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

Abstract

To provide an elevator monitoring device, an elevator monitoring method, and an elevator monitoring program capable of further accurately predicting a future abrasion amount of a plurality of sheave grooves.SOLUTION: An elevator monitoring device 20 comprises an abrasion prediction unit 22. The abrasion prediction unit 22 calculates an abrasion amount prediction value by using an abrasion prediction formula. The abrasion amount prediction value is a prediction value of a future abrasion amount generated during a setting period in a plurality of sheave grooves. The abrasion prediction formula includes, as inputs, the tension of a car side part and the tension of a balance weight side part in a plurality of ropes, the sliding amounts of the ropes, and sheave material hardness.SELECTED DRAWING: Figure 6

Description

[Technical Field]

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

[0002] In a conventional elevator wear amount measuring device, an estimated value of the amount of wear of the sheave groove is calculated from the amount of sheave rotation that occurs while the car travels a reference distance (see, for example, Patent Document 1). [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Laid-Open No. 2011-195253 Summary of the Invention [Problem to be solved by the invention]

[0004] Conventional elevator wear measurement devices such as those described above estimate the current amount of wear in the sheave grooves, but are unable to predict the amount of wear in the sheave grooves in the future.

[0005] The present disclosure has been made to solve the above-mentioned problems, and aims to provide an elevator monitoring device, an elevator monitoring method, an elevator monitoring program, and a recording medium that can more accurately predict the future amount of wear of multiple sheave grooves. [Means for solving the problem]

[0006] The elevator monitoring device according to the present disclosure includes a wear prediction unit that calculates a wear prediction value, which is a prediction value of the future wear amount that will occur in the multiple sheave grooves over a set period, using a wear prediction formula that takes as input the tension of the car-side portion and the tension of the counterweight-side portion of the multiple ropes that suspend the car and counterweight, the amount of slippage of the multiple ropes, and the material hardness of the sheaves. In addition, the elevator monitoring method according to the present disclosure includes a wear prediction step of calculating a wear amount prediction value, which is a prediction value of the future wear amount that will occur in the multiple sheave grooves over a set period, using a wear prediction formula that takes as input the tension of the car-side portion and the tension of the counterweight-side portion of the multiple ropes that suspend the car and counterweight, the amount of slippage of the multiple ropes, and the material hardness of the sheave. [Effects of the Invention]

[0007] According to the present disclosure, it is possible to more accurately predict the future amount of wear of multiple sheave grooves. [Brief explanation of the drawings]

[0008] [Figure 1] 1 is a schematic configuration diagram showing an elevator system according to a first embodiment. [Figure 2] FIG. 2 is an explanatory diagram showing tensions acting on each rope in FIG. [Figure 3] FIG. 3 is a perspective view showing the drive sheave of FIG. 2. [Figure 4] FIG. 4 is a cross-sectional view showing a first example of the sheave groove of FIG. 3. [Figure 5] FIG. 4 is a cross-sectional view showing a second example of the sheave groove of FIG. 3. [Figure 6] FIG. 2 is a block diagram showing a control system of the elevator system of FIG. 1. [Figure 7] 7 is a flowchart showing a wear prediction process performed by the elevator monitoring device of FIG. 6. [Figure 8] 3 is an explanatory diagram showing an example of a calculation result of a predicted wear amount value in a sheave groove into which the first rope of FIG. 2 is inserted. FIG. [Figure 9] 3 is an explanatory diagram showing an example of a calculation result of a predicted wear amount value in a sheave groove into which the second rope of FIG. 2 is inserted. FIG. [Figure 10] FIG. 10 is an explanatory diagram showing an example of a calculation result of a predicted wear amount value according to the second embodiment. [Figure 11] FIG. 10 is a block diagram showing a control system of the elevator system according to the third embodiment. [Figure 12] FIG. 10 is a block diagram showing a control system of the elevator system according to the fourth embodiment. [Figure 13] FIG. 10 is a block diagram showing a control system of an elevator system according to a fifth embodiment. [Figure 14] FIG. 13 is a block diagram showing a control system of the elevator system according to the sixth embodiment. [Figure 15] FIG. 1 is an explanatory diagram showing an equivalent model of a rope passing over a pulley. [Figure 16] FIG. 16 is an explanatory diagram showing the equivalent model of FIG. 15 replaced with a model in a one-dimensional coordinate system. [Figure 17] 15 is a flowchart showing a wear prediction process performed by the elevator monitoring device of FIG. 14. [Figure 18] FIG. 20 is an explanatory diagram illustrating a method for calculating a predicted wear amount value in the seventh embodiment. [Figure 19] 13 is a flowchart showing a wear prediction process performed by the elevator monitoring device of the seventh embodiment. [Figure 20] 13 is a flowchart showing a wear prediction process performed by the elevator monitoring device of the eighth embodiment. [Figure 21] FIG. 16 is an explanatory diagram showing the equivalent model of FIG. 15 divided into a winding-side portion and a feeding-side portion. [Figure 22] FIG. 2 is an explanatory diagram showing a model of the elevator in FIG. 1. [Figure 23] 10 is a graph showing the relationship between the tension of two ropes and the car position when the depths of the two sheave grooves are equal. [Figure 24] 10 is a graph showing the relationship between the tension of the two ropes and the car position when there is a 0.2 mm difference in depth between the two sheave grooves. [Figure 25] 10 is a graph showing the relationship between the calculated tension of the two ropes and the car position when there is a 0.7 mm difference in depth between the two sheave grooves, compared with multiple actual measured values. [Figure 26] 13 is a flowchart showing a wear prediction process performed by the elevator monitoring device of the modified example of the eighth embodiment. [Figure 27]FIG. 13 is a schematic configuration diagram showing an elevator system according to a ninth embodiment. [Figure 28] FIG. 2 is an explanatory diagram schematically showing the relationship between a car, a drive sheave, and a plurality of ropes. [Figure 29] FIG. 29 is an explanatory diagram showing a state in which the car of FIG. 28 approaches the drive sheave. [Figure 30] FIG. 29 is a cross-sectional view showing an example of a state of wear of each sheave groove in the drive sheave of FIG. 28. [Figure 31] 1 is a configuration diagram showing a first example of a processing circuit that realizes each function of the elevator monitoring device according to the first to tenth embodiments. [Figure 32] FIG. 2 is a configuration diagram showing a second example of a processing circuit that realizes each function of the elevator monitoring device according to the first to tenth embodiments. DETAILED DESCRIPTION OF THE INVENTION

[0009] Hereinafter, embodiments will be described with reference to the drawings. Embodiment 1 1 is a schematic configuration diagram showing an elevator system according to embodiment 1. In the figure, the elevator system includes an elevator device 10, an elevator monitoring device 20, and a maintenance device 30.

[0010] The elevator system 10 includes a car 1, a counterweight 2, a hoist 3, a deflector sheave 4, a plurality of ropes 5, and an elevator control device 11. In FIG. 1, only one rope 5 is shown.

[0011] The hoist 3 has a hoist main body 6 and a drive sheave 7. The hoist main body 6 has a hoist motor (not shown) and a hoist brake (not shown). The hoist motor rotates the drive sheave 7. The hoist brake keeps the drive sheave 7 stationary. The hoist brake also brakes the rotation of the drive sheave 7.

[0012] The plurality of ropes 5 are wound around the drive sheave 7 and the deflector pulley 4. The car 1 is connected to one end of the plurality of ropes 5. The counterweight 2 is connected to the other end of the plurality of ropes 5.

[0013] The car 1 and the counterweight 2 are suspended by a plurality of ropes 5. The car 1 and the counterweight 2 are raised and lowered by rotating a drive sheave 7. The elevator system 10 of the first embodiment is a 1:1 roping type elevator system.

[0014] The elevator control device 11 controls the operation of the car 1 by controlling the hoisting machine 3.

[0015] A first tension measuring device 12 is provided at the ends of the plurality of ropes 5 on the car 1 side. A second tension measuring device 13 is provided at the ends of the plurality of ropes 5 on the counterweight 2 side. As the first tension measuring device 12 and the second tension measuring device 13, for example, a load cell can be used.

[0016] Note that accelerometers attached to the rope 5 may be used as the first tension measuring device 12 and the second tension measuring device 13. In this case, the frequency of the string vibration of the rope 5 is measured by the accelerometer. Then, tension information is obtained by converting the frequency into tension. The accelerometers may be attached to the rope 5 only during maintenance and inspection work, or may be attached to the rope 5 all the time.

[0017] The hoisting machine 3 is provided with a rotation sensor 14. The rotation sensor 14 generates a signal according to the rotation of the drive sheave 7. As the rotation sensor 14, for example, an encoder is used.

[0018] The elevator monitoring device 20 monitors the status of the elevator device 10. The elevator monitoring device 20 is also capable of communicating with the elevator control device 11. As a result, the elevator monitoring device 20 acquires various information relating to the status of the elevator device 10 from the elevator control device 11. A signal from the rotation sensor 14 is input to the elevator monitoring device 20 via the elevator control device 11.

[0019] The maintenance device 30 is a terminal carried by a maintenance worker during maintenance and inspection work. The maintenance worker can obtain information about the elevator device 10 that is the target of maintenance and inspection from the maintenance device 30. The maintenance device 30 can be, for example, a laptop computer, a tablet, or a smartphone.

[0020] The maintenance device 30 is capable of communicating with the elevator monitoring device 20. Furthermore, the signal from the first tension measuring device 12 and the signal from the second tension measuring device 13 are input to the maintenance device 30.

[0021] Fig. 2 is an explanatory diagram showing the tension acting on each rope 5 in Fig. 1. For simplicity, two ropes 5 are shown in Fig. 2, but the number of ropes 5 may be three or more.

[0022] Hereinafter, the portion of each rope 5 closer to the car 1 than the drive sheave 7 will be referred to as the car-side portion. Also, the portion of each rope 5 closer to the counterweight 2 than the drive sheave 7 will be referred to as the counterweight-side portion. Also, one of the two ropes 5 will be referred to as the first rope 5a, and the other as the second rope 5b.

[0023] The tension Tc1 of the car side portion of the first rope 5a, the tension Tw1 of the counterweight side portion of the first rope 5a, the tension Tc2 of the car side portion of the second rope 5b, and the tension Tw2 of the counterweight side portion of the second rope 5b are all different.

[0024] Normally, when the car 1 is empty, the weight of the counterweight 2 is greater than the weight of the car 1. Also, when the car 1 is fully loaded with passengers, the weight of the car 1 is greater than the weight of the counterweight 2.

[0025] Therefore, when the car 1 is empty, the relationship (Tc1 + Tc2) < (Tw1 + Tw2) holds. Also, when the car 1 is fully loaded with passengers, the relationship (Tc1 + Tc2) > (Tw1 + Tw2) holds.

[0026] When tension acts on each rope 5, an elongation corresponding to the magnitude of the tension occurs in each rope 5. For example, under the tension condition of Tc1 < Tc2, the relationship (the elongation amount of the car side portion of the first rope 5a) < (the elongation amount of the car side portion of the second rope 5b) holds.

[0027] When the drive sheave 7 rotates in the direction to raise the car 1, the car side portion of the first rope 5a is wound up and the counterweight side portion of the first rope 5a is paid out. At this time, the elongation amount of the car side portion of the first rope 5a and the elongation amount of the counterweight side portion of the first rope 5a are different from each other.

[0028] Therefore, the first rope 5a is guided by the drive sheave 7 while slightly slipping on the drive sheave 7 by the difference in the elongation amounts between the car side portion and the counterweight side portion. Such a small slip amount on the drive sheave 7 is referred to as the creep amount. And the value of the creep amount increases as the difference between the tension of the car side portion and the tension of the counterweight side portion increases.

[0029] Figure 3 is a perspective view showing the drive sheave 7 of Figure 2. Although omitted in Figure 2, a plurality of sheave grooves 8 are provided on the outer peripheral surface of the drive sheave 7. Each rope 5 is inserted into the corresponding sheave groove 8. In Figure 3, the second rope 5b is omitted.

[0030] Figure 4 is a cross-sectional view showing a first example of the sheave groove 8 of Figure 3. In the first example, the cross-section of the bottom surface of the sheave groove 8 is arc-shaped.

[0031] Fig. 5 is a cross-sectional view showing a second example of the sheave groove 8 of Fig. 3. In the second example, an undercut groove is provided on the bottom surface of the sheave groove 8.

[0032] A surface pressure corresponding to the magnitude of the tension acting on the corresponding rope 5 acts on the bottom surface of each sheave groove 8. For this reason, as the car 1 operates, the bottom surface of each sheave groove 8 wears over time, increasing the depth of each sheave groove 8. In Figures 4 and 5, the initial position of the bottom surface of the sheave groove 8 is indicated by a two-dot chain line.

[0033] Wear on the bottom surface of the sheave groove 8 progresses faster the greater the surface pressure acting on the bottom surface. Also, wear on the bottom surface of the sheave groove 8 progresses faster the greater the amount of slippage of the rope 5 within the sheave groove 8. In other words, the greater the difference between the tension on the car side portion of the rope 5 and the tension on the counterweight side portion, the greater the creep amount and the faster the wear progresses.

[0034] The cross-sectional shape of the sheave groove 8 is not limited to the first and second examples, and may be V-shaped.

[0035] Figure 6 is a block diagram showing a control system of the elevator system in Figure 1. The elevator control device 11 has, as functional blocks, an operation control unit 11a and a main transmission / reception unit 11b. The operation control unit 11a controls the operation of the car 1. The main transmission / reception unit 11b transmits and receives signals to and from devices external to the elevator control device 11.

[0036] Furthermore, the elevator control device 11 stores the history of the running pattern of the car 1 up to the present.

[0037] The maintenance device 30 has, as functional blocks, a maintenance transmitting / receiving unit 31 and a maintenance display unit 32. The maintenance transmitting / receiving unit 31 transmits and receives signals to and from devices external to the maintenance device 30.

[0038] A maintenance display (not shown) is provided in the maintenance device 30. The maintenance display unit 32 displays information required for maintenance work on the elevator device 10 on the maintenance display.

[0039] The elevator monitoring device 20 has, as functional blocks, a monitoring transmission / reception unit 21, a wear prediction unit 22, and a monitoring display unit 23. The monitoring transmission / reception unit 21 transmits and receives signals to and from devices external to the elevator monitoring device 20.

[0040] A monitoring display (not shown) is provided in the elevator monitoring device 20. The monitoring display unit 23 displays information required for monitoring the elevator device 10 on the monitoring display.

[0041] The wear prediction unit 22 calculates a plurality of predicted wear amounts using a wear prediction formula. The plurality of predicted wear amounts are predicted values ​​of future wear amounts that will occur in a set period in each of the plurality of sheave grooves 8. The wear prediction formula receives as input the tensions of the car-side portions and the counterweight-side portions of the plurality of ropes 5, the amount of slippage of the plurality of ropes 5, and the material hardness of the drive sheave 7.

[0042] The wear prediction unit 22 also outputs a plurality of predicted wear amounts to the monitoring display unit 23. The monitoring display unit 23 displays the plurality of predicted wear amounts on a monitoring display. The wear prediction unit 22 also outputs the plurality of predicted wear amounts to the maintenance device 30 via the monitoring transmission / reception unit 21. The maintenance display unit 32 displays the plurality of predicted wear amounts on a maintenance display.

[0043] As an example of a method for displaying a plurality of predicted wear amounts, a two-dimensional cross-sectional shape of the sheave groove 8 as shown in FIG. 4 or FIG. 5 may be displayed on a maintenance display.

[0044] The wear prediction unit 22 has a storage unit 24. The storage unit 24 stores a wear prediction formula and a plurality of predicted wear amounts.

[0045] A specific method for calculating a plurality of predicted wear amounts will be described below. The wear prediction formula is the following relational formula.

[0046] Wear amount = (f (slip amount, tension, sheave hardness) / lifting stroke) x reference running distance

[0047] The wear prediction unit 22 acquires the average value of the tension of the car-side portion of each of the multiple ropes 5 from the first tension measuring device 12 via the maintenance device 30. The average value of the tension of the car-side portion of each rope 5 is the average value of the tension fluctuation of the car-side portion for each rope 5 when the car 1 runs from the lowest floor to the top floor.

[0048] Furthermore, the wear prediction unit 22 acquires the average value of the tension in the counterweight side portion of each of the multiple ropes 5 from the second tension measuring device 13 via the maintenance device 30. The average value of the tension in the counterweight side portion of each rope 5 is the average value of the tension fluctuation in the counterweight side portion for each rope 5 when the car 1 travels from the lowest floor to the top floor.

[0049] Therefore, each average value includes tension fluctuations due to car 1 movement.

[0050] During maintenance and inspection, a maintenance worker measures the average value of the tension in the car side portion and the average value of the tension in the counterweight side portion of each of the multiple ropes 5, and inputs the measured values ​​into the maintenance device 30. The average tension value may be automatically transmitted to the maintenance device 30 without the intervention of the maintenance worker.

[0051] The calculation of the average value may be performed by the first tension measuring device 12 and the second tension measuring device 13, or may be performed by the maintenance device 30. Furthermore, the wear prediction unit 22 may calculate the average value of the tension based on the tensions acquired from the first tension measuring device 12 and the second tension measuring device 13.

[0052] Furthermore, the wear prediction unit 22 acquires data on the amount of rotation of the drive sheave 7 and data on the travel distance of the car 1 from the elevator control device 11. The data on the amount of rotation is a measurement value of the amount of rotation of the drive sheave 7 up to the present.

[0053] The wear prediction unit 22 calculates the amount of slippage of the rope 5 from the difference between the latest amount of rotation of the drive sheave 7 and the travel distance of the car 1.

[0054] It should be noted that the latest rotation amount of the drive sheave 7 and the travel distance of the car 1 may be values ​​obtained by running the car 1 back and forth during maintenance and inspection.

[0055] The sheave hardness is the material hardness of the drive sheave 7, and is input and stored in advance in the elevator monitoring device 20.

[0056] The wear prediction unit 22 inputs the average value of the tension in the cage side portion of each rope 5, the average value of the tension in the counterweight side portion of each rope 5, the amount of slippage of the rope 5, and the sheave hardness into a wear prediction formula, and calculates multiple predicted wear amounts.

[0057] In the wear prediction formula, f (slippage, tension, sheave hardness) is an estimate of the amount of wear that will occur when car 1 travels once over a distance equivalent to the distance from the bottom floor to the top floor in the current state. Also, f (slippage, tension, sheave hardness) is a relational expression described as a function of the slippage of rope 5, tension, and sheave hardness.

[0058] For example, the following relational expression can be used for f (slippage, tension, sheave hardness).

[0059] f(slippage, tension, sheave hardness) = α × (P(T)L) / H

[0060] Here, P(T) is the surface pressure acting on the sheave groove 8 and is a function of the tension T. L is the amount of slippage that occurs when the car 1 travels once over a distance equivalent to the distance from the lowest floor to the top floor. H is the sheave hardness. α is a proportionality constant.

[0061] The reference running distance is the average running distance that the car 1 runs within a set period. The wear prediction unit 22 estimates the amount of wear that will occur within the set period using a wear prediction formula. The set period is the interval between regular maintenance inspections, for example, three months. However, the set period is not limited to the interval between maintenance inspections and can be set to any period.

[0062] The tension substituted into the right-hand side of the wear prediction equation is used to calculate the surface pressure applied to the sheave groove 8. Therefore, the tension of the car-side portion is calculated by adding the data measured by the first tension measuring device 12 to the rope weight corresponding to the length of the car-side portion. Also, the tension of the counterweight-side portion is calculated by adding the data measured by the second tension measuring device 13 to the rope weight corresponding to the length of the counterweight-side portion.

[0063] The plurality of predicted wear amounts calculated by the wear prediction unit 22 are transmitted to the maintenance device 30 and displayed on the maintenance display. The maintenance worker checks the plurality of predicted wear amounts displayed on the maintenance display, and if the predicted wear amount exceeds a standard, plans regrooving work to make the depth of each sheave groove 8 uniform before the standard is exceeded.

[0064] This allows measures to be taken before problems due to wear of the sheave groove 8 occur.

[0065] Furthermore, as the elevator system operates, the diameter of each rope 5 also decreases over time. When the diameter of each rope 5 decreases, the effective diameter of the drive sheave 7 decreases, just as the sheave grooves 8 wear. In order to distinguish between the amount of wear of the sheave grooves 8 and the reduction in the diameter of the ropes 5, it is sufficient to subtract the amount of reduction in the diameter of the ropes 5 measured during maintenance inspection from the estimated amount of wear of the sheave grooves 8.

[0066] Fig. 7 is a flowchart showing the wear prediction process by the elevator monitoring device 20 of Fig. 6. When the wear prediction process is started, the elevator monitoring device 20 acquires data to be input into the wear prediction formula in step S101.

[0067] Next, in step S102, the elevator monitoring device 20 calculates a plurality of predicted wear amounts using the wear prediction formula. After that, in step S103, the elevator monitoring device 20 outputs the plurality of predicted wear amounts to the maintenance device 30. In addition, the elevator monitoring device 20 displays the plurality of predicted wear amounts on a monitoring display.

[0068] Fig. 8 is an explanatory diagram showing an example of the calculation results of the predicted wear amount in the sheave groove 8 into which the first rope 5a in Fig. 2 is inserted. The graph on the left of Fig. 8 shows the measurement results of the tension in the car side portion and the measurement results of the tension in the counterweight side portion. The graph on the right of Fig. 8 is a graph showing the current wear amount in the sheave groove 8 into which the first rope 5a is inserted and the future wear amount after the car 1 has run for a set period of time.

[0069] Fig. 9 is an explanatory diagram showing an example of the calculation results of the predicted wear amount in the sheave groove 8 into which the second rope 5b in Fig. 2 is inserted. The graph on the left of Fig. 9 shows the measurement results of the tension in the car side portion and the measurement results of the tension in the counterweight side portion. The graph on the right of Fig. 9 is a graph showing the current wear amount in the sheave groove 8 into which the second rope 5b is inserted and the future wear amount after the car 1 has run for a set period of time.

[0070] In the examples of FIGS. 8 and 9, (average value of Tc1 and Tw1)>(average value of Tc2 and Tw2).

[0071] 8 and 9, |Tc1-Tw1|>|Tc2-Tw2|. That is, the first rope 5a has larger surface pressure and creep amount values ​​than the second rope 5b. The larger the creep amount value, the faster the wear of the sheave groove 8 progresses, so the slope of the wear amount in the graph on the right of FIG. 8 is larger than the slope of the wear amount in the graph on the right of FIG. 9.

[0072] As shown in FIGS. 8 and 9, the progress of the wear amount can be predicted for each sheave groove 8.

[0073] The elevator monitoring method of the first embodiment includes a wear prediction step, in which a wear prediction formula is used to calculate a wear amount prediction value, which is a prediction value of the amount of future wear that will occur in the plurality of sheave grooves 8 over a set period of time.

[0074] In such an elevator monitoring device 20 and elevator monitoring method, a predicted wear amount value is calculated using a wear prediction formula that takes as input the tension of the car-side portion, the tension of the counterweight-side portion, the amount of slippage of the multiple ropes 5, and the material hardness of the drive sheave 7. This makes it possible to more accurately predict the future wear amount of the multiple sheave grooves 8.

[0075] Furthermore, the wear prediction unit 22 calculates the surface pressure acting on the multiple sheave grooves 8 using the tension of the multiple ropes 5 in a wear prediction formula. The wear prediction unit 22 also calculates the amount of creep as the amount of slippage from the difference between the amount of rotation of the drive sheave 7 and the traveling distance of the car 1. This makes it possible to more accurately predict the future amount of wear on the multiple sheave grooves 8.

[0076] Furthermore, the wear prediction unit 22 acquires the average value of the tension in the car-side portion and the average value of the tension in the counterweight-side portion of each of the plurality of ropes 5. Then, the wear prediction unit 22 calculates the surface pressure acting on each of the plurality of sheave grooves 8, and calculates a predicted wear amount value for each of the plurality of sheave grooves 8.

[0077] This makes it possible to more accurately predict the amount of future wear in each of the multiple sheave grooves 8. This allows a maintenance worker to refer to the multiple predicted wear amounts and loosen the tension on the ropes 5 applied to the sheave grooves 8 where wear is predicted to progress faster, thereby suppressing imbalances in the progression of wear.

[0078] Furthermore, each average value acquired by the wear prediction unit 22 includes tension fluctuations due to movement of the car 1. Therefore, the future amount of wear in each of the plurality of sheave grooves 8 can be predicted more accurately.

[0079] The elevator monitoring program of the first embodiment is a program that causes a computer to execute the elevator monitoring method described above.

[0080] Furthermore, the program is generally stored in a readable format in a storage medium, such as the memory 202 in Fig. 32. 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.

[0081] Embodiment 2 Next, an elevator system according to Embodiment 2 will be described. The configuration of the elevator system according to Embodiment 2 is the same as that shown in Fig. 1. The control system of the elevator system according to Embodiment 2 is the same as that shown in Fig. 6.

[0082] However, the wear prediction unit 22 of embodiment 2 obtains the average value of the average tensions of all the cage side portions of the multiple ropes 5 and the average value of the average tensions of all the counterweight side portions of the multiple ropes 5 as the tensions of the multiple ropes 5 input into the wear prediction formula.

[0083] Fig. 10 is an explanatory diagram showing an example of the calculation results of the predicted wear amount value according to embodiment 2. The graph on the left of Fig. 10 shows the measurement results of the average tension of all car-side portions and the measurement results of the average tension of all counterweight-side portions.

[0084] The average tension is the average value of the tension fluctuations of all ropes 5. a1 in Fig. 10 is the average value of the average tension obtained by averaging the tension fluctuations of all car side sections. a2 in Fig. 10 is the average value of the average tension obtained by averaging the tension fluctuations of all counterweight side sections.

[0085] The graph on the right of Fig. 10 is a graph showing the current average wear amount in all sheave grooves 8 and the future average wear amount after the car 1 has run for a set period of time. The average wear amount is the average value of the wear amounts of each of the multiple sheave grooves 8.

[0086] In this case too, each average value includes tension fluctuations due to car 1 movement.

[0087] Other configurations and monitoring methods in the second embodiment are the same as those in the first embodiment.

[0088] This configuration also makes it possible to more accurately predict the future wear amounts of the plurality of sheave grooves 8. Furthermore, by using the average value of the average tension, processing can be simplified.

[0089] The elevator monitoring program of the second embodiment is a program that causes a computer to execute the processing of the monitoring method by the elevator monitoring device 20 of the second embodiment. Moreover, the recording medium of the second embodiment is a computer-readable recording medium on which the elevator monitoring program of the second embodiment is recorded.

[0090] Embodiment 3 Next, Fig. 11 is a block diagram showing a control system of an elevator system according to embodiment 3. In embodiment 3, tension measurement data is transmitted from first tension measuring device 12 and second tension measuring device 13 to elevator control device 11. Elevator control device 11 transmits the tension measurement data to elevator monitoring device 20 in response to a request from elevator monitoring device 20 or automatically.

[0091] The elevator monitoring device 20 is installed, for example, in a maintenance center away from the elevator device 10.

[0092] Other configurations and monitoring methods in the third embodiment are the same as those in the first or second embodiment.

[0093] With this configuration as well, the future wear amounts of the plurality of sheave grooves 8 can be predicted more accurately.

[0094] The elevator monitoring program of the third embodiment is a program that causes a computer to execute the processing of the monitoring method by the elevator monitoring device 20 of the third embodiment. Moreover, the recording medium of the third embodiment is a computer-readable recording medium on which the elevator monitoring program of the third embodiment is recorded.

[0095] Embodiment 4 Next, Fig. 12 is a block diagram showing a control system of an elevator system according to embodiment 4. In embodiment 4, tension measurement data is sent directly from the first tension measuring device 12 and the second tension measuring device 13 to the elevator monitoring device 20, either in response to a request from the elevator monitoring device 20 or automatically.

[0096] Other configurations and monitoring methods in the fourth embodiment are the same as those in the first or second embodiment.

[0097] With this configuration as well, the future wear amounts of the plurality of sheave grooves 8 can be predicted more accurately.

[0098] The elevator monitoring program of the fourth embodiment is a program that causes a computer to execute the processing of the monitoring method by the elevator monitoring device 20 of the fourth embodiment. Moreover, the recording medium of the fourth embodiment is a computer-readable recording medium on which the elevator monitoring program of the fourth embodiment is recorded.

[0099] In addition, in the first to fourth embodiments, either the first tension measuring device 12 or the second tension measuring device 13 may be omitted. For example, when the second tension measuring device 13 is omitted, the tension of the counterweight side portion can be calculated from the design value of the weight of the counterweight 2.

[0100] Embodiment 5 Next, Fig. 13 is a block diagram showing a control system of an elevator system according to embodiment 5. In embodiment 5, neither first tension measuring device 12 nor second tension measuring device 13 is used. Instead, storage unit 24 stores in advance the average value of the average tensions of all car-side portions and the average value of the average tensions of all counterweight-side portions in embodiment 2.

[0101] The average value of the average tension in all car side sections is calculated using the formula: car mass / number of ropes. The average value of the average tension in all counterweight side sections is calculated using the formula: counterweight mass / number of ropes.

[0102] The wear prediction unit 22 inputs each of the average values ​​stored in advance into a wear prediction formula to calculate a plurality of predicted wear amounts.

[0103] Other configurations and monitoring methods in the fifth embodiment are the same as those in the second embodiment.

[0104] This configuration also makes it possible to more accurately predict the future wear amounts of the multiple sheave grooves 8. Furthermore, since each average value is stored in advance, the configuration can be simplified and the effort required for tension measurement can be reduced.

[0105] The elevator monitoring program of the fifth embodiment is a program that causes a computer to execute the processing of the monitoring method by the elevator monitoring device 20 of the fifth embodiment. Moreover, the recording medium of the fifth embodiment is a computer-readable recording medium on which the elevator monitoring program of the fifth embodiment is recorded.

[0106] In the first to fifth embodiments, the signal from the rotation sensor 14 may be transmitted directly to the elevator monitoring device 20 without going through the elevator control device 11.

[0107] Embodiment 6 Next, Fig. 14 is a block diagram showing a control system of an elevator system according to embodiment 6. In embodiment 6, rotation sensor 14 in embodiment 1 is omitted.

[0108] The wear prediction unit 22 stores two types of slippage calculation formulas, namely, a first slippage calculation formula and a second slippage calculation formula. The memory unit 24 stores the first slippage calculation formula and the second slippage calculation formula. Both of the two types of slippage calculation formulas are formulas for obtaining an estimated slippage value. The estimated slippage value is an estimated value of the slippage of the multiple ropes 5.

[0109] The wear prediction unit 22 uses the slippage amount estimated values ​​as the slippage amounts of the multiple ropes 5 to be input into the wear prediction formula.

[0110] In addition, the wear prediction unit 22 determines which of the two slippage calculation formulas to select depending on whether the ratio of the tension in the car side portion to the tension in the counterweight side portion exceeds the limit traction ratio Γ.

[0111] If the ratio of the tension in the car-side portion to the tension in the counterweight-side portion does not exceed the limit traction ratio Γ, the following first slippage calculation formula is selected.

[0112]

number

[0113] Here, consider the simplest model in which one rope is wound around one pulley. Fig. 15 is an explanatory diagram showing an equivalent model of a rope passing over a pulley. Fig. 16 is an explanatory diagram showing the equivalent model of Fig. 15 replaced with a model in a one-dimensional coordinate system.

[0114] 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 FIG. 16, 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.

[0115] 15 and 16, the rope model 51 is made up of three parts: a winding 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.

[0116] In the following description, the subscript i is added to variables relating to the winding side portion of the rope model 51, signifying that the variables are input side codes. The winding side portion is the portion of the rope model 51 that is upstream of the pulley model 50 in the movement direction of the rope model 51.

[0117] 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.

[0118] When the rope model 51 is wound by a small amount Δx due to a small rotation of the pulley model 50, the wound 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.

[0119] That is, the reeling amount Δx corresponds to the rope displacement amount when tension is applied, and is the sum of the rope elongation amount due to tension and the free rope length ΔLi, which is the rope displacement amount when tension is not applied. As shown in Figure 7, the rope displacement amounts when tension is not applied for the reeling side part, the unreeling side part, and the part that moves integrally with the pulley are all the same free rope length ΔLi.

[0120] Δx=ΔLi+Δui (1.1)

[0121] The rope elongation Δui in the winding-side portion is calculated from the tension Ti in the winding-side portion. On the other hand, the tension in the unwinding-side portion is To, so the rope elongation Δuo in the unwinding-side portion is different from the rope elongation Δui in the winding-side portion.

[0122] 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.

[0123] Δcr=Δuo- Δui

[0124] The amount of creep when car 1 travels from the bottom floor to the top floor is found by integrating the amount of creep Δcr from 0 over the length of the ascending / descending stroke TR.

[0125] On the other hand, when the ratio of the tension in the car side portion to the tension in the counterweight side portion exceeds the limit traction ratio Γ, the following second slippage calculation formula is selected.

[0126] Estimated slip amount = (Tw1(x)-ΓTc1(x)) / (kw(x)+Γkc(x))

[0127] In the first rope 5a in Fig. 2, when the ratio of the tension in the car side portion to the tension in the counterweight side portion exceeds the limit traction ratio Γ, the amount of slippage of the first rope 5a on the drive sheave 7 is calculated using the second slippage calculation formula. Note that kc is the stiffness of the car side portion of the first rope 5a, and kw is the stiffness of the counterweight side portion of the first rope 5a.

[0128] When calculating an estimated slippage amount for the second rope 5b in FIG. 2, Tc2 and Tw2 are substituted into the tension term of the second slippage amount calculation formula.

[0129] The amount of slippage that occurs when the traction ratio limit Γ is exceeded is greater than the amount of creep that occurs when the traction ratio limit Γ is not exceeded.

[0130] Fig. 17 is a flowchart showing the wear prediction process by the elevator monitoring device 20 of Fig. 14. When the wear prediction process is started, the elevator monitoring device 20 acquires necessary data in step S201.

[0131] Next, in step S202, the elevator monitoring device 20 determines whether the tension ratio is equal to or less than the limit traction ratio Γ. If the tension ratio is equal to or less than the limit traction ratio Γ, that is, if the tension ratio does not exceed the limit traction ratio Γ, the elevator monitoring device 20 selects the first slippage calculation formula in step S203.

[0132] If the tension ratio is not equal to or less than the limit traction ratio Γ, that is, if the tension ratio exceeds the limit traction ratio Γ, the elevator monitoring device 20 selects the second slippage calculation formula in step S204.

[0133] Thereafter, in step S205, the elevator monitoring device 20 calculates a slippage amount estimated value using the first slippage amount calculation formula or the second slippage amount calculation formula. Then, in step S206, the elevator monitoring device 20 calculates a plurality of wear amount predicted values ​​using the wear prediction formula.

[0134] After that, in step S207, the elevator monitoring device 20 outputs the plurality of predicted wear amounts to the maintenance device 30. In addition, the elevator monitoring device 20 displays the plurality of predicted wear amounts on a monitoring display.

[0135] Other configurations and monitoring methods in the sixth embodiment are the same as those in the first or second embodiment.

[0136] With such a configuration and monitoring method, the future wear amount of the plurality of sheave grooves 8 can be predicted more accurately.

[0137] Furthermore, the wear prediction unit 22 uses, as the slippage, an estimated slippage value calculated using a slippage calculation formula, which allows for more accurate prediction of future wear of the plurality of sheave grooves 8.

[0138] Furthermore, the wear prediction unit 22 determines whether to select the first slippage calculation formula or the second slippage calculation formula depending on whether the ratio of the tension in the car-side portion to the tension in the counterweight-side portion exceeds the limit traction ratio. Therefore, even when a large slippage of the multiple ropes 5 occurs due to the tension ratio exceeding the limit traction ratio Γ, the future wear of the multiple sheave grooves 8 can be predicted more accurately.

[0139] The elevator monitoring program of the sixth embodiment is a program that causes a computer to execute the processing of the monitoring method by the elevator monitoring device 20 of the sixth embodiment. Moreover, the recording medium of the sixth embodiment is a computer-readable recording medium on which the elevator monitoring program of the sixth embodiment is recorded.

[0140] Embodiment 7 Next, an elevator system according to Embodiment 7 will be described. The configuration of the elevator system according to Embodiment 7 is the same as that shown in FIG. 1. The control system of the elevator system according to Embodiment 7 is the same as that shown in FIG.

[0141] In the seventh embodiment, the first tension measuring device 12 continuously measures the tension at each moment in the car side portion of each of the plurality of ropes 5. In addition, the second tension measuring device 13 continuously measures the tension at each moment in the counterweight side portion of each of the plurality of ropes 5.

[0142] The elevator control device 11 stores information about the load amount in the car obtained from a weighing device (not shown). The elevator control device 11 also stores history data from the start of use of the elevator device 10 to the present for each of the car travel distance, car stopped positions, and car load amount.

[0143] The wear prediction unit 22 inputs the momentary tension data into a wear prediction formula to calculate an instantaneous value of the amount of wear for each of the plurality of sheave grooves 8. The wear prediction unit 22 also accumulates each instantaneous value of the amount of wear to calculate the predicted amount of wear for each sheave groove 8.

[0144] The wear prediction unit 22 also updates the parameters of the wear prediction formula using past state quantities, which include past tension data, past rotation amount of the drive sheave 7, past travel distance of the car 1, past wear amount, and past car load amount.

[0145] In this way, the wear prediction formula is adjusted for each elevator device 10 by using past data to update the constants included in the wear prediction formula so as to match the wear gradient of the actual measured value.

[0146] Fig. 18 is an explanatory diagram illustrating a method for calculating a predicted wear amount value in the seventh embodiment. Fig. 18 shows a method for calculating a predicted wear amount value of the sheave groove 8 corresponding to the first rope 5a in Fig. 2.

[0147] Figure 18(a) shows the measured tension of the first rope 5a. When the car 1 is located at position P1, the tension in the car-side portion is Tca1 and the tension in the counterweight-side portion is Twa1. When the car 1 is located at position P2, the tension in the car-side portion is Tca2 and the tension in the counterweight-side portion is Twa2.

[0148] In this way, it is assumed that the tension varies depending on the car position, and the surface pressure acting on the sheave groove 8 varies depending on the car position.

[0149] For example, when car 1 is located at position P1, the surface pressure is small and the instantaneous value of the amount of wear is shown by the straight line E1 in Figure 18(b). Also, when car 1 is located at position P2, the surface pressure is larger than when car 1 is located at position P1 and the instantaneous value of the amount of wear is shown by the straight line E2 in Figure 18(b).

[0150] Then, as shown in FIG. 18(c), E3, which is the slope of the accumulated wear amount, is output from the accumulation of such instantaneous wear amount values.

[0151] In the seventh embodiment, the wear amount that is expected if the trend of the slope E3 from the past to the present continues into the future is calculated as the predicted wear amount value.

[0152] 19 is a flowchart showing the wear prediction process by the elevator monitoring device 20 according to the seventh embodiment. When the wear prediction process is started, the elevator monitoring device 20 acquires the latest data in step S301. The latest data includes the latest tension data, the latest rotation amount of the drive sheave 7, and the latest travel distance of the car 1.

[0153] Next, in step S302, the elevator monitoring device 20 calculates an instantaneous value of the amount of wear using the wear prediction formula.

[0154] Thereafter, in step S303, the elevator monitoring device 20 accumulates the instantaneous wear amount values ​​to estimate the wear amount. The elevator monitoring device 20 also updates the parameters of the wear prediction formula based on the past state quantities. The elevator monitoring device 20 also calculates the amount of change in the wear amount based on data including the past history.

[0155] Thereafter, in step S304, the elevator monitoring device 20 calculates a plurality of predicted wear amounts for the future for the set period. Then, in step S305, the elevator monitoring device 20 outputs the plurality of predicted wear amounts to the maintenance device 30. In addition, the elevator monitoring device 20 displays the plurality of predicted wear amounts on a monitoring display.

[0156] Other configurations and monitoring methods in the seventh embodiment are the same as those in the first or second embodiment.

[0157] With such a configuration and monitoring method, the future wear amount of the plurality of sheave grooves 8 can be predicted more accurately.

[0158] Furthermore, the wear prediction unit 22 calculates an instantaneous value of the wear amount, and calculates a predicted wear amount value by accumulating the instantaneous value of the wear amount. Therefore, the future wear amounts of the plurality of sheave grooves 8 can be predicted more accurately.

[0159] Furthermore, wear prediction unit 22 updates the parameters of the wear prediction formula based on past state quantities. This allows the wear prediction formula to be optimized for each elevator device 10, making it possible to more accurately predict the future amounts of wear of the multiple sheave grooves 8.

[0160] The elevator monitoring program of the seventh embodiment is a program that causes a computer to execute the processing of the monitoring method by the elevator monitoring device 20 of the seventh embodiment. Moreover, the recording medium of the seventh embodiment is a computer-readable recording medium on which the elevator monitoring program of the seventh embodiment is recorded.

[0161] In the seventh embodiment, the slippage estimated value calculated by the slippage calculation formula shown in the sixth embodiment may be used as the slippage to be input to the wear prediction formula. In this case, the slippage calculation formula may be updated based on past state quantities.

[0162] Embodiment 8 Next, an elevator system according to embodiment 8 will be described. The configuration of the elevator system according to embodiment 8 is the same as that shown in FIG. 1. The control system of the elevator system according to embodiment 8 is the same as that shown in FIG.

[0163] In the eighth embodiment, the first tension measuring device 12 continuously measures the tension at each moment in the car side portion of each of the plurality of ropes 5. The second tension measuring device 13 continuously measures the tension at each moment in the counterweight side portion of each of the plurality of ropes 5.

[0164] The measurement results from the first tension measuring device 12 and the second tension measuring device 13 are sent to the elevator monitoring device 20 via the maintenance device 30.

[0165] A tension model, which will be described later, is stored in the wear prediction unit 22. That is, the storage unit 24 stores the tension model. The wear prediction unit 22 uses tension analysis values ​​as the tension of the car-side portion and the tension of the counterweight-side portion. The tension analysis values ​​are calculated using the tension model.

[0166] The wear prediction unit 22 inputs into the tension model the measured values ​​from the first tension measuring device 12 and the second tension measuring device 13, and the instantaneous wear amount value calculated in the same manner as in embodiment 7. As a result, the wear prediction unit 22 calculates, as tension analysis values, analysis values ​​of tension fluctuations in the car side portion and the counterweight side portion when the car 1 travels back and forth between the lowest floor and the top floor.

[0167] 20 is a flowchart showing the wear prediction process by the elevator monitoring device 20 according to the eighth embodiment. When the wear prediction process starts, the elevator monitoring device 20 acquires the latest data in step S401. The latest data includes the latest tension data, the latest rotation amount of the drive sheave 7, and the latest travel distance of the car 1.

[0168] Next, in step S402, the elevator monitoring device 20 calculates an instantaneous value of the amount of wear using the wear prediction formula.

[0169] Thereafter, in step S403, the elevator monitoring device 20 accumulates the instantaneous wear amount values ​​to estimate the wear amount. Also, the elevator monitoring device 20 updates the parameters of the wear prediction formula based on the past state quantities.

[0170] Next, in step S404, the elevator monitoring device 20 determines whether the amount of wear for the designated period has been calculated.

[0171] If the amount of wear for the specified period has not been calculated, the elevator monitoring device 20 adds the time for one step to the period Δt in step S405. Then, the elevator monitoring device 20 calculates a tension analysis value using the tension model in step S406.

[0172] Thereafter, in step S407, the elevator monitoring device 20 determines whether the tension ratio is equal to or less than the limit traction ratio Γ. If the tension ratio is equal to or less than the limit traction ratio Γ, that is, if the tension ratio does not exceed the limit traction ratio Γ, the elevator monitoring device 20 selects the first slippage calculation formula in step S408.

[0173] If the tension ratio is not equal to or less than the limit traction ratio Γ, that is, if the tension ratio exceeds the limit traction ratio Γ, the elevator monitoring device 20 selects the second slippage calculation formula in step S409.

[0174] Thereafter, in step S410, the elevator monitoring device 20 calculates the slippage estimated value using the first slippage calculation formula or the second slippage calculation formula, and returns to the processing of step S403.

[0175] In the process of step S404, if the wear amount for the designated period has been calculated, in step S411, the elevator monitoring device 20 outputs a plurality of predicted wear amount values ​​to the maintenance device 30. In addition, the elevator monitoring device 20 displays the plurality of predicted wear amount values ​​on the monitoring display.

[0176] In this way, the instantaneous wear amount values ​​of the sheave grooves 8 are calculated for a pre-specified period, and the cumulative value of the instantaneous wear amount values ​​is displayed on the maintenance display of the maintenance device 30 as the predicted wear amount value of each sheave groove 8.

[0177] Other configurations and monitoring methods in the eighth embodiment are the same as those in the seventh embodiment.

[0178] With such a configuration and monitoring method, the future wear amount of the plurality of sheave grooves 8 can be predicted more accurately.

[0179] Furthermore, the wear prediction unit 22 uses tension analysis values ​​as the tension of the car-side portion and the tension of the counterweight-side portion, which allows for more accurate prediction of the future wear amounts of the plurality of sheave grooves 8.

[0180] The elevator monitoring program of the eighth embodiment is a program that causes a computer to execute the processing of the monitoring method by the elevator monitoring device 20 of the eighth embodiment. Moreover, the recording medium of the eighth embodiment is a computer-readable recording medium on which the elevator monitoring program of the eighth embodiment is recorded.

[0181] The tension model used in the eighth embodiment will be described below. The tension model is a model consisting of a plurality of equations of motion, in which the car side portion and the counterweight side portion are each modeled as springs.

[0182] Figure 21 is an explanatory diagram showing the equivalent model of Figure 15, divided into a winding-side portion and a supply-side portion. In Figure 21, the winding-side portion and the supply-side portion are each 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.

[0183] In Figure 21, yi indicates the displacement of the upper end of the winding-side portion, and yo indicates 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:

[0184] Ti=ki(yi-xi)=(EA / Li)(0-x'i) (1.3)

[0185] 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.

[0186] Also, x'i is the initial elongation of the bottom end of the take-up side section, and 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.

[0187] The winding-side portion is wound around the pulley model 50 while being subjected to tension Ti, and the following relational expression is obtained:

[0188] Ti=(EA / ΔLi)Δui (1.4)

[0189] 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, regardless of the rope stiffness, as shown in Figure 16. Therefore, the balance of forces after the rope has been wound up by Δx is given by the following equation.

[0190] Ti=(EA / (Li-ΔLi))(yi-xi) =(EA / (Li-ΔLi)){yi-(x'i+Δx)} (1.5)

[0191] The tension Ti in the take-up side section is calculated from the difference in displacement yi-xi between the top and bottom ends of the take-up side section. This equation also gives the relationship that the displacement yi of the top end of the take-up side section must satisfy.

[0192] yi=(Ti / EA)(Li-ΔLi)+x'i+Δx (1.6)

[0193] By rearranging the above equation using equations (1.1), (1.3), and (1.4), the following equation is obtained.

[0194] yi=(Ti / EA)(Li-ΔLi)-(Ti / EA)Li+ΔLi+Δui =-(Ti / EA)ΔLi+ΔLi+Δui =-Δui+ΔLi+Δui=ΔLi (1.7)

[0195] 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.

[0196] Next, consider the behavior of the two winding sections that are subjected to different tensions. In an actual elevator, the lower ends of the two winding sections are connected to car 1 or counterweight 2, and the amount of displacement is the same. For this reason, the winding 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 section that is subjected to tension Ti2 has its lower end pulled down, increasing tension.

[0197] In the model used in this study, the amount of lift at the upper ends of the two winding-side sections is not a uniform Δx, but is different from each other, being the free lengths ΔLi1 and ΔLi2 of the rope 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 winding-side sections is both Δx.

[0198] Next, the feed-side portion will be described. From Fig. 21, the relational expression for the feed-side portion when stationary is as follows:

[0199] To=ko(yo-xo)=(EA / Lo)(0-x'o) (1.8)

[0200] 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.

[0201] Also, x'o is the initial elongation amount at 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.

[0202] When the winding-side portion is wound by Δx, the unwinding-side portion becomes longer by the free length ΔLi of the rope on the pulley model 50. In addition, due to the tension To of the unwinding-side portion, the free length ΔLi of the rope in the unwinding-side portion is extended by Δuo.

[0203] To = (EA / ΔLi)Δuo (1.9)

[0204] Therefore, when rope model 51 is wound slightly by Δx on 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 by Δx is given by the following equation.

[0205] To=(EA / (Lo+ΔLi))(yo-xo) =(EA / (Lo+ΔLi)){ yo-(x'o-ΔLi-Δuo)} (1.10)

[0206] The tension To of the payout side portion is calculated from the displacement difference yo-xo between the upper and lower ends of the payout side portion. From this equation, the relational expression that the displacement yo of the upper end of the payout side portion must satisfy is obtained.

[0207] yo=(To / EA)(Lo+ΔLi)+x'o-ΔLi-Δuo (1.11)

[0208] The above equation can be rearranged using equations (1.11), (1.8), and (1.9).

[0209] yo=(To / EA)(Lo+ΔLi)-(To / EA)Lo-ΔLi-Δuo =(To / EA)ΔLi-ΔLi-Δuo =Δuo-ΔLi-Δuo=-ΔLi (1.12)

[0210] 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.

[0211] Note that the displacement Δxi=ΔLi+Δui at the bottom end of the winding-side portion, while the displacement xo at the bottom end of the unwinding-side portion is different from ΔLi+Δuo. This difference is the creep amount Δcr of the rope model 51 on the pulley model 50.

[0212] Δcr=Δuo-Δui=(ΔLi / EA)(To-Ti) (1.13)

[0213] The discussion up to this point has been on the formulation for the case where pulley model 50 rotates counterclockwise in Fig. 15, as shown in Fig. 15. On the other hand, when considering the relational equation for the case where pulley model 50 rotates clockwise in Fig. 15, 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. 15, it is necessary to replace Ti in equation (1.4) with To in Fig. 15.

[0214] 15 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.

[0215] Based on the above results, the model of winding the rope model 51 around the pulley model 50 can be organized as follows:

[0216] 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 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. The rope stiffness ko of the payout side 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 payout side. The lengths Li and Lo when calculating the rope stiffness ki and ko are set to the free length of the rope with no tension acting on the rope model 51.

[0217] 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 payout side is defined as the rope stiffness ko multiplied by the difference in displacement between the upper and lower ends yo-xo.

[0218] The displacement of the end of the pulley model 50 side in the winding side portion is defined as the value obtained by subtracting the rope elongation amount Δui in the winding side portion from the minute winding amount Δx of the rope model 51 on the pulley model 50, and is equivalent to the free length ΔLi of the rope relative to the winding amount Δx. The displacement of the end of the pulley model 50 side in the unwinding side is defined as the value obtained by subtracting the rope elongation amount Δui in the winding side part from the minute winding amount Δx of the rope model 51 on the pulley model 50, and is equivalent to the free length ΔLi of the rope relative to the winding amount Δx. The amount of rope elongation on the pulley model 50 is calculated from the tension Ti on the winding side.

[0219] Next, Fig. 22 is an explanatory diagram showing a model of the elevator in Fig. 1. Fig. 22 shows the simplest model, which is a 1:1 roping system with one rope.

[0220] Each element of the elevator is modeled as a spring and mass system. The rope 5 is modeled as a mass element on the drive sheave 7, and as a spring element on both the winding and unwinding sides.

[0221] In FIG. 22, Js is the moment of inertia of the drive sheave 7. Jr is the moment of inertia of the rope 5 on the drive sheave 7. Jr is the moment of inertia due to the mass of the part of the rope 5 that moves integrally with the drive sheave 7.

[0222] Mc is the mass of car 1. Mw is the mass of counterweight 2. msc is the mass of the car side shackle. msw is the mass of the counterweight side shackle. In Figure 1, the car side shackle and the counterweight side shackle are omitted.

[0223] mrc is the mass of the car side portion of the rope 5. mrw is the mass of the counterweight side portion of the rope 5. The car side portion is the portion of the rope 5 located on the car 1 side of the drive sheave 7. The counterweight side portion is the portion of the rope 5 located on the counterweight 2 side of the drive sheave 7. The above are parameters related to inertia elements.

[0224] 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 rope 5. krw is the stiffness of the counterweight side portion of the rope 5. These are parameters related to stiffness elements.

[0225] θs is the rotation angle of the drive sheave 7. θr is the rotation angle of the rope 5 on the drive sheave 7. xc is the displacement of the car 1. xw is the displacement of the counterweight 2. 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 part of the rope 5. xrw is the displacement of the counterweight side part of the rope 5.

[0226] The equation of motion expressed as a differential equation that does not take into account the damping term due to damping elements is as follows: Here, d^2 / dt^2 is used as the operator indicating the second-order differentiation operation with respect to time t.

[0227] Mc(d^2 / dt^2)xc-ksc(xsc-xc)=-Mc g (1.14)

[0228] Mw(d^2 / dt^2)xw-ksw(xsw-xw)=-Mw g (1.15)

[0229] msc(d^2 / dt^2)xsc+ksc(xsc-xc)-krc(xrc-xsc) =-msc g (1.16)

[0230] msw(d^2 / dt^2)xsw+ksw(xsw-xw)-krw(xrw-xsw) =-msw g (1.17)

[0231] mrc(d^2 / dt^2)xrc+krc(xrc-xsc)-krc(-R1θr-xrc) =-mrc g (1.18)

[0232] mrw(d^2 / dt^2)xrw+krw(xrw-xsw)-krw(R1θr-xrw) =-mrw g (1.19)

[0233] Js(d^2 / dt^2)θs=τ-λ (1.20)

[0234] Jr(d^2 / dt^2)θr-krcR1(-R1θr-xrc)+krwR1(R1θr-xrw) =λ (1.21)

[0235] Here, R1 is the radius of the drive sheave 7. g is the gravitational acceleration. τ is the drive torque applied to the drive sheave 7. λ is the restraint torque acting between the drive sheave 7 and the rope 5.

[0236] On the drive sheave 7, the drive sheave 7 and the rope 5 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 7 and the rope 5 and the winding angle of the rope 5 around the drive sheave 7.

[0237] In this case, the condition to be satisfied for the ratio of the tension Ti in the winding side portion of the rope 5 to the tension To in the unwinding 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.

[0238] (1 / Γ)<(To / Ti)<Γ (1.22)

[0239] (d / dt)θs-(d / dt)θr=0 (1.23)

[0240] The restraining torque λ acts on the drive sheave 7 and rope 5 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 rope 5 slips relative to the drive sheave 7, resulting in a difference in rotational speed between the drive sheave 7 and the rope 5.

[0241] (d / dt)θs-(d / dt)θr≠0 (1.24)

[0242] Below, we will explain the behavior when the car 1 descends, that is, when the drive sheave 7 rotates counterclockwise in Figure 22. We will consider the balance state at time t+Δt, after an infinitesimal time Δt has elapsed, from the balance state at time t. When the car 1 descends during the infinitesimal time Δt, the amount of winding Δx on the drive sheave 7 is given by the following equation.

[0243] Δx=R1Δθr=ΔL+Δu (1.25)

[0244] Here, ΔL is the free length of the rope relative to the minute amount of winding Δx when the car 1 descends, that is, the length of the rope when no tension is applied. Also, Δu is the amount of rope elongation relative to the minute amount of winding Δx when the car 1 descends.

[0245] Each sheave groove 8 is worn down over time by the rope 5. The radius R1 is the radius of the drive sheave 7 in each sheave groove 8, so if the amount of wear in multiple sheave grooves 8 differs from one another, the radius R1 will differ slightly depending on the sheave groove 8.

[0246] Such a difference in radius R1 causes a difference in the amount of winding, resulting in a difference in tension among the plurality of ropes 5.

[0247] If the tension acting on the counterweight side portion of the rope 5 is Tw, Δu satisfies the following equation.

[0248] Tw=(EA / ΔL)Δu → Δu=(Tw / EA)ΔL (1.26)

[0249] Therefore, the free rope length ΔL can be calculated from the minute winding amount Δx.

[0250] Δx=(1+(Tw / EA))ΔL → ΔL=Δx / (1+(Tw / EA)) (1.27)

[0251] From this equation, the length Lc of the rope 5 on the car side and the length Lw of the rope 5 on the counterweight side are given by the following equations.

[0252] Lo(t+Δt)=Lc(t+Δt)=Lc(t)+ΔL, Li(t+Δt)=Lw(t+Δt)=Lw(t)-ΔL (1.28)

[0253] The winding amount at time t+Δt, the corresponding free length of the rope, and the amount of rope elongation are given by the following equations.

[0254] x(t+Δt)=x(t)+Δx, L(t+Δt)=L(t)+ΔL, u(t+Δt)=u(t)+Δu (1.29)

[0255] The amount of rope taken up by the drive sheave 7, x(t+Δt)=Rθr(t+Δt), includes the amount of rope stretch. However, in order to calculate the tension generated in the take-up side of the rope 5 and the tension generated in the pay-out side of the rope 5, it is necessary to use Rθr as the free length L of the rope rather than using it as the take-up amount.

[0256] The free rope length L can be calculated using the following formula:

[0257] x(t+Δt)=R1θr(t+Δt) =L(t+Δt)+u(t+Δt) → L=R1θr-u (1.30)

[0258] Therefore, the tension Ti generated in the winding side portion of the rope 5 is given by the following formula.

[0259] Ti=Tw=ki(L-xrw) =krw(L-xrw)=krw(R1θr-u-xrw) (1.31)

[0260] The tension To generated in the payout side portion of the rope 5 is given by the following formula.

[0261] To=ko(-L-xrc) =krc(-L-xrc)=krc(-R1θr+u-xrc) (1.32)

[0262] From these equations, the winding amount parts in the equations of motion (1.18), (1.19), and (1.21) are modified as follows:

[0263] R1θr → R1θr-u (1.33)

[0264] Next, we will explain the behavior when the car 1 ascends, that is, when the drive sheave 7 rotates clockwise in Figure 21. When the car 1 ascends in an infinitesimal time Δt, the amount of winding Δx on the drive sheave 7 is given by the following equation. Note that since the counterclockwise direction in Figure 21 is considered positive, when the drive sheave 7 rotates clockwise in Figure 21, the amount of winding Δx becomes a negative value.

[0265] Δx=R1θr=ΔL+Δu (1.34)

[0266] Here, Δu is the amount of rope stretch relative to the minute amount of winding Δx when the car 1 is rising, and is a negative value.

[0267] If the tension acting on the car side portion of the rope 5 is Tc, Δu satisfies the following equation.

[0268] Tc=(EA / ΔL)Δu → Δu=(Tc / EA)ΔL (1.35)

[0269] Therefore, the free rope length ΔL can be calculated from the minute winding amount Δx.

[0270] Δx=(1+(Tc / EA))ΔL → ΔL=Δx / (1+(Tc / EA)) (1.36)

[0271] From this equation, the length Lc of the rope 5 on the car side and the length Lw of the rope 5 on the counterweight side are given by the following equations.

[0272] Li(t+Δt)=Lc(t+Δt)=Lc(t)+ΔL, Lo(t+Δt)=Lw(t+Δt)=Lw(t)-ΔL (1.37)

[0273] 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.

[0274] The free length L of the rope when the car 1 is rising can be calculated using the following formula.

[0275] x(t+Δt)=R1θr(t+Δt) =L(t+Δt)+u(t+Δt) → L=R1θr-u (1.38)

[0276] Therefore, the tension Ti generated in the winding side portion of the rope 5 is given by the following formula.

[0277] Ti=Tc=ki(-L-xrc) =krc(-L-xrc)=krc(-R1θr+u-xrc) (1.39)

[0278] The tension To generated in the payout side portion of the rope 5 is given by the following formula.

[0279] To=ko(L-xrw) =krw(L-xrw)=krw(R1θr-u-xrw) (1.40)

[0280] From these equations, the winding amount parts in the equations of motion (1.18), (1.19), and (1.21) are modified as follows:

[0281] R1θr → R1θr-u (1.41)

[0282] 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.

[0283] Regardless of the direction of travel of the car 1, the rope length Lc on the car 1 side and the rope length Lw on the counterweight 2 side can be obtained by the following formulas. In other words, the length of the winding side portion and the length of the unwinding side portion are calculated from the free rope length ΔL.

[0284] Lc(t+Δt)=Lc(t)+ΔL,Lw(t+Δt)=Lw(t)-ΔL (1.42)

[0285] Here, ΔL satisfies the following equation:

[0286] When the car descends: ΔL = (1.27) When the car ascends: ΔL = (1.36) (1.43)

[0287] The winding amount parts in the equations of motion (1.18), (1.19), and (1.21) are modified as follows:

[0288] R1θr → L=R1θr-u (1.44)

[0289] 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 in the winding side portion.

[0290] Here, the relational expression of the correction amount u over a very short time period is as follows:

[0291] u(t+Δt)=u(t)+Δu (1.45)

[0292] When the car descends: Δu = (1.26) When the car ascends: Δu = (1.35) (1.46)

[0293] 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 in the winding side portion.

[0294] The above relational expressions also hold true when there is one or more pulleys other than the drive sheave 7, which is a sheave, and also hold true regardless of the number of ropes 5.

