Dynamic Response of a Casting Crane Rigid-Flexible Coupling System to High Temperature

To determine the influence of temperature on the mechanical properties of crane metal structures, three Q355 alloy steel samples were processed and their elastic moduli were tested at different temperatures using a metal tension test bed. -e constitutive equation for the elastic modulus of Q355 alloy steel at different temperatures was predicted using test data and a neural network algorithm. Based on crane structural characteristics and the principle of system dynamics, a coupling vibration model was established that included the crane flexible girder, cabin, trolley, crane, and temperature. System motion equations were established according to the Lagrange equation, and the approximate solution of nonlinear system vibration was solved by the direct integration method (the Newmark method). -e dynamic characteristics of the main beam and cabin were analyzed at different temperatures, as well as safety during service. -e results show that, with increasing temperature, the maximum midspan displacement of the main beam increases gradually, by 14.3%, 21.4%, and 57.1% at temperatures of 300°C, 400°C, and 600°C, respectively. -e cabin vibration displacement increases with temperature, by up to 32.5% at 600°C, but the influence of temperature on cabin vibration acceleration is not obvious. It was concluded that the influence of temperature on the dynamic characteristics of the main beam must be considered during the design stage of cranes. -e proposed model and analysis method provide a theoretical basis for the design of casting cranes according to temperature.


Introduction
Casting cranes are one of the most important devices in steelmaking and the continuous casting process and key heavy machinery equipment for mechanized and automated production [1]. ey are predominantly used for loading and unloading molten steel in modern steel plants; thus, they operate in harsh environments characterized by high temperature and dust content. Because the temperature of the ladle is very high, approximately 1600°C, casting crane accidents can cause substantial losses to human life and wealth [2]; therefore, crane design standards are very high to ensure operational safety and reliability. e main beam of the crane close to the molten steel is subjected to intense thermal radiation, which results in a much higher temperature of the crossbeam than normal. Because the main body of the casting crane is a steel structure, the physical properties and mechanical properties of the material are sensitive to temperature, and its performance differs substantially between high and normal temperatures [3]. Moreover, the dynamic characteristics of the bridge structure are affected by many factors. erefore, understanding the thermoelastic coupling dynamics of the main beam of a casting crane has important engineering applications.
In high-temperature environments, the mechanical properties of metal materials will change significantly, which can directly affect the structure's service life and safety performance of casting crane equipment. erefore, many studies have investigated the mechanical properties of metal materials. Kirby and Preston [4] tested metal specimens under different loads at high temperature and recorded a series of strain-temperature curves and stress-strain curves for steel at different temperatures, ultimately deriving the relationship between the elastic modulus and temperature of steel. Cold-formed steels were studied by Chen and Young [5]. Kodur et al. [6] reviewed high-temperature constitutive relationships for standard steel currently available in America and Europe and highlighted the variation between these relationships through a comparison with published experimental results.
As for the mechanical properties of building steel structures in high-temperature environments, Lu and Zhu [7] analyzed the structural response of a reinforced concrete frame by the nonlinear finite element method according to simulation results, constitutive relationship experiments, unstable heat conduction theory, and the nonlinear direct stiffness method. rough experiments, Lv [8] analyzed the strength and deformation of building steel bars at different temperatures, including the strength, stress-strain curve, elastic modulus, deformation under stress, and short-term creep of all grades of steel bars in the range of 20-800°C. e strength of five grades of steel bars decreased continuously with increasing temