs to be the free rope length - ΔLi of the payout amount, not the reeled amount - Δx. As a result, the displacement xo of the lower end of the payout side portion becomes the payout amount ΔLi + Δuo.

[0103] The displacement Δxi of the lower end of the winding-side portion is ΔLi+Δui, whereas the displacement xo of the lower end of the unwinding-side portion is ΔLi+Δuo. This difference is the creep amount Δcr of the rope model 51 on the pulley model 50.

[0104] Δcr=Δuo-Δui=(ΔLi / EA)(To-Ti) (1.13)

[0105] The discussion so far has been on the formulation for the case where the pulley model 50 rotates counterclockwise in Fig. 6, as shown in Fig. 6. On the other hand, when considering the relational equation for the case where the pulley model 50 rotates clockwise in Fig. 6, the counterclockwise relational equation can be used as is by defining the winding amount Δx as a negative value. However, since the tension in the winding side portion is To in Fig. 6, it is necessary to replace Ti in equation (1.4) with To in Fig. 6.

[0106] 6 shows a configuration in which the rope model 51 is wound around the upper part of the pulley model 50 and pulled downward. However, the derived relational expression remains unchanged in a configuration in which the rope model 51 is wound around the lower part of the pulley model 50 and pulled upward.

[0107] Based on the above results, the model of winding the rope model 51 around the pulley model 50 can be organized as follows:

[0108] Counterclockwise rope displacement on the pulley model 50 is positive, and clockwise rope displacement is negative, and the sign of the winding amount Δx is set according to the direction of rotation. The rope stiffness ki of the winding side portion is defined as the product of Young's modulus E and cross-sectional area A of the rope model 51 divided by the length Li of the winding side portion. The rope stiffness ko of the unwinding side portion is defined as the product of Young's modulus E and cross-sectional area A of the rope model 51 divided by the length Lo of the unwinding side portion. The lengths Li and Lo when calculating the rope stiffness ki and ko are set to the free length of the rope when no tension is acting on the rope model 51.

[0109] The tension Ti on the winding side is defined as the rope stiffness ki multiplied by the difference in displacement between the upper and lower ends yi-xi. The tension To on the unwinding side is defined as the rope stiffness ko multiplied by the difference in displacement between the upper and lower ends yo-xo.

[0110] The displacement of the end of the pulley model 50 side in the winding side portion is defined as the value obtained by excluding the rope elongation amount Δui of the winding side portion from the minute winding amount Δx of the rope model 51 on the pulley model 50, and corresponds to the free length ΔLi of the rope for the winding amount Δx. The displacement of the end of the pulley model 50 side in the unwinding side portion is defined as the value obtained by excluding the rope elongation amount Δui of the winding side portion from the minute winding amount Δx of the rope model 51 on the pulley model 50, and corresponds to the free length ΔLi of the rope for the winding amount Δx. The rope elongation amount on the pulley model 50 is calculated from the tension Ti of the winding side portion.

[0111] Next, Fig. 9 is an explanatory diagram showing a model of the elevator in Fig. 1. Fig. 9 shows the simplest model, which is a 1:1 roping system with one rope.

[0112] Each element of the elevator is modeled as a spring and mass system. The main rope 6 is modeled as a mass element on the drive sheave 5, and as a spring element on the take-up and pay-out sides.

[0113] In Figure 9, Js is the moment of inertia of the drive sheave 5. Jr is the moment of inertia of the main rope 6 on the drive sheave 5. Jr is the moment of inertia due to the mass of the part of the main rope 6 that moves integrally with the drive sheave 5.

[0114] Mc is the mass of the car 7. Mw is the mass of the counterweight 8. msc is the mass of the car side shackle. msw is the mass of the counterweight side shackle. The car side shackle and the counterweight side shackle are omitted in FIG. 1 .

[0115] mrc is the mass of the car side portion of the main ropes 6. mrw is the mass of the counterweight side portion of the main ropes 6. The car side portion is the portion of the main ropes 6 located closer to the car 7 than the drive sheave 5. The counterweight side portion is the portion of the main ropes 6 located closer to the counterweight 8 than the drive sheave 5. The above are parameters related to inertia elements.

[0116] ksc is the stiffness of the car side shackle. ksw is the stiffness of the counterweight side shackle. krc is the stiffness of the car side portion of the main rope 6. krw is the stiffness of the counterweight side portion of the main rope 6. These are parameters related to stiffness elements.

[0117] θs is the rotation angle of the drive sheave 5. θr is the rotation angle of the main rope 6 on the drive sheave 5. xc is the displacement of the car 7. xw is the displacement of the counterweight 8. xsc is the displacement of the car side shackle. xsw is the displacement of the counterweight side shackle. xrc is the displacement of the car side portion of the main rope 6. xrw is the displacement of the counterweight side portion of the main rope 6.

[0118] The equation of motion expressed as a differential equation that does not take into account the damping term due to the damping element is as follows: Here, d^2 / dt^2 is used as the operator indicating the second-order differentiation operation with respect to time t.

[0119] Mc(d^2 / dt^2)xc-ksc(xsc-xc)=-Mc g (1.14)

[0120] Mw(d^2 / dt^2)xw-ksw(xsw-xw)=-Mw g (1.15)

[0121] msc(d^2 / dt^2)xsc+ksc(xsc-xc)-krc(xrc-xsc) =-msc g (1.16)

[0122] msw(d^2 / dt^2)xsw+ksw(xsw-xw)-krw(xrw-xsw) =-msw g (1.17)

[0123] mrc(d^2 / dt^2)xrc+krc(xrc-xsc)-krc(-R １ θr-xrc) =-mrc g (1.18)

[0124] mrw(d^2 / dt^2)xrw+krw(xrw-xsw)-krw(R １ θr−xrw) =−mrw g (1.19)

[0125] Js(d^2 / dt^2)θs=τ−λ (1.20)

[0126] Jr(d^2 / dt^2)θr−krcR １ (-R １ θr−xrc)+krwR １ (R １ θr−xrw) = λ (1.21)

[0127] In addition, R １ is the radius of the drive sheave 5. g is the acceleration due to gravity. τ is the drive torque applied to the drive sheave 5. λ is the restraint torque acting between the drive sheave 5 and the main rope 6.

[0128] On the drive sheave 5, the drive sheave 5 and the main rope 6 move together within the range of a limit traction ratio Γ. The limit traction ratio Γ is given as a function of the coefficient of friction between the drive sheave 5 and the main rope 6 and the winding angle of the main rope 6 around the drive sheave 5.

[0129] In this case, the condition for satisfying the ratio of the tension Ti of the take-up side portion of the main rope 6 to the tension To of the pay-out side portion, and the constraint condition equation, are given by the following equation. Here, d / dt is used as the operator indicating the first-order differentiation operation with respect to time t.

[0130] (1 / Γ)<(To / Ti)<Γ (1.22)

[0131] (d / dt)θs−(d / dt)θr=0 (1.23)

[0132] The restraining torque λ acts on the drive sheave 5 and the main rope 6 as a force that satisfies the above equation. On the other hand, when the tension ratio To / Ti exceeds the limit traction ratio Γ, a frictional force acts and the main rope 6 slips relative to the drive sheave 5, resulting in a difference in rotational speed between the drive sheave 5 and the main rope 6.

[0133] (d / dt)θs−(d / dt)θr≠0 (1.24)

[0134] Below, we will explain the behavior of the car 7 when it descends, that is, when the drive sheave 5 rotates counterclockwise in Figure 9. We will consider the balanced state at time t+Δt, after an infinitesimal time Δt has elapsed, from the balanced state at time t. When the car 7 descends during the infinitesimal time Δt, the amount of winding Δx on the drive sheave 5 is given by the following equation.

[0135] Δx=R １ Δθr=ΔL+Δu (1.25)

[0136] Here, ΔL is the free length of the rope relative to the minute winding amount Δx when the car 7 is lowered, i.e., the length of the rope when no tension is applied. Also, Δu is the amount of rope elongation relative to the minute winding amount Δx when the car 7 is lowered.

[0137] Each rope groove 5a is worn down over time by the main rope 6. Radius R １ is the radius of the drive sheave 5 in each rope groove 5a. Therefore, if the amount of wear in the multiple rope grooves 5a is different from one another, the radius R １ will be slightly different.

[0138] Such a radius R １ The difference in the amount of winding causes a difference in the amount of winding, resulting in a difference in tension between the multiple main ropes 6.

[0139] If the tension acting on the counterweight side portion of the main rope 6 is Tw, Δu satisfies the following equation.

[0140] Tw=(EA / ΔL)Δu → Δu=(Tw / EA)ΔL (1.26)

[0141] Therefore, the free length ΔL of the rope can be calculated from the minute winding amount Δx.

[0142] Δx=(1+(Tw / EA))ΔL → ΔL=Δx / (1+(Tw / EA)) (1.27)

[0143] From this equation, the length Lc of the car side portion of the main rope 6 and the length Lw of the counterweight side portion of the main rope 6 are given by the following equations, respectively.

[0144] Lo(t+Δt)=Lc(t+Δt)=Lc(t)+ΔL, Li(t+Δt)=Lw(t+Δt)=Lw(t)−ΔL (1.28)

[0145] The winding amount at time t+Δt, the corresponding free length of the rope, and the rope stretch amount are given by the following equations, respectively.

[0146] x(t+Δt)=x(t)+Δx, L(t+Δt)=L(t)+ΔL, u(t+Δt)=u(t)+Δu (1.29)

[0147] The amount x(t+Δt)=Rθr(t+Δt) taken up by the drive sheave 5 includes the amount of rope stretch. However, in order to calculate the tension generated in the take-up side portion of the main rope 6 and the tension generated in the pay-out side portion of the main rope 6, it is necessary to use Rθr as the free length L of the rope rather than using it as the take-up amount.

[0148] The free length L of the rope can be calculated using the following formula:

[0149] x(t+Δt)=R １ θr(t+Δt) =L(t+Δt)+u(t+Δt) → L=R １ θr−u (1.30)

[0150] Therefore, the tension Ti generated in the winding side portion of the main rope 6 is given by the following equation.

[0151] Ti=Tw=ki(L-xrw) =krw(L-xrw)=krw(R １ θr-u-xrw) (1.31)

[0152] The tension To generated in the payout side portion of the main rope 6 is given by the following formula.

[0153] To=ko(-L-xrc) =krc(-L-xrc)=krc(-R １ θr+u−xrc) (1.32)

[0154] From these equations, the winding amounts in the equations of motion (1.18), (1.19), and (1.21) are modified as follows:

[0155] R １ θr → R １ θr−u (1.33)

[0156] Next, the behavior when the car 7 ascends, that is, when the drive sheave 5 rotates clockwise in Fig. 8 will be described. When the car 7 ascends in an infinitesimal time Δt, the amount of winding Δx on the drive sheave 5 is given by the following equation. Note that since the counterclockwise direction in Fig. 8 is considered positive, when the drive sheave 5 rotates clockwise in Fig. 8, the amount of winding Δx becomes a negative value.

[0157] Δx=R１ θr=ΔL+Δu (1.34)

[0158] Here, Δu is the amount of rope stretch relative to the minute amount of winding Δx when the car 7 is rising, and is a negative value.

[0159] If the tension acting on the car side portion of the main rope 6 is Tc, Δu satisfies the following equation.

[0160] Tc=(EA / ΔL)Δu → Δu=(Tc / EA)ΔL (1.35)

[0161] Therefore, the free length ΔL of the rope can be calculated from the minute winding amount Δx.

[0162] Δx=(1+(Tc / EA))ΔL → ΔL=Δx / (1+(Tc / EA)) (1.36)

[0163] From this equation, the length Lc of the car side portion of the main rope 6 and the length Lw of the counterweight side portion of the main rope 6 are given by the following equations, respectively.

[0164] Li(t+Δt)=Lc(t+Δt)=Lc(t)+ΔL, Lo(t+Δt)=Lw(t+Δt)=Lw(t)−ΔL (1.37)

[0165] Here, since the free length ΔL is a negative value, the rope length on the car side decreases and the rope length on the counterweight side increases.

[0166] The free length L of the rope when the car 7 is rising can be calculated by the following formula.

[0167] x(t+Δt)=R １ θr(t+Δt) =L(t+Δt)+u(t+Δt) → L=R １ θr−u (1.38)

[0168] Therefore, the tension Ti generated in the winding side portion of the main rope 6 is given by the following equation.

[0169] Ti=Tc=ki(-L-xrc) =krc(-L-xrc)=krc(-R １ θr+u−xrc) (1.39)

[0170] The tension To generated in the payout side portion of the main rope 6 is given by the following formula.

[0171] To=ko(L-xrw)=krw(L-xrw)=krw(R １ θr-u-xrw) (1.40)

[0172] From these equations, the winding amounts in the equations of motion (1.18), (1.19), and (1.21) are modified as follows:

[0173] R １ θr → R １ θr−u (1.41)

[0174] From the above results, the tension model as a generalized model of rope winding can be defined as follows: In this specification and claims, the analytical model for rope tension will be simply called the tension model.

[0175] Regardless of the direction of travel of the car 7, the rope length Lc on the car 7 side and the rope length Lw on the counterweight 8 side can be obtained by the following equations. That is, the length of the winding side portion and the length of the unwinding side portion are calculated from the free rope length ΔL.

[0176] Lc(t+Δt)=Lc(t)+ΔL, Lw(t+Δt)=Lw(t)−ΔL (1.42)

[0177] Here, ΔL satisfies the following equation:

[0178] When the car is descending: ΔL = (1.27), when the car is ascending: ΔL = (1.36) (1.43)

[0179] The winding amount parts in the equations of motion (1.18), (1.19), and (1.21) are modified as follows:

[0180] R １ θr → L=R １ θr−u (1.44)

[0181] As shown in equations (1.27) and (1.36), the free length ΔL of the rope is a function of the winding amount Δx and the tension Ti of the winding side portion.

[0182] Here, the relational expression of the correction amount u over a very short time period is as follows:

[0183] u(t+Δt)=u(t)+Δu (1.45)

[0184] When the car descends: Δu = (1.26), when the car ascends: Δu = (1.35) (1.46)

[0185] As shown in equations (1.26) and (1.35), the rope elongation Δu is a value proportional to the rope free length ΔL and the tension Ti of the winding side portion.

[0186] The above relational expressions also hold true when there is one or more pulleys other than the drive sheave 5, which is a sheave, and also hold true regardless of the number of main ropes 6.

[0187] Next, as an example, calculation results are shown for an elevator using a 1:1 roping system in which two main ropes 6 are wound around the drive sheave 5 in a single-wrap manner. In the calculations below, the tensions of the two main ropes 6 are found by changing the car position when the depths of the two rope grooves 5a are equal and when they are different.

[0188] Fig. 10 is a graph showing the relationship between the tension of the two main ropes 6 and the car position when the two rope grooves 5a have the same depth. Fig. 11 is a graph showing the relationship between the tension of the two main ropes 6 and the car position when there is a difference of 0.2 mm in the depths of the two rope grooves 5a. Fig. 12 is a graph showing the relationship between the calculated values ​​of the tension of the two main ropes 6 and the car position, comparing them with multiple actual measured values ​​when there is a difference of 0.7 mm in the depths of the two rope grooves 5a.

[0189] 10, 11, and 12, the car 7 travels back and forth between the top floor and the bottom floor. Car1 indicates the tension in the car-side portion of one main rope 6. Car2 indicates the tension in the car-side portion of the other main rope 6.

[0190] CWT1 indicates the tension of the counterweight side portion of one main rope 6. CWT2 indicates the tension of the counterweight side portion of the other main rope 6. The measured values ​​of each tension are values ​​obtained by measuring the tension acting on the shackle spring.

[0191] When the depths of the two rope grooves 5a are equal to each other, the tension exhibits a constant value regardless of the car position, as shown in FIG.

[0192] On the other hand, the fact that the depths of the two rope grooves 5a are different from each other means that the radius R of the drive sheave 5 in the equation of motion １ This corresponds to the fact that the depth of each main rope 6 is different. When there is a difference in the depth of the two rope grooves 5a, the tension when the car 7 is ascending and the tension when it is descending will trace different trajectories, as shown in Figure 11. In Figure 11, the rope grooves 5a corresponding to Car2 and CWT2 are deeper than the rope grooves 5a corresponding to Car1 and CWT1.

[0193] If the winding amount were calculated using a model that did not take rope elongation into account, even if the groove depth were the same, the tension would change with changes in the car position due to differences in the initial elongation of the rope, which represents a deviation in the initial tension.As a result, the results would differ from the actual tension behavior, where the tension does not change with car position.

[0194] When the difference in depth between the two rope grooves 5a becomes large, the tension ratio between the winding side portion and the unwinding side portion exceeds the limit traction ratio Γ, the main rope 6 slips relative to the drive sheave 5, and the gradient of the tension fluctuation changes midway, as shown in Figure 12. Figure 12 shows that the analysis method of embodiment 1 makes it possible to accurately calculate tension fluctuation, including rope slippage behavior.

[0195] Since the limit traction ratio Γ is a function of the coefficient of friction between the drive sheave 5 and the main rope 6, if the coefficient of friction changes, the limit traction ratio Γ also changes. This change in the limit traction ratio Γ appears as a shift in the inflection point where the gradient of the tension fluctuation changes. Therefore, by understanding the amount of shift in this inflection point, it is possible to determine the amount of fluctuation in the friction coefficient.

[0196] Here, in the second embodiment, the correction parameter α ｍ The tension values ​​included in the discrete tension data used in are obtained by measuring the tension of the winding side portion of each main rope 6 relative to the drive sheave 5. This is because, when the measured value of the unwinding side portion is used, the calculation accuracy is reduced due to the presence of minute slippage caused by the tension difference between the inlet side and outlet side of the drive sheave 5.

[0197] Specifically, in an elevator using a 1:1 roping system as shown in FIG. 3, when measuring the tension of the main rope 6 on the car 7 side, it is sufficient to measure the tension of the main rope 6 when the car 7 is ascending.

[0198] Furthermore, it is desirable that one of the car positions where tension is measured be the lowest floor position. This is because the tension ratio between the winding side and the unwinding side is unlikely to exceed the limit traction ratio Γ. Also, when measuring tension using the percussion method, the longer the rope length, the higher the accuracy of tension measurement.

[0199] That is, it is desirable to obtain the tension value contained in the discrete tension data by measuring the tension at the car position where the rope length is at its maximum, and then measuring the tension at the car position where the rope length is shorter than the maximum.

[0200] Third Embodiment Next, Fig. 13 is a schematic diagram showing an elevator according to a third embodiment. The elevator according to the third embodiment is a mechanical elevator of a 2:1 roping system. A hoisting machine 3 is installed at the top of the hoistway 1. Although omitted in Fig. 13, an elevator control device 4 is installed within the hoistway 1.

[0201] The car 7 is provided with a car hoisting sheave 7a which is a pulley. The counterweight 8 is provided with a counterweight hoisting sheave 8a which is a pulley.

[0202] A car side rope stopper 12 and a counterweight side rope stopper 13 are installed at the top of the hoistway 1. A first end of each main rope 6 is connected to the car side rope stopper 12. A second end of each main rope 6 is connected to the counterweight side rope stopper 13.

[0203] Each main rope 6 is wound around the car sheave 7a, the drive sheave 5, and the counterweight sheave 8a in that order from the first end side.

[0204] The main rope 6 has a first portion 6a, a second portion 6b, a third portion 6c, and a fourth portion 6d. The first portion 6a is the portion between the car side rope stopper 12 and the car sheave 7a. The second portion 6b is the portion between the car sheave 7a and the drive sheave 5. The third portion 6c is the portion between the drive sheave 5 and the counterweight sheave 8a. The fourth portion 6d is the portion between the counterweight sheave 8a and the counterweight side rope stopper 13.

[0205] The configuration of the state monitoring device 21 is the same as that of the state monitoring device 21 of the second embodiment shown in FIG.

[0206] Here, the pulley closest to the first end or the second end of the multiple main ropes 6 is referred to as the first pulley, and the pulley located next to the first pulley is referred to as the second pulley. When the multiple main ropes 6 are wound around two or more pulleys, the wear difference in the first pulley is calculated, and then the wear difference in the second pulley is calculated using the difference in payout amount due to the wear difference in the first pulley and the tension change due to minute slippage on the first pulley.

[0207] In the portion of the main rope 6 between the pulleys, for example, the second portion 6b, in addition to the change in the amount of elongation due to winding and unwinding by the pulley, minute slippage occurs due to the difference in tension between the entrance and exit sides of the pulley.

[0208] For this reason, when calculating the difference in wear in the drive sheave 5, it is necessary to consider not only the drive sheave 5 but also the difference in payout amount due to the difference in wear in the car sheave 7a, and tension changes due to slight slippage on the car sheave 7a. In this case, the first pulley is the car sheave 7a, and the second pulley is the drive sheave 5. Also, the rope length in this case is the length of the portion of the main rope 6 between the car sheave 7a and the drive sheave 5.

[0209] When the car 7 is raised, the relative value β of the minute slippage occurring in the m-th main rope 6 relative to the minute slippage occurring in the first main rope 6 on the car hoisting wheel 7a ｍ is calculated by the following formula:

[0210] β ｍ = ∫ h(T ｍ (x), T １ (x), T ｍ '(x),T １ '(x),E,A)dx

[0211] In addition, T １ (x) is the tension in the second portion 6b of the first main rope 6. T ｍ (x) is the tension in the second portion 6b of the mth main rope 6;

[0212] T １ '(x) is the tension of the first portion 6a of the first main rope 6. T ｍ '(x) is the tension of the first portion 6a of the m-th main rope 6. T １ (x), T ｍ (x), T １ '(x), and T ｍ '(x) are each expressed as a function of car position x.

[0213] Wear difference ΔR in the cage hoist 7a ｍ The difference in the feed rate due to ' and the relative value of micro-slip β ｍ and the wear difference ΔR in the drive sheave 5 ｍ is calculated by the following formula:

[0214] ΔR ｍ = (R / Δx ｃ ){f(T １ (x ２ ), T ｍ (x ２ ), k(x ２ ))-f(T １ (x １ ), T ｍ (x １ ), k(x １ ))+α ｍ +β ｍ +(ΔR ｍ ' / R ｍ ')Δx ｃ}

[0215] The difference in wear in the counterweight sheave 8a can be calculated using the discrete tension data of the fourth portion 6d of each main rope 6. In this case, the difference in wear in the drive sheave 5 can also be calculated by regarding the counterweight sheave 8a as the first pulley and the drive sheave 5 as the second pulley.

[0216] In addition, the wear difference in the counterweight hoisting sheave 8 a can also be calculated using the discrete tension data of the second portion 6 b, the discrete tension data of the third portion 6 c, and the wear difference in the drive sheave 5.

[0217] According to the state monitoring device 21 and state monitoring method, in an elevator having a plurality of pulleys, the difference in wear among the pulleys can be calculated more accurately.

[0218] In addition, when multiple ropes are wound around two or more pulleys, after calculating the wear difference in the first pulley, the wear differences in the pulleys other than the first pulley can be estimated from the wear difference in the first pulley using a correction coefficient obtained from the pulley information of each pulley. The pulley information includes at least one of the groove surface pressure, hardness, groove coefficient, and rotation speed of each pulley.

[0219] Even with this method, the difference in wear can be calculated using the change in tension due to the movement of the target pulley for which the difference in wear is to be calculated and the movement of a pulley located adjacent to the target pulley.

[0220] In addition, in FIG. 13, the car hoisting sheave 7a is provided on the upper part of the car 7, but a plurality of car hoisting sheaves 7a may be provided on the lower part of the car 7.

[0221] Alternatively, the hoist 3 may be installed at the bottom of the elevator shaft 1, and the car return wheel as a pulley and the counterweight return wheel as a pulley may be installed at the top of the elevator shaft 1.

[0222] The elevator may also be an elevator that uses a deflector pulley as a pulley.

[0223] The status monitoring program of the third embodiment is a program that causes a computer to execute the processing of the status monitoring method by the status monitoring device 21 of the third embodiment. The recording medium of the third embodiment is a computer-readable recording medium that records an elevator status monitoring program that causes a computer to execute the status monitoring method by the status monitoring device 21 of the third embodiment.

[0224] 14 is a block diagram showing an elevator status monitoring device 21 according to a fourth embodiment. The wear difference calculation unit 25 of the fourth embodiment has a traction limit determination unit 27. As described above, when the tension ratio To / Ti exceeds the limit traction ratio Γ, the main rope 6 slips relative to the drive sheave 5 while a frictional force is applied.

[0225] 15 is a graph showing the relationship between car position and tension fluctuation when slippage occurs due to the tension ratio To / Ti exceeding the limit traction ratio Γ. The condition under which slippage does not occur due to the tension ratio To / Ti exceeding the limit traction ratio Γ is as shown in equation (1.22) above. However, the tensions To and Ti are obtained at the same car position.

[0226] If the tension ratio To / Ti deviates from the range of equation (1.22), the main ropes 6 slip on the drive sheave 5 so that the tension ratio To / Ti maintains the limit traction ratio Γ. Therefore, the tension of each main rope 6 varies discontinuously with respect to the car position.

[0227] The calculation of the wear difference in the first to third embodiments does not take into account the case where the tension ratio To / Ti exceeds the limit traction ratio Γ. For this reason, when calculating the wear difference, it is necessary to use discrete tension data acquired at a car position where the tension ratio To / Ti does not exceed the limit traction ratio Γ.

[0228] The traction limit determination unit 27 of the fourth embodiment determines whether the tension ratio To / Ti satisfies the condition of formula (1.22). That is, the traction limit determination unit 27 determines whether the tension ratio To / Ti between the inlet side and the outlet side of the pulley in the main rope 6 has reached the limit traction ratio Γ.

[0229] Fig. 16 is a flowchart showing the operation of the wear state estimation unit 22 in Fig. 14. In step S101, the wear state estimation unit 22 acquires discrete tension data of the first portion 6a and the second portion 6b at the same car position.

[0230] Next, in step S102, the wear state estimation unit 22 calculates the tension ratio between the first portion 6a and the second portion 6b. Then, in step S103, it is determined whether the tension ratio satisfies the condition of equation (1.22). The processes of steps S102 and S103 are executed by the traction limit determination unit 27.

[0231] If the tension ratio does not satisfy the condition of formula (1.22), the worker changes the car position and measures the tensions of the first portion 6 a and the second portion 6 b, which causes the wear state estimation unit 22 to acquire new discrete tension data in step S101.

[0232] The wear state estimation unit 22 repeats the above process until the tension ratio satisfies the condition of equation (1.22).

[0233] If the tension ratio satisfies the condition of equation (1.22), the wear state estimating unit 22 calculates the wear difference in step S104, as in the first to third embodiments, and ends the process.

[0234] According to the condition monitoring device 21 and the condition monitoring method, the difference in wear of each pulley can be calculated more accurately.

[0235] It is also possible to determine whether the tension ratio To / Ti has reached the limit traction ratio Γ by utilizing the fact that the rope tension fluctuations become discontinuous.

[0236] Here, an example of a method for calculating the wear difference when the car hoist 7a is the target pulley will be described with reference to Fig. 17. The tension acquisition unit 23 calculates the tension of the first portion 6a of the m-th main rope 6 as T ｍ As the car position x １ , x ２ , x ３Discrete tension data is acquired at the three points. Next, the traction limit determination unit 27 determines whether the tension ratio To / Ti has reached the limit traction ratio Γ.

[0237] At this time, the tension T of the first portion 6a in the section where slippage does not occur due to the tension ratio To / Ti exceeding the limit traction ratio Γ is ｍ Assume that (x) is a linear function. １ <x<x ３ If the limit traction ratio Γ is not exceeded within the range, the tension gradients at two adjacent points will be equal, and therefore the tension Tm will satisfy the following condition:

[0238] (T ｍ (x ２ )- T ｍ (x １ )) / (x ２ -x １ )=( T ｍ (x ３ )- T ｍ (x ２ )) / ( x ３ -x ２ )

[0239] If the above formula is satisfied, the wear difference calculation unit 25 calculates the car position x １ , x ２ , x ３ The wear difference can be calculated using all the discrete tension data acquired in the above.

[0240] On the other hand, in the example shown in FIG. ３ is located within the slippage occurrence section, the tension gradients at two adjacent points are not equal, and the above formula is not satisfied. In this case, the wear difference calculation unit 25 calculates １ , x ２ The wear difference is calculated using only the discrete tension data obtained in step 1.

[0241] In this way, in the wear difference calculation step, it is determined whether the tensions at the three car positions are changing linearly. If they are not changing linearly, the wear difference is calculated using the discrete tension data at the two car positions from the bottom floor.

[0242] According to such a condition monitoring device 21 and condition monitoring method, even if slippage occurs due to the tension ratio To / Ti exceeding the limit traction ratio Γ, the wear difference in each pulley can be calculated more accurately.

[0243] The status monitoring program of the fourth embodiment is a program that causes a computer to execute the processing of the status monitoring method by the status monitoring device 21 of the fourth embodiment. The recording medium of the fourth embodiment is a computer-readable recording medium that records an elevator status monitoring program that causes a computer to execute the status monitoring method by the status monitoring device 21 of the fourth embodiment.

[0244] 18 is a block diagram showing a condition monitoring device 21 according to embodiment 5. A wear state estimation unit 22 according to embodiment 5 has a wear difference determination unit 28 instead of the wear difference calculation unit 25 according to embodiments 1 to 4.

[0245] Based on the discrete tension data and a plurality of parameters, the wear difference determination unit 28 calculates the tension gradient of each main rope 6. Then, by comparing the tension gradients of each main rope 6, the wear difference determination unit 28 determines the state of the relative wear difference between the plurality of rope grooves 5 a.

[0246] FIG. 19 is a graph showing the relationship between the tension and the car position when the tensions of the two main ropes 6 are obtained at the same car position.

[0247] In the fifth embodiment, the car position x １ , x ２ In this case, the discrete tension data T of the m-th main rope 6 is ｍ (x １ ), T ｍ (x ２ ) and obtain the tension difference ΔT ｍ and car position x １ , x ２ Distance Δx between ｃ From this, the tension gradient ΔT in the first portion 6a of the m-th main rope 6 is ｍ / Δx ｃ Similarly, the tension gradient ΔT in the first portion 6a of the first main rope 6 is calculated. １ / Δxｃ Ask for.

[0248] When a difference in wear occurs between the first rope groove 5a and the m-th rope groove 5a, the following formula is satisfied.

[0249] |(ΔT １ / Δx ｃ )-(ΔT ｍ / Δx ｃ )|≧ε

[0250] As shown in FIG. 20, the car position and distance Δx ｃ may be different for each main rope 6.

[0251] Fig. 21 is a flowchart showing the operation of the wear state estimation unit 22 in Fig. 18. Fig. 21 shows the operation when the car hoist 7a is the target pulley.

[0252] In step S201, the wear state estimation unit 22 acquires discrete tension data of the first portion 6a at the same car position. Then, in step S202, the wear state estimation unit 22 calculates the tension gradient in the first portion 6a.

[0253] Thereafter, in step S203, the wear state estimation unit 22 determines whether the absolute value of the difference in tension gradient is less than a preset small value ε. If the absolute value of the difference in tension gradient is less than ε, that is, if the above formula is not satisfied, in step S204, the wear state estimation unit 22 determines that no wear difference has occurred and ends the process.

[0254] On the other hand, if the absolute value of the difference in tension gradient is not less than ε, that is, if the above formula is satisfied, the wear state estimation unit 22 determines in step S205 that a wear difference has occurred, and ends the process.

[0255] The wear state estimation step of embodiment 5 includes a wear difference determination step instead of the wear difference calculation step of embodiment 1. The wear difference determination step is a step in which the tension gradient of each main rope 6 is calculated based on the discrete tension data and a plurality of parameters, and the tension gradients of each main rope 6 are compared to determine the state of the relative wear difference between the plurality of rope grooves 5 a.

[0256] According to such a condition monitoring device 21 and condition monitoring method, it is possible to more accurately determine whether there is a relative difference in wear among the multiple rope grooves 5a by comparing the tension gradients of each main rope 6. Therefore, it is possible to more accurately estimate the degree of wear of the rope grooves 5a without directly measuring the depth of each rope groove 5a.

[0257] In addition, in the wear difference determination unit 28 and the wear difference determination step, the degree of relative wear difference between the multiple rope grooves 5 a can also be determined from the difference in tension gradient of each main rope 6.

[0258] 22 is an explanatory diagram showing an example of the degree of wear of a plurality of rope grooves 5a. In this example, the second rope groove 5a has a wear rate of ΔR ２ That is, the depth of the second rope groove 5a is worn by ΔR less than the depth of the first rope groove 5a. ２ Only bigger.

[0259] In addition, the m-th rope groove 5a has a ΔR ｍ That is, the depth of the m-th rope groove 5a is worn by ΔR less than the depth of the first rope groove 5a. ｍ Only bigger.

[0260] Fig. 23 is a graph showing the relationship between the rope tension and the car position corresponding to the degree of wear in Fig. 22. The magnitude of the difference in wear with respect to the reference rope groove 5a, in this case the first rope groove 5a, correlates with the magnitude of the difference in the tension gradient.

[0261] When tension fluctuations such as those shown in FIG. 23 occur, the relationship between the tension gradient in each main rope 6 and the wear difference in each rope groove 5a satisfies the following two formulas.

[0262] |(ΔT １ / Δx ｃ )-(ΔT ｍ / Δx ｃ )|>|(ΔT １ / Δx ｃ )-(ΔT ２ / Δx ｃ ) | ΔR ｍ >ΔR ２

[0263] In this way, the degree of relative wear difference between the multiple rope grooves 5a can be determined more accurately based on the magnitude of the difference in tension gradient.

[0264] In the first to fifth embodiments, the wear difference may be calculated or the state of the wear difference may be determined by excluding the mass that fluctuates due to the movement of the car 7 from the discrete tension data. Examples of the mass that fluctuates due to the movement of the car 7 include the mass of the control cable 9, the balancing rope 10, etc.

[0265] Moreover, the status monitoring program of the fifth embodiment is a program that causes a computer to execute the processing of the status monitoring method by the status monitoring device 21 of the fifth embodiment. Moreover, the recording medium of the fifth embodiment is a computer-readable recording medium that records an elevator status monitoring program that causes a computer to execute the status monitoring method by the status monitoring device 21 of the fifth embodiment.

[0266] Sixth Embodiment Next, Fig. 24 is an explanatory diagram showing the relationship between the wear state estimating unit 22 and input / output data in a sixth embodiment.

[0267] The wear state estimation unit 22 compares the discrete tension data with the continuous tension data. The continuous tension data is continuous data on the tensions of all the main ropes 6 at all the car positions. In the continuous tension data, the tension, the rope number, and the car position are associated with each other.

[0268] The continuous tension data can be obtained, for example, by actual measurement. Alternatively, the continuous tension data can be obtained by inputting the discrete tension data and a plurality of parameters into the tension model described above.

[0269] The multiple types of data related to rope specifications include Young's modulus E, cross-sectional area A, rope diameter d, linear density ρ, number of ropes N, shackle stiffness ks, etc., but among these, Young's modulus E and cross-sectional area A change over time. When Young's modulus E and cross-sectional area A change, a discrepancy occurs between the continuous tension data and the discrete tension data.

[0270] In contrast to this, in the sixth embodiment, the parameter values ​​of each main rope 6, namely, the value of Young's modulus E, the value of cross-sectional area A, and the value of rope length L, are converged and identified by repeated calculation so that the continuous tension data and the discrete tension data coincide with each other. The basic configuration of the condition monitoring device 21 according to the sixth embodiment is the same as that shown in FIG.

[0271] FIG. 25 is a flowchart showing part of the operation of the wear state estimating unit 22 according to the sixth embodiment. In addition to the same operations as those in the first embodiment, the wear state estimating unit 22 compares continuous tension data obtained from a tension model that uses the calculated wear difference as an input with the discrete tension data used to calculate the wear difference. The wear state estimating unit 22 then periodically executes a parameter value update process shown in FIG. 25 so that the continuous tension data and the discrete tension data match. The calculation of the parameter value update process is generally called parameter estimation or parameter identification.

[0272] The wear state estimation unit 22 calculates the wear difference in step S301. Subsequently, in step S302, the wear state estimation unit 22 calculates the difference between the continuous tension data and the discrete tension data at the same car position for each main rope 6, i.e., the tension difference.

[0273] Thereafter, in step S303, the wear state estimation unit 22 determines whether the absolute value of the tension difference is smaller than the difference threshold ε. The difference threshold ε is a minute value that is preset in the wear state estimation unit 22. If the tension difference is smaller than the difference threshold ε, the wear state estimation unit 22 ends the processing for that cycle.

[0274] If the tension difference is equal to or greater than the difference threshold value ε, the wear state estimation unit 22 corrects the parameter values ​​in step S304. The parameter values ​​include the Young's modulus E, the cross-sectional area A, the rope length L, and the shackle stiffness ks.

[0275] At this time, the wear state estimation unit 22 uses a data table that stores the results of calculations using a plurality of different parameter values ​​for the tension model. The wear state estimation unit 22 estimates, by interpolation from the data table, the parameter values ​​that result in the smallest tension difference.

[0276] Thereafter, in step S305, the wear state estimation unit 22 calculates a new wear difference using the corrected parameters, and then in step S306, the wear state estimation unit 22 calculates new continuous tension data using the updated parameters and the new wear difference.

[0277] Thereafter, the wear state estimation unit 22 updates the continuous tension data in step S307, and returns to the processing of step S301. By repeating the above processing until the absolute value of the tension difference becomes smaller than the difference threshold value ε, it is possible to identify parameter values ​​after aging and update the parameter values.

[0278] The condition monitoring method according to the sixth embodiment includes a wear state estimation step and a parameter value updating step, similar to those in the first embodiment. The parameter value updating step is a step of updating at least one of the value of Young's modulus E and the value of cross-sectional area A when the difference between the continuous tension data and the discrete tension data is equal to or greater than the difference threshold ε, so that the continuous tension data and the discrete tension data match.

[0279] In such a condition monitoring device 21 and condition monitoring method, the values ​​of Young's modulus E and cross-sectional area A are updated in response to changes over time in each main rope 6. Since Young's modulus E and cross-sectional area A affect rope rigidity, the tension of each main rope 6 can be estimated more accurately.

[0280] Furthermore, the identified cross-sectional area A of each main rope 6 can be used as an index for determining the deterioration state of each main rope 6. For example, if the identified cross-sectional area A is below an allowable value, a maintenance inspection is carried out, and depending on the condition of the main rope 6, the rope is replaced.

[0281] Among the multiple types of data related to the specifications of the main rope 6, values ​​that change over time include the rope diameter d, in addition to Young's modulus E and cross-sectional area A. When the rope diameter d changes, the amount of winding of the main rope 6 on the pulley changes, similar to when the groove depth in the pulley changes, affecting the tension. Therefore, the rope diameter d may be identified by converging through repeated calculations so that the continuous tension data and the discrete tension data match.

[0282] Furthermore, while the amount of groove wear does not change depending on the car position, the rope diameter d varies depending on the car position because the number of bends varies for each rope section. Such differences in rope diameter d due to car position can also be calculated by comparing the difference between the continuous tension data and the discrete tension data for each car position.

[0283] The status monitoring program of the sixth embodiment is a program that causes a computer to execute the processing of the status monitoring method by the status monitoring device 21 of the sixth embodiment. The recording medium of the sixth embodiment is a computer-readable recording medium that records an elevator status monitoring program that causes a computer to execute the status monitoring method by the status monitoring device 21 of the sixth embodiment.

[0284] Seventh Embodiment Next, Fig. 26 is an explanatory diagram showing the relationship between the wear state estimating unit 22 and input / output data in a seventh embodiment. The basic configuration of the condition monitoring device 21 in the seventh embodiment is the same as that of the condition monitoring device 21 in the second embodiment shown in Fig. 5.

[0285] The correction unit 26 approximates tension fluctuations relative to car position using a function. When the approximation error becomes large, a deviation occurs between the continuous tension data and the discrete tension data. In contrast, in the seventh embodiment, the correction parameters in the correction unit 26 are identified by converging them through repeated calculations so that the continuous tension data and the discrete tension data coincide with each other.

[0286] The condition monitoring method according to the seventh embodiment includes a correction parameter updating step in addition to the wear difference calculating step similar to that of the first embodiment. The correction parameter updating step is a step of updating the correction parameter so that the continuous tension data and the discrete tension data match when the difference between the continuous tension data and the discrete tension data is equal to or greater than the difference threshold ε.

[0287] The specific content of the correction parameter updating step is that the Young's modulus E, the cross-sectional area A, and the rope length L in the description of FIG. 25 are replaced with correction parameters.

[0288] According to such a condition monitoring device 21 and condition monitoring method, the values ​​of the correction parameters are updated in response to aging of the pulleys and main ropes 6. This makes it possible to more accurately calculate the difference in wear between the pulleys.

[0289] The status monitoring program of the seventh embodiment is a program that causes a computer to execute the processing of the status monitoring method by the status monitoring device 21 of the seventh embodiment. The recording medium of the seventh embodiment is a computer-readable recording medium that records an elevator status monitoring program that causes a computer to execute the status monitoring method by the status monitoring device 21 of the seventh embodiment.

[0290] Furthermore, both the parameter value updating step in the sixth embodiment and the correction parameter updating step in the seventh embodiment may be executed.

[0291] Eighth Embodiment Next, an eighth embodiment will be described. The basic configuration of a state monitoring device 21 according to the eighth embodiment is the same as that shown in FIG.

[0292] The elevator that is the object of maintenance work measures the tension of each main rope 6 at a preset period and transmits the measured tension as discrete tension data. The condition monitoring device 21 receives the discrete tension data via a communication network line.

[0293] 27 is a flowchart showing part of the operation of the wear state estimating unit 22 according to embodiment 8. In step S401, the wear state estimating unit 22 acquires discrete tension data via a communication network line. Data related to rope specifications is stored in the wear state estimating unit 22 in advance.

[0294] In step S402, the wear state estimation unit 22 calculates the wear difference. Then, in step S403, the wear state estimation unit 22 determines whether the maximum value of the wear difference, i.e., the maximum wear difference, exceeds the wear difference tolerance. The wear difference tolerance is set in advance in the wear state estimation unit 22.

[0295] If the maximum wear difference exceeds the wear difference tolerance, the wear state estimation unit 22 issues a maintenance command, i.e., notifies the management room that maintenance work is required, in step S404. If the maximum wear difference does not exceed the wear difference tolerance, the wear state estimation unit 22 waits to receive the next discrete tension data.

[0296] The condition monitoring method according to the eighth embodiment includes a maintenance command issuing step in addition to the wear difference calculation step similar to that of the first embodiment. The maintenance command issuing step is a step of determining whether the calculated maximum value of the wear difference is outside the wear difference tolerance, and issuing a notification that maintenance work is required if it is outside the wear difference tolerance.

[0297] In such a condition monitoring device 21 and condition monitoring method, a maintenance command is issued when the maximum wear difference exceeds the wear difference tolerance. This allows the wear difference of each pulley to be adjusted at a more appropriate time, and prevents the lifespan of each pulley and each main rope 6 from being shortened.

[0298] Furthermore, excessive maintenance work can be prevented, and the allocation of maintenance workers can be optimized.

[0299] Furthermore, the target of maintenance work can be more clearly identified, and the maintenance work time can be reduced.

[0300] In addition, by optimizing the timing of maintenance work, it is possible to suppress vibrations, abnormal noises, etc. caused by deterioration of elevator performance.

[0301] The status monitoring program of the eighth embodiment is a program that causes a computer to execute the processing of the status monitoring method by the status monitoring device 21 of the eighth embodiment. The recording medium of the eighth embodiment is a computer-readable recording medium that records an elevator status monitoring program that causes a computer to execute the status monitoring method by the status monitoring device 21 of the eighth embodiment.

[0302] Ninth Embodiment Next, a description will be given of a ninth embodiment. The basic configuration of a state monitor 21 according to the ninth embodiment is the same as that shown in FIG.

[0303] The amount of processing of each rope groove 5a is stored as a parameter in the wear state estimation unit 22. The initial value of the amount of processing is 0.

[0304] 28 is a flowchart showing part of the operation of the wear state estimation unit 22 according to embodiment 9. In step S501, the wear state estimation unit 22 acquires, via a communication network line, discrete tension data, multiple types of data related to rope specifications, etc. Some of the multiple types of data related to rope specifications, for example, the rope diameter d, may be a fixed value.

[0305] Next, in step S502, the wear state estimation unit 22 calculates the wear difference.

[0306] Thereafter, in step S503, the wear state estimation unit 22 determines whether the wear difference is equal to or less than a reference value. Specifically, the wear state estimation unit 22 determines whether the maximum wear difference is equal to or less than a reference value. The reference value is stored in advance in the wear state estimation unit 22.

[0307] If the wear difference is equal to or less than the reference value, the wear state estimation unit 22 sets the amount of processing of the rope grooves 5a in step S504, transmits the set amount of processing to the elevator, and ends the process. The maintenance worker mechanically processes each rope groove 5a according to the transmitted amount of processing. If the amount of processing is the initial value of 0, no processing is required.

[0308] If the difference in wear exceeds the reference value, the wear state estimation unit 22 updates the processing amount of each rope groove 5a by increasing it by a set amount in step S505.

[0309] Then, in step S506, the wear state estimating unit 22 determines whether machining with the updated machining amount is feasible.

[0310] Specifically, the wear state estimation unit 22 determines whether the work time required to process the updated processing amount is equal to or less than a set time, and if it is equal to or less than the set time, determines that it is feasible, and if it exceeds the set time, determines that it is not feasible.

[0311] In addition, the wear state estimation unit 22 determines whether the strength of the pulley is equal to or greater than the set strength due to the processing of the updated processing amount, and if it is equal to or greater than the set strength, determines that it is feasible, and if it is less than the set strength, determines that it is not feasible.

[0312] If the processing with the updated processing amount is feasible, the wear state estimation unit 22 returns to the process of step S501. Then, in step S502, the wear state estimation unit 22 calculates the wear difference while taking the updated processing amount into consideration. The wear state estimation unit 22 repeats the above process until the wear difference becomes equal to or less than the reference value.

[0313] If processing with the updated processing amount is not feasible, it is difficult to reduce the wear difference to below the reference value even if the processing amount is increased, so in step S507, the wear state estimation unit 22 sends an equipment replacement command to the elevator and terminates the processing.

[0314] The condition monitoring method according to the ninth embodiment includes a machining determination step and a machining amount setting step in addition to the wear difference calculation step similar to that of the first embodiment.

[0315] The machining determination step is a step for determining whether or not machining is required for each rope groove 5 a based on the relative wear difference between the rope grooves 5 a. The machining amount setting step is a step for setting the amount of machining when it is determined that machining is required.

[0316] According to such a condition monitoring device 21 and condition monitoring method, it is determined whether machining is necessary for each rope groove 5a, and if so, the amount of machining is set, thereby improving the efficiency of maintenance work on the pulley.

[0317] In addition, in the machining amount setting step, it is determined whether machining is feasible, and if not, a device replacement command is sent, which allows the device to be replaced at a more appropriate time.

[0318] In the ninth embodiment, the state of the relative wear difference between the plurality of rope grooves 5a may be the result of determination by the wear difference determination unit 28 in the fifth embodiment.

[0319] Moreover, the status monitoring program of the ninth embodiment is a program that causes a computer to execute the processing of the status monitoring method by the status monitoring device 21 of the ninth embodiment. Moreover, the recording medium of the ninth embodiment is a computer-readable recording medium that records an elevator status monitoring program that causes a computer to execute the status monitoring method by the status monitoring device 21 of the ninth embodiment.

[0320] Tenth Embodiment Next, a tenth embodiment will be described. The basic configuration of a state monitor 21 according to the tenth embodiment is the same as that shown in FIG.

[0321] 29 is an explanatory diagram showing the relationship between the wear state estimating unit 22 and input / output data in embodiment 10. When the rope diameter of each main rope 6 changes over time, the difference in wear of each rope groove 5 a changes equivalently.

[0322] In contrast to this, in the tenth embodiment, the rope diameter is actually measured for each main rope 6, and the difference between the measured and calculated wear difference is calculated, thereby calculating the wear difference excluding the influence of the difference in rope diameter.

[0323] The condition monitoring method according to the tenth embodiment includes a wear difference correction step in addition to the wear difference calculation step similar to that of the first embodiment. The wear difference correction step is a step in which the calculation result of the wear difference is corrected based on rope diameter data obtained by actually measuring the rope diameter of each main rope 6 and the wear difference.

[0324] According to such a condition monitoring device 21 and condition monitoring method, the value of the wear difference is corrected in response to aging of the pulleys and main ropes 6. This allows for more accurate estimation of the wear difference of each pulley.

[0325] The status monitoring program of the tenth embodiment is a program that causes a computer to execute the processing of the status monitoring method by the status monitoring device 21 of the tenth embodiment. The recording medium of the tenth embodiment is a computer-readable recording medium that records an elevator status monitoring program that causes a computer to execute the status monitoring method by the status monitoring device 21 of the tenth embodiment.

[0326] Furthermore, all of the parameter value updating step in the sixth embodiment, the correction parameter updating step in the seventh embodiment, and the wear difference correcting step in the tenth embodiment may be executed.

[0327] The condition monitoring method disclosed herein may be performed automatically by the condition monitoring device 21, without relying on the manual operation of an operator. In this case, the tension included in the discrete tension data is automatically measured by a tension measuring device permanently or temporarily installed in the elevator. At this time, the condition monitoring device 21 sends a command to the elevator control device 4, thereby measuring the tension at a plurality of different car positions. Furthermore, the plurality of parameters may use values ​​stored in advance and values ​​acquired from the elevator control device 4.

[0328] Furthermore, the term "rope" in this disclosure is used in a broad sense and includes, for example, a belt for suspending a car.

[0329] The elevator may also be an elevator with a machine room, a machine room-less elevator, a double-deck elevator, a one-shaft multi-car elevator, etc. In a one-shaft multi-car elevator, an upper car and a lower car located directly below the upper car each independently ascend and descend in a common elevator shaft.

[0330] Each function of the state monitoring device 21 in the first to tenth embodiments is realized by a processing circuit. Fig. 30 is a configuration diagram showing a first example of a processing circuit that realizes each function of the state monitoring device 21 in the first to tenth embodiments. The processing circuit 100 in the first example is dedicated hardware.

[0331] The processing circuit 100 may be, for example, a single circuit, a composite circuit, a programmed processor, a parallel programmed processor, an ASIC (Application Specific Integrated Circuit), an FPGA (Field Programmable Gate Array), or a combination thereof. Each function of the status monitoring device 21 may be realized by a separate processing circuit 100, or all functions may be realized by the processing circuit 100.

[0332] 31 is a configuration diagram showing a second example of a processing circuit that realizes each function of the state monitor 21 according to the first to tenth embodiments. The processing circuit 200 of the second example includes a processor 201 and a memory 202.

[0333] In the processing circuit 200, each function of the status monitor 21 is realized by software, firmware, or a combination of software and firmware. The software and firmware are written as programs and stored in the memory 202. The processor 201 realizes each function by reading and executing the programs stored in the memory 202.

[0334] The programs stored in memory 202 can be said to cause the computer to execute the procedures or methods of the above-mentioned components. Here, memory 202 refers to non-volatile or volatile semiconductor memory such as RAM (Random Access Memory), ROM (Read Only Memory), flash memory, EPROM (Erasable Programmable Read Only Memory), and EEPROM (Electrically Erasable and Programmable Read Only Memory). Magnetic disks, flexible disks, optical disks, compact disks, minidisks, DVDs, and the like also fall under memory 202.

[0335] It should be noted that some of the functions of the above-described units may be realized by dedicated hardware, and other parts may be realized by software or firmware.

[0336] In this way, the processing circuit can realize the functions of each of the above-mentioned units by hardware, software, firmware, or a combination of these.

[0337] 5 Drive sheave (pulley), 6 Main rope, 7 Cage, 7a Cage hoisting wheel (pulley), 8 Counterweight, 8a Counterweight hoisting wheel (pulley), 21 Condition monitoring device, 22 Wear state estimation unit, 23 Tension acquisition unit, 24 Parameter acquisition unit, 25 Wear difference calculation unit, 26 Correction unit, 27 Traction limit determination unit, 28 Wear difference determination unit.

Claims

1. An elevator status monitoring device comprising: a wear state estimation unit that estimates the wear state of multiple rope grooves in a pulley around which multiple ropes that suspend a car and a counterweight are wound, wherein the wear state estimation unit has: a tension acquisition unit that acquires discrete tension data that is the tension value of each of the ropes at multiple different car positions; a parameter acquisition unit that acquires multiple parameters including the rope lengths at the multiple car positions; and a wear difference calculation unit that calculates the relative wear difference between the multiple rope grooves based on the discrete tension data and the multiple parameters.

2. The elevator status monitoring device according to claim 1, wherein said plurality of parameters include specifications of said plurality of ropes and pulley diameters.

3. An elevator status monitoring device as described in claim 1 or claim 2, wherein the wear difference calculation unit calculates a correction parameter to correct the change in the amount of elongation of each rope due to the pulley winding each rope, and calculates the wear difference using the correction parameter.

4. An elevator status monitoring device as claimed in any one of claims 1 to 3, wherein the wear difference calculation unit has a traction limit determination unit that determines whether the tension ratio between the entrance side and exit side of the pulley in the rope has reached the limit traction ratio.

5. An elevator condition monitoring device as described in any one of claims 1 to 4, wherein the wear state estimation unit determines whether the calculated maximum value of the wear difference is outside the wear difference tolerance, and if it is outside the wear difference tolerance, issues a warning that maintenance work is required.

6. An elevator status monitoring device comprising: a wear state estimation unit that estimates the wear state of multiple rope grooves in a pulley around which multiple ropes that suspend a car and a counterweight are wound, wherein the wear state estimation unit has: a tension acquisition unit that acquires discrete tension data that is the tension value of each of the ropes at multiple different car positions; a parameter acquisition unit that acquires multiple parameters including the rope lengths at the multiple car positions; and a wear difference determination unit that calculates the tension gradient of each of the ropes based on the discrete tension data and the multiple parameters and compares the tension gradients to determine the relative wear difference state between the multiple rope grooves.

7. An elevator status monitoring device according to claim 6, wherein the wear difference determining unit determines the degree of relative wear difference between the plurality of rope grooves from the difference in the tension gradient of each of the ropes.

8. A method for monitoring the status of an elevator, comprising: a wear state estimation step of estimating the wear state of multiple rope grooves in a pulley around which multiple ropes that suspend a car and a counterweight are wound, wherein the wear state estimation step comprises: a tension acquisition step of acquiring discrete tension data which is the tension value of each of the ropes at multiple different car positions; a parameter acquisition step of acquiring multiple parameters including rope lengths at the multiple car positions; and a wear difference calculation step of calculating the relative wear difference between the multiple rope grooves based on the discrete tension data and the multiple parameters.

9. The elevator status monitoring method according to claim 8, wherein the plurality of parameters include specifications of the plurality of ropes and pulley diameters.

10. An elevator status monitoring method as described in claim 8 or claim 9, wherein the wear difference calculation step calculates a correction parameter that corrects the change in the amount of elongation of each of the ropes due to the pulley winding each of the ropes, and calculates the wear difference using the correction parameter.

11. The elevator status monitoring method according to claim 10, wherein the tension values ​​included in the discrete tension data are obtained by measuring the tension of the winding side portion of each of the ropes relative to the pulley.

12. A method for monitoring the status of an elevator as described in claim 11, wherein the tension value included in the discrete tension data is obtained by measuring the tension at a car position where the rope length is at its maximum, and then measuring the tension at a car position where the rope length is shorter than the maximum.

13. A method for monitoring the condition of an elevator as described in claim 11 or claim 12, wherein when the plurality of ropes are wound around two or more pulleys, the method calculates the difference in wear on a first pulley, which is the pulley closest to the ends of the plurality of ropes, and then calculates the difference in wear on a second pulley, which is the pulley located next to the first pulley, using the difference in payout amount due to the difference in wear on the first pulley and the change in tension due to minute slippage on the first pulley.

14. A method for monitoring the condition of an elevator as described in claim 11 or claim 12, wherein, when the plurality of ropes are wound around two or more pulleys, after calculating the difference in wear at a first pulley which is the pulley closest to the ends of the plurality of ropes, the difference in wear at pulleys other than the first pulley is estimated from the difference in wear at the first pulley using a correction coefficient obtained from pulley information including at least one of the groove surface pressure, hardness, groove coefficient, and rotation speed of each pulley.

15. An elevator status monitoring method as described in any one of claims 8 to 14, wherein the wear difference calculation step determines whether the tension ratio between the entrance side and exit side of the pulley in the rope has reached a limit traction ratio, and calculates the wear difference using the discrete tension data where the tension ratio is equal to or less than the limit traction ratio.

16. A method for monitoring the status of an elevator as described in any one of claims 8 to 14, wherein the wear difference calculation step determines whether the tension at the three car positions is changing linearly, and if it is not changing linearly, calculates the wear difference using the discrete tension data at the two car positions from the bottom floor.

17. An elevator status monitoring method as set forth in any one of claims 8 to 16, further comprising a parameter value updating step of updating at least one of the plurality of parameters so that the continuous tension data and the discrete tension data coincide when the difference between the continuous tension data, which is continuous data on the tension of each of the ropes, and the discrete tension data is equal to or greater than a difference threshold.

18. An elevator status monitoring method as set forth in any one of claims 10 to 14, further comprising a correction parameter updating step of updating the correction parameter so that the continuous tension data and the discrete tension data coincide when the difference between the continuous tension data, which is continuous data on the tension of each of the ropes, and the discrete tension data is equal to or greater than a difference threshold.

19. An elevator condition monitoring method as set forth in any one of claims 8 to 18, further comprising a maintenance command issuing step of determining whether the calculated maximum value of the wear difference is outside the wear difference tolerance, and issuing a maintenance command notification indicating that maintenance work is required if the maximum value of the calculated wear difference is outside the wear difference tolerance.

20. An elevator status monitoring method according to any one of claims 8 to 19, further comprising a wear difference correction step of correcting the calculated wear difference based on rope diameter data obtained by actually measuring the rope diameter of each of the ropes and the calculated wear difference.

21. A method for monitoring the status of an elevator, comprising: a wear state estimation step of estimating the wear state of multiple rope grooves in a pulley around which multiple ropes that suspend a car and a counterweight are wound, wherein the wear state estimation step comprises: a tension acquisition step of acquiring discrete tension data which is the tension value of each of the ropes at multiple different car positions; a parameter acquisition step of acquiring multiple parameters including rope lengths at the multiple car positions; and a wear difference determination step of calculating the tension gradient of each of the ropes based on the discrete tension data and the multiple parameters, and comparing the tension gradients to determine the relative wear difference state between the multiple rope grooves.

22. The elevator condition monitoring method according to claim 21, wherein the wear difference determining step determines the degree of relative wear difference between the plurality of rope grooves from the difference in the tension gradient of each of the ropes.

23. A method for monitoring the condition of an elevator as set forth in any one of claims 8 to 22, further comprising: a machining determination step for determining whether machining is required for each of the rope grooves based on the relative difference in wear between the plurality of rope grooves; and a machining amount setting step for setting the amount of machining when it is determined that machining is required.

24. An elevator status monitoring program that causes a computer to execute the status monitoring method according to any one of claims 8 to 23.

25. A recording medium on which an elevator status monitoring program is recorded that causes a computer to execute the status monitoring method according to any one of claims 8 to 23.

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