[0295] Next, as an example, calculation results are shown for a 1:1 roping elevator in which two ropes 5 are wound around the drive sheave 7 in a single-wrap manner. In the calculations below, the tensions of the two ropes 5 are calculated by changing the car position when the depths of the two sheave grooves 8 are equal and when they are different.

[0296] Fig. 23 is a graph showing the relationship between the tension of the two ropes 5 and the car position when the depths of the two sheave grooves 8 are equal. Fig. 24 is a graph showing the relationship between the tension of the two ropes 5 and the car position when there is a difference of 0.2 mm in the depths of the two sheave grooves 8. Fig. 25 is a graph showing the relationship between the calculated values ​​of the tension of the two ropes 5 and the car position, compared with multiple actual measured values, when there is a difference of 0.7 mm in the depths of the two sheave grooves 8.

[0297] 23, 24, and 25, car 1 travels back and forth between the top floor and the bottom floor. Car 1 indicates the tension in the car-side portion of one rope 5. Car 2 indicates the tension in the car-side portion of the other rope 5.

[0298] CWT1 indicates the tension of the counterweight side portion of one rope 5. CWT2 indicates the tension of the counterweight side portion of the other rope 5. The measured values ​​of each tension are the measured values ​​of the tension acting on the shackle spring.

[0299] When the depths of the two sheave grooves 8 are equal to each other, the tension exhibits a constant value regardless of the car position, as shown in FIG.

[0300] On the other hand, the fact that the depths of the two sheave grooves 8 are different from each other corresponds to the radius R1 of the drive sheave 7 in the equation of motion being different for each rope 5. When there is a difference in the depths of the two sheave grooves 8, the tension when the car 1 is ascending and the tension when it is descending trace different trajectories, as shown in Figure 24. In Figure 24, the sheave grooves 8 corresponding to Car2 and CWT2 are deeper than the sheave grooves 8 corresponding to Car1 and CWT1.

[0301] 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.

[0302] When the difference in depth between the two sheave grooves 8 becomes large, the tension ratio between the winding side portion and the unwinding side portion exceeds the limit traction ratio Γ, the rope 5 slips relative to the drive sheave 7, and the gradient of the tension fluctuation changes midway, as shown in Figure 25. Figure 25 shows that the analysis method of the first embodiment makes it possible to accurately calculate tension fluctuation, including rope slippage behavior.

[0303] Because the limit traction ratio Γ is a function of the coefficient of friction between the drive sheave 7 and the rope 5, 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 change in the coefficient of friction.

[0304] The tensions measured by the first tension measuring device 12 and the second tension measuring device 13 may be tensions measured with the car 1 stopped at any position in the elevator shaft. According to the elevator monitoring device 20 of the eighth embodiment, the tension model can be used to calculate tensions at positions other than the measurement position as tension analysis values.

[0305] Furthermore, the tension measured by the first tension measuring device 12 and the second tension measuring device 13 may be a continuous tension measured while the car 1 is traveling. In this case, the travel section of the car 1 may be from the lowest floor to the top floor, or may be between any two points.

[0306] Furthermore, in the eighth embodiment, the first tension measuring device 12 and the second tension measuring device 13 may be permanently installed sensors, or may be sensors that are attached only during maintenance and inspection. In the elevator monitoring device 20 of the eighth embodiment, by inputting information about the tension measured during maintenance and inspection, the car travel distance, the car position, and the load amount in the car into a tension model, it is possible to calculate a tension analysis value and also to calculate a plurality of predicted wear amounts.

[0307] 26 is a flowchart showing a wear prediction process by the elevator monitoring device 20 according to a modification of the embodiment 8. In this modification, the processes of steps S407 to S410 in FIG. 20 are omitted.

[0308] In this way, the determination regarding the limit traction ratio Γ may be omitted.

[0309] Furthermore, in the eighth embodiment, the rotation sensor 14 may be omitted, similar to the sixth embodiment shown in Fig. 14. In this case, the slippage amount estimated value is calculated, similar to the sixth embodiment.

[0310] Embodiment 9 Next, Fig. 27 is a schematic configuration diagram showing an elevator system according to a ninth embodiment. The elevator device 10 of the ninth embodiment is a machine room-less elevator of a 2:1 roping system. The hoisting machine 3 is installed at the top of the hoistway. The elevator control device 11 is installed inside the hoistway.

[0311] A car hoisting sheave 1a is provided on the car 1. A counterweight hoisting sheave 2a, which is also a sheave, is provided on the counterweight 2.

[0312] At the top of the hoistway, car side rope stops (not shown) and counterweight side rope stops (not shown) are installed. A first end of each rope 5 is connected to the car side rope stop. A second end of each rope 5 is connected to the counterweight side rope stop.

[0313] Each rope 5 is wound around the car sheave 1a, the drive sheave 7, and the counterweight sheave 2a, in that order from the first end. A first tension measuring device 12 is provided at the first end. A second tension measuring device 13 is provided at the second end.

[0314] Each rope 5 has a first section, a second section, a third section, and a fourth section. The first section is the section between the car side cleat and the car hoisting sheave 1a. The second section is the section between the car hoisting sheave 1a and the drive sheave 7. The third section is the section between the drive sheave 7 and the counterweight hoisting sheave 2a. The fourth section is the section between the counterweight hoisting sheave 2a and the counterweight side cleat.

[0315] A tension force Tca acts on the first portion due to the weight of car 1. A tension force Tcm acts on the second portion due to the weight of car 1. A tension force Twm acts on the third portion due to the weight of counterweight 2. A tension force Twa acts on the fourth portion due to the weight of counterweight 2.

[0316] The tension Tca is measured by a first tension measuring device 12. The tension Twa is measured by a second tension measuring device 13.

[0317] The tensions Tcm and Twm can be calculated as tension analysis values ​​using a tension model. The tensions Tcm and Twm may also be measured by a percussion method or by a removable sensor during maintenance and inspection.

[0318] The control system of the elevator system of the ninth embodiment is the same as that of the eighth embodiment. In addition, the method of calculating a plurality of predicted wear amounts is the same as that of the eighth embodiment.

[0319] Even for such a 2:1 roping type elevator device 10, the future amount of wear of the plurality of sheave grooves 8 can be predicted more accurately.

[0320] The elevator monitoring program of the ninth embodiment is a program that causes a computer to execute the processing of the monitoring method by the elevator monitoring device 20 of the ninth embodiment. Moreover, the recording medium of the ninth embodiment is a computer-readable recording medium on which the elevator monitoring program of the ninth embodiment is recorded.

[0321] Embodiment 10 Next, a tenth embodiment will be described. The elevator system according to the tenth embodiment is the same as that shown in FIG. 1. The control system of the elevator system according to the tenth embodiment is the same as that of any of the first to eighth embodiments.

[0322] Fig. 28 is an explanatory diagram that schematically shows the relationship between the car 1, the drive sheave 7, and multiple ropes 5. Fig. 29 is an explanatory diagram that shows a state in which the car 1 in Fig. 28 approaches the drive sheave 7. In Figs. 28 and 29, three ropes 5 are shown as an example.

[0323] The wear prediction unit 22 of the tenth embodiment stores the rope angle relational expression shown below. That is, the memory unit 24 stores the rope angle relational expression. The rope angle relational expression indicates the relationship between the angle θ(t) of the rope 5 with respect to the vertical direction, the vertical distance L(t) from the drive sheave 7 to the car 1 side end of the rope 5, and the horizontal deviation d of the car 1 side end of the rope 5 with respect to the sheave groove 8. The angle θ(t) is also called the fleet angle.

[0324] θ(t)=tan -1 (d / L(t))

[0325] Since the horizontal displacement of car 1 is restricted by a pair of car guide rails (not shown), the deviation d is a constant value independent of the car position. In other words, the deviation d in Figure 28 is the same value as the deviation d in Figure 29.

[0326] On the other hand, the distance L(t) and angle θ(t) vary depending on the car position. When car 1 moves from a lower floor to a higher floor, the value of the distance L(t) decreases and the value of the angle θ(t) increases. Conversely, when car 1 moves from a higher floor to a lower floor, the value of the distance L(t) increases and the value of the angle θ(t) decreases.

[0327] Because the angle θ(t) varies depending on the cage position, the direction of the surface pressure acting on the sheave grooves 8 also varies depending on the cage position. When the direction of the surface pressure varies, the direction of wear in the sheave grooves 8 also varies. The angle θ(t) corresponds to the direction in which wear progresses.

[0328] Figure 30 is a cross-sectional view showing an example of the wear state of each sheave groove 8 in the drive sheave 7 of Figure 28. Each sheave groove 8 has worn from the initial state shown by the two-dot chain line to the state shown by the solid line. The wear progresses in each sheave groove 8 in the direction shown by the arrow.

[0329] The wear prediction unit 22 of the tenth embodiment estimates the direction in which wear will progress by using the rope angle relational equation for the instantaneous wear amount value calculated by the wear prediction equation. When calculating the cumulative value of the instantaneous wear amount value, the wear prediction unit 22 also includes the angle θ(t) at which wear progresses. The wear prediction unit 22 then outputs a two-dimensional cross-sectional shape, such as that shown in FIG. 30, to the maintenance device 30 along with multiple predicted wear amounts.

[0330] In this case, the maintenance device 30 displays on the maintenance display a two-dimensional cross-sectional shape as shown in Fig. 30. Furthermore, the elevator monitoring device 20 displays on the monitoring display a two-dimensional cross-sectional shape as shown in Fig. 30.

[0331] The configuration and monitoring method in the tenth embodiment are the same as those in any of the first to ninth embodiments.

[0332] With this configuration as well, the future wear amounts of the plurality of sheave grooves 8 can be predicted more accurately.

[0333] Furthermore, the wear prediction unit 22 uses the rope angle relational expression to estimate the direction in which future wear will progress in the multiple sheave grooves 8. This makes it possible to more accurately predict the future wear state for each sheave groove 8.

[0334] The elevator monitoring program of the tenth embodiment is a program that causes a computer to execute the processing of the monitoring method by the elevator monitoring device 20 of the tenth embodiment. Moreover, the recording medium of the tenth embodiment is a computer-readable recording medium on which the elevator monitoring program of the tenth embodiment is recorded.

[0335] In addition, in the sixth to tenth embodiments, either the first tension measuring device 12 or the second tension measuring device 13 may be omitted. For example, when the second tension measuring device 13 is omitted, the tension of the counterweight side portion can be calculated from the design value of the weight of the counterweight 2.

