CN111060272B - Free vibration damping test method for elevator car - Google Patents

Free vibration damping test method for elevator car Download PDF

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CN111060272B
CN111060272B CN201911389219.4A CN201911389219A CN111060272B CN 111060272 B CN111060272 B CN 111060272B CN 201911389219 A CN201911389219 A CN 201911389219A CN 111060272 B CN111060272 B CN 111060272B
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steel wire
wire rope
car
elevator
damping
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CN111060272A (en
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薛江红
许�鹏
彭启凤
李善倾
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Jinan University
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    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M7/00—Vibration-testing of structures; Shock-testing of structures
    • G01M7/02—Vibration-testing by means of a shake table

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

The invention discloses a free vibration damping test method for an elevator car, which comprises the following steps: measuring the mass m of the elevator car by adopting a weighing device, obtaining the elastic modulus E of a single steel wire rope, measuring the diameter d of the steel wire rope by adopting a vernier caliper, and calculating the sectional area S of the single steel wire rope; calculating a traction ratio i and the number n of suspended steel wire ropes; measuring the length l of the steel wire rope from the car top to the tangent point of the traction wheel by using a laser range finder and a measuring tape; a vibration tester is arranged on the top of the elevator car, when the elevator runs downwards in a no-load state to a constant speed state, the power is cut off to make the elevator brake emergently, parameters of free vibration of the car after emergency braking are read, and the logarithmic decrement delta is calculated; and calculating the free vibration damping of the elevator car. The invention determines the damping of the elevator steel wire rope-car system during free vibration by measurement, solves the limitation that the damping value is estimated only by experience during traditional calculation, and provides the measurement accuracy.

Description

Free vibration damping test method for elevator car
Technical Field
The invention relates to the technical field of elevator vibration testing, in particular to a free vibration damping testing method for an elevator car.
Background
When the engineering structure vibrates freely, the amplitude of the vibration is gradually attenuated along with the time due to the damping effect, and finally the vibration is close to zero to stop vibrating.
The elevator acts as a suspension system, the movement of which in the shaft is subject to a damping force, which is a non-negligible factor, for the accurate analysis of the movement of the elevator. However, because damping influence factors are numerous and testing is difficult, damping is rarely considered in traditional elevator vibration research, and analysis result errors are large.
Disclosure of Invention
In order to overcome the defects and shortcomings in the prior art, the invention provides the free vibration damping test method for the elevator car, which can conveniently and quickly test the vibration damping of the elevator steel wire rope-car system in use, so that the vibration characteristic of the elevator car is mastered, the riding comfort of the elevator car is improved, and relevant parameters are provided for improving the energy efficiency of the elevator.
In order to achieve the purpose, the invention adopts the following technical scheme:
the invention provides a free vibration damping measurement method of an elevator car, which comprises the following steps:
adopt weighing device to record elevator car quality m, obtain single wire rope' S elastic modulus E, adopt slide caliper to measure wire rope diameter d, calculate single wire rope sectional area S:
Figure BDA0002344493740000011
calculating a traction ratio i and the number n of suspended steel wire ropes;
measuring the length l of the steel wire rope from the car top to the tangent point of the traction wheel by using a laser range finder and a measuring tape;
a vibration tester is arranged on the top of the elevator car, when the elevator runs downwards in a no-load state to a constant speed state, the power is cut off to make the elevator brake emergently, parameters of free vibration of the car after emergency braking are read, and the logarithmic decrement delta is calculated;
calculating the free vibration damping of the elevator car:
Figure BDA0002344493740000021
wherein c represents the damping value of the free vibration of the elevator car.
As a preferred technical scheme, the calculation formula of the free vibration damping of the elevator car specifically comprises the following steps:
constructing a steel wire rope-car system into a damping spring vibration system;
the differential equation of the free vibration of the system is constructed as follows:
Figure BDA0002344493740000022
in the formula: m is the mass of the elevator car, c is the measured damping coefficient, k is the elastic constant of the elevator steel wire rope, t is time, and x (t) is the displacement of the elevator car along with the change of time;
the elastic constant of the elevator steel wire rope is as follows:
Figure BDA0002344493740000023
in the formula, i represents a traction ratio, n is the number of steel wire ropes, E is the elastic modulus of the steel wire ropes, S is the area of a single steel wire rope, and l is the length of the steel wire rope from the car roof to a tangent point of a traction wheel;
dividing both sides of formula (1) by mass m to obtain:
Figure BDA0002344493740000024
in the formula, ωnIs the natural frequency of an undamped system, i.e.
Figure BDA0002344493740000025
Zeta is damping ratio, and the calculation formula is as follows:
Figure BDA0002344493740000031
the steel wire rope-car system is a damped vibration system, zeta is more than 0 and less than 1, and the solution of equation (1) can be obtained as follows:
Figure BDA0002344493740000032
wherein, ω isdIn order to have the natural frequency of the damping system:
Figure BDA0002344493740000033
wherein, X represents the amplitude of the vibration,
Figure BDA0002344493740000034
the phase of the initial phase is represented,
the damped natural period of a damped vibration system is:
Figure BDA0002344493740000035
according to exponential decay, a logarithmic decay rate delta is adopted to express the natural logarithm of the ratio of two adjacent amplitudes of a natural period, namely:
Figure BDA0002344493740000036
the combined vertical type (2), (5) and (9) are finished to obtain
Figure BDA0002344493740000037
Wherein c represents the damping value of the free vibration of the elevator car.
Compared with the prior art, the invention has the following advantages and beneficial effects:
(1) the invention determines the damping of the free vibration of the elevator steel wire rope-car system by measurement, solves the limitation that the damping value is estimated only by experience in the traditional calculation, can measure corresponding parameters only by carrying out emergency braking operation, is safe and economical to implement, and can be widely applied to the damping measurement of a traction type structure.
Drawings
Fig. 1 is a schematic view of measurement parameters of the elevator car free vibration damping measurement method in the embodiment.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
As shown in fig. 1, the present embodiment provides a method for measuring damping of free vibration of an elevator car, which obtains damping of free vibration of an elevator car by taking relevant parameter measurement into a calculation module, and includes the following measurement steps:
the basic parameters to be measured include: measured by means of weighing devicesThe quality of the elevator car, the performance parameter table are looked up to obtain the elastic modulus of a single steel wire rope, the diameter of the steel wire rope is measured by a vernier caliper, and therefore the sectional area of the single steel wire rope is calculated
Figure BDA0002344493740000041
The traction ratio i, the number n of the suspended steel wire ropes and the free vibration amplitude value are obtained through visual inspection on the car top, related parameters are input into an input module, free vibration damping of the car is obtained through a calculation module according to the following calculation formula, and the free vibration damping is displayed through an output module.
When the elevator car vibrates freely, the brake stably clasps the brake, the traction sheave does not rotate any more, the elevator car is suspended on the traction sheave through the steel wire rope, and at the moment, the steel wire rope-car can be regarded as a vibration system with a damping spring.
The system free vibration differential equation is:
Figure BDA0002344493740000042
in the formula: m is the mass of the elevator car, c is the measured damping coefficient, k is the elastic constant of the elevator steel wire rope, t is time, and x (t) is the displacement of the elevator car along with the change of time;
wherein the elastic constant of the elevator steel wire rope is as follows:
Figure BDA0002344493740000051
in the formula, i represents a traction ratio, n is the number of steel wire ropes, E is the elastic modulus of the steel wire ropes, S is the area of a single steel wire rope, and l is the length of the steel wire rope from the car roof to a tangent point of a traction wheel;
dividing both sides of formula (1) by mass m to obtain:
Figure BDA0002344493740000052
in the formula, ωnIs the natural frequency of an undamped system, i.e.
Figure BDA0002344493740000053
Zeta is damping ratio, and the calculation formula is as follows:
Figure BDA0002344493740000054
the steel wire rope-car system discussed in this embodiment is a damped vibration system, and belongs to the small damping situation in engineering, i.e. 0 < ζ < 1, so the solution of equation (1) can be obtained as follows:
Figure BDA0002344493740000055
wherein ω isdIn order to have the natural frequency of the damping system:
Figure BDA0002344493740000056
x (amplitude) and
Figure BDA0002344493740000057
the (initial phase) is determined by the initial conditions of the elevator car;
according to the physical meaning of the inherent period, the inherent period of the damping system with damping is as follows:
Figure BDA0002344493740000058
the steel wire rope-car system of the embodiment is a damped vibration system, the amplitude of the system is exponentially attenuated in the free vibration process, and the natural logarithm of the ratio of two adjacent amplitudes in a natural period is represented by a logarithmic attenuation rate delta, namely:
Figure BDA0002344493740000061
the combined vertical type (2), (5) and (9) are finished to obtain
Figure BDA0002344493740000062
Wherein: m, i, n, E and S are constants, l is determined by the position of the elevator, and delta can be measured through a free vibration experiment, so that the free vibration damping value of the elevator car at any point can be measured.
The specific measurement steps are as follows:
(1) measuring the mass m of the car by using a weighing device;
(2) visually measuring the traction ratio i and the number n of the steel wire ropes on the car roof;
(3) looking up a performance parameter table to obtain the elastic modulus E of the single steel wire rope;
(4) measuring the diameter d of the steel wire rope by using a vernier caliper so as to calculate the sectional area of a single steel wire rope
Figure BDA0002344493740000063
(5) Measuring the length l of the steel wire rope from the car top to the tangent point of the traction wheel by using a laser range finder and a measuring tape;
(6) firstly, mounting a vibration tester on the top of an elevator car; secondly, the elevator runs downwards to a constant speed state in no-load mode; thirdly, the elevator is emergently braked by power failure; fourthly, reading parameters of free vibration of the car after braking; calculating the natural logarithm delta of the ratio of the two amplitudes;
(7) the measured parameters are substituted into the formula (10) to obtain the free vibration damping of the system.
The embodiment can determine the damping of the free vibration of the elevator steel wire rope-car system through measurement, solves the limitation that the damping value is estimated only through experience in the traditional calculation, can measure corresponding parameters only through emergency braking operation, is safe and economical to implement, and can be widely applied to the damping measurement of a traction type structure.
The above embodiments are preferred embodiments of the present invention, but the present invention is not limited to the above embodiments, and any other changes, modifications, substitutions, combinations, and simplifications which do not depart from the spirit and principle of the present invention should be construed as equivalents thereof, and all such changes, modifications, substitutions, combinations, and simplifications are intended to be included in the scope of the present invention.

Claims (2)

1. A free vibration damping measurement method of an elevator car is characterized by comprising the following steps:
adopt weighing device to record elevator car quality m, obtain single wire rope' S elastic modulus E, adopt slide caliper to measure wire rope diameter d, calculate single wire rope sectional area S:
Figure FDA0002344493730000011
calculating a traction ratio i and the number n of suspended steel wire ropes;
measuring the length l of the steel wire rope from the car top to the tangent point of the traction wheel by using a laser range finder and a measuring tape;
a vibration tester is arranged on the top of the elevator car, when the elevator runs downwards in a no-load state to a constant speed state, the power is cut off to make the elevator brake emergently, parameters of free vibration of the car after emergency braking are read, and the logarithmic decrement delta is calculated;
calculating the free vibration damping of the elevator car:
Figure FDA0002344493730000012
wherein c represents the damping value of the free vibration of the elevator car.
2. The method for measuring the free vibration damping of the elevator car according to claim 1, wherein the calculation formula of the free vibration damping of the elevator car is specifically constructed by the following steps:
constructing a steel wire rope-car system into a damping spring vibration system;
the differential equation of the free vibration of the system is constructed as follows:
Figure FDA0002344493730000013
in the formula: m is the mass of the elevator car, c is the measured damping coefficient, k is the elastic constant of the elevator steel wire rope, t is time, and x (t) is the displacement of the elevator car along with the change of time;
the elastic constant of the elevator steel wire rope is as follows:
Figure FDA0002344493730000014
in the formula, i represents a traction ratio, n is the number of steel wire ropes, E is the elastic modulus of the steel wire ropes, S is the area of a single steel wire rope, and l is the length of the steel wire rope from the car roof to a tangent point of a traction wheel;
dividing both sides of formula (1) by mass m to obtain:
Figure FDA0002344493730000021
in the formula, ωnIs the natural frequency of an undamped system, i.e.
Figure FDA0002344493730000022
Zeta is damping ratio, and the calculation formula is as follows:
Figure FDA0002344493730000023
the steel wire rope-car system is a damped vibration system, zeta is more than 0 and less than 1, and the solution of equation (1) can be obtained as follows:
Figure FDA0002344493730000024
wherein, ω isdIn order to have the natural frequency of the damping system:
Figure FDA0002344493730000025
wherein, X represents the amplitude of the vibration,
Figure FDA0002344493730000026
the phase of the initial phase is represented,
the damped natural period of a damped vibration system is:
Figure FDA0002344493730000027
according to exponential decay, a logarithmic decay rate delta is adopted to express the natural logarithm of the ratio of two adjacent amplitudes of a natural period, namely:
Figure FDA0002344493730000028
the combined vertical type (2), (5) and (9) are finished to obtain
Figure FDA0002344493730000029
Wherein c represents the damping value of the free vibration of the elevator car.
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CN207016312U (en) * 2017-05-24 2018-02-16 住友富士电梯有限公司 A kind of elevator for reducing maintenance cost
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CN105984782A (en) * 2015-03-16 2016-10-05 三菱电机株式会社 Elevator system, method controlling operation of elevator system, and non-instantaneous computer readable medium
JP2016199378A (en) * 2015-04-13 2016-12-01 株式会社日立ビルシステム Gap measuring device for emergency stop device of elevator
CN207016312U (en) * 2017-05-24 2018-02-16 住友富士电梯有限公司 A kind of elevator for reducing maintenance cost
CN107356419A (en) * 2017-07-18 2017-11-17 厦门大学 A kind of experimental method for being used to measure rope damping parameter
CN108773750A (en) * 2018-06-06 2018-11-09 辽宁优力安机电设备有限公司 The detection method of magneto-rheologic liquid brake elevator operation damping

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