[0336] In addition, in the sixth to tenth embodiments, the measurement data from the first tension measuring device 12 and the second tension measuring device 13 may be transmitted to the elevator monitoring device 20 via the elevator control device 11 without going through the maintenance device 30.

[0337] In addition, in the sixth to tenth embodiments, the measurement data from the first tension measuring device 12 and the second tension measuring device 13 may be transmitted directly to the elevator monitoring device 20 without going through the maintenance device 30.

[0338] In addition, in the seventh to tenth embodiments, the signal from the rotation sensor 14 may be transmitted directly to the elevator monitoring device 20 without going through the elevator control device 11.

[0339] Furthermore, the term "rope" in this disclosure is used in a broad sense and includes, for example, a belt for suspending a car.

[0340] Furthermore, the sheave in this disclosure is not limited to the drive sheave 7.

[0341] Furthermore, the elevator system in this disclosure may be an elevator with a machine room, a machine room-less elevator, a double-deck elevator, a one-shaft multi-car elevator, etc. The one-shaft multi-car system is a system in which an upper car and a lower car located directly below the upper car independently ascend and descend in a common elevator shaft.

[0342] In the first to tenth embodiments, the elevator monitoring device 20 may be an independent device or may be incorporated into another device as part of the function of the other device. Examples of the other device include the maintenance device 30 and the elevator control device 11.

[0343] The elevator monitoring device 20 may also be implemented in a cloud, a server, or the like on a communication network.

[0344] Moreover, each function of the elevator monitoring device 20 according to the first to tenth embodiments is realized by a processing circuit. Fig. 31 is a configuration diagram showing a first example of a processing circuit that realizes each function of the elevator monitoring device 20 according to the first to tenth embodiments. The processing circuit 100 of the first example is dedicated hardware.

[0345] 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 elevator monitoring device 20 may be realized by a separate processing circuit 100, or all functions may be realized by the processing circuit 100.

[0346] 32 is a configuration diagram showing a second example of a processing circuit that realizes each function of the elevator monitoring device 20 according to any one of the first to tenth embodiments. The processing circuit 200 of the second example includes a processor 201 and a memory 202.

[0347] The processor 201 may be, for example, a central processing unit (CPU), a graphics processing unit (GPU), a microprocessor, a microcontroller, or a digital signal processor (DSP).

[0348] In the processing circuit 200, each function of the elevator monitoring device 20 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.

[0349] It can also be said that the programs stored in memory 202 cause the computer to execute the procedures or methods of the above-mentioned sections. 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.

[0350] 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.

[0351] 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.

[0352] The above describes in detail preferred embodiments, but the present invention is not limited to the above-described embodiments, and various modifications and substitutions can be made to the above-described embodiments without departing from the scope of the claims.

[0353] Various aspects of the present disclosure are summarized below as appendices.

[0354] (Appendix 1) A wear prediction unit that calculates a wear amount prediction value that is a prediction value of future wear amounts that will occur in the multiple sheave grooves over a set period using a wear prediction formula that takes as input the tensions of the car-side portions and the counterweight-side portions of the multiple ropes that suspend the car and counterweight, the amount of slippage of the multiple ropes, and the material hardness of the sheave. An elevator monitoring device comprising: (Appendix 2) The wear prediction unit an average value of the tension in the car side portion and an average value of the tension in the counterweight side portion of each of the plurality of ropes are obtained; calculating a surface pressure acting on each of the plurality of sheave grooves; 2. An elevator monitoring device according to claim 1, wherein the predicted wear amount value for each of the plurality of sheave grooves is calculated. (Appendix 3) The elevator monitoring device according to claim 1, wherein the wear prediction unit obtains an average value of the average tension of all of the car-side portions of the plurality of ropes and an average value of the average tension of all of the counterweight-side portions of the plurality of ropes. (Appendix 4) 4. The elevator monitoring device according to claim 2 or 3, wherein each of the average values ​​includes tension fluctuations due to movement of the car. (Appendix 5) The wear prediction unit In the wear prediction formula, the tensions of the plurality of ropes are used to calculate the surface pressure acting on the plurality of sheave grooves; 5. An elevator monitoring device according to any one of claims 1 to 4, wherein the amount of creep as the amount of slippage is calculated from the difference between the amount of rotation of the sheave and the distance traveled by the car. (Appendix 6) The wear prediction unit stores a slippage calculation formula, 5. The elevator monitoring device according to claim 1, wherein the wear prediction unit uses, as the slippage, a slippage estimated value calculated using the slippage calculation formula. (Appendix 7) The wear prediction unit stores a first slippage calculation formula and a second slippage calculation formula as the slippage calculation formula, 7. The elevator monitoring device according to claim 6, wherein the wear prediction unit determines whether to select the first slippage calculation formula or the second slippage calculation formula depending on whether a ratio of the tension in the car-side portion to the tension in the counterweight-side portion exceeds a limit traction ratio. (Appendix 8) 8. The elevator monitoring device according to claim 1, wherein the wear prediction unit inputs momentary tension data as the tension of the car-side portion and the tension of the counterweight-side portion into the wear prediction formula to calculate instantaneous values ​​of wear of the plurality of sheave grooves, and accumulates the instantaneous values ​​of wear to calculate the predicted wear amount. (Appendix 9) 9. The elevator monitoring device according to any one of appendices 1 to 8, wherein the wear prediction unit updates parameters of the wear prediction formula based on past state quantities including past tension data, past rotation amounts of the sheave, and past wear amounts. (Appendix 10) the wear prediction unit uses tension analysis values ​​calculated using a tension model as the tension of the car side portion and the tension of the counterweight side portion, 10. The elevator monitoring device according to any one of claims 1 to 9, wherein the tension model is a model consisting of a plurality of equations of motion, in which the car side portion and the counterweight side portion are each modeled as springs. (Appendix 11) The wear prediction unit stores a rope angle relational expression for determining the angle of each of the ropes that varies depending on the car position, The elevator monitoring device according to any one of claims 1 to 10, wherein the wear prediction unit uses the rope angle relational expression to estimate a future direction of wear progression in the plurality of sheave grooves. (Appendix 12) a wear prediction step of calculating a wear amount prediction value that is a prediction value of future wear amounts that will occur in the multiple sheave grooves over a set period using a wear prediction formula that inputs the tensions of the car-side portions and the counterweight-side portions of the multiple ropes that suspend the car and the counterweight, the slippage of the multiple ropes, and the material hardness of the sheave; An elevator monitoring method comprising: (Appendix 13) An elevator monitoring program that causes a computer to execute the elevator monitoring method described in Appendix 12. (Appendix 14) A recording medium having recorded thereon an elevator monitoring program that causes a computer to execute the elevator monitoring method described in Appendix 12. [Explanation of symbols]

[0355] 1. Cage, 2. Counterweight, 5. Rope, 7. Drive sheave, 8. Sheave groove, 20. Elevator monitoring device, 22. Wear prediction unit.

Claims

1. A wear prediction unit that calculates a wear amount prediction value that is a prediction value of future wear amounts that will occur in the multiple sheave grooves over a set period using a wear prediction formula that takes as input the tensions of the car-side portions and the counterweight-side portions of the multiple ropes that suspend the car and counterweight, the amount of slippage of the multiple ropes, and the material hardness of the sheave. An elevator monitoring device comprising:

2. The wear prediction unit an average value of the tension in the car side portion and an average value of the tension in the counterweight side portion of each of the plurality of ropes are obtained; calculating a surface pressure acting on each of the plurality of sheave grooves; The elevator monitoring device according to claim 1, wherein the predicted wear amount value is calculated for each of the plurality of sheave grooves.

3. 2. The elevator monitoring device according to claim 1, wherein the wear prediction unit obtains an average value of the average tensions of all of the plurality of ropes on the car side and an average value of the average tensions of all of the plurality of ropes on the counterweight side.

4. 4. The elevator monitoring device according to claim 2, wherein each of the average values ​​includes tension fluctuations due to movement of the car.

5. The wear prediction unit In the wear prediction formula, the tensions of the plurality of ropes are used to calculate the surface pressure acting on the plurality of sheave grooves; 4. The elevator monitoring device according to claim 1, wherein a creep amount as the slippage amount is calculated from a difference between an amount of rotation of the sheave and a travel distance of the car.

6. The wear prediction unit stores a slippage calculation formula, 4. The elevator monitoring device according to claim 1, wherein the wear prediction unit uses, as the slippage amount, a slippage amount estimated value calculated using the slippage amount calculation formula.

7. The wear prediction unit stores a first slippage calculation formula and a second slippage calculation formula as the slippage calculation formula, 7. The elevator monitoring device according to claim 6, wherein the wear prediction unit determines whether to select the first slippage calculation formula or the second slippage calculation formula depending on whether a ratio of the tension in the car-side portion to the tension in the counterweight-side portion exceeds a limit traction ratio.

8. 4. The elevator monitoring device according to claim 1, wherein the wear prediction unit inputs momentary tension data as the tension of the car-side portion and the tension of the counterweight-side portion into the wear prediction formula to calculate instantaneous values ​​of wear amounts of the plurality of sheave grooves, and calculates the predicted wear amount value by accumulating the instantaneous wear amount values.

9. 4. The elevator monitoring device according to claim 1, wherein the wear prediction unit updates parameters of the wear prediction formula based on past state quantities including past tension data, past rotation amounts of the sheave, and past amounts of wear.

10. the wear prediction unit uses tension analysis values ​​calculated using a tension model as the tension of the car side portion and the tension of the counterweight side portion, 4. The elevator monitoring device according to claim 1, wherein the tension model is a model consisting of a plurality of equations of motion in which the car-side portion and the counterweight-side portion are each modeled as a spring.

11. The wear prediction unit stores a rope angle relational expression for determining the angle of each of the ropes that varies depending on the car position, 4. The elevator monitoring device according to claim 1, wherein the wear prediction unit estimates a direction in which future wear will progress in the plurality of sheave grooves using the rope angle relational expression.

12. a wear prediction step of calculating a wear amount prediction value that is a prediction value of future wear amounts that will occur in the multiple sheave grooves over a set period using a wear prediction formula that inputs the tensions of the car-side portions and the counterweight-side portions of the multiple ropes that suspend the car and the counterweight, the slippage of the multiple ropes, and the material hardness of the sheave; An elevator monitoring method comprising:

13. An elevator monitoring program that causes a computer to execute the elevator monitoring method according to claim 12.

14. A recording medium storing an elevator monitoring program for causing a computer to execute the elevator monitoring method according to claim 12.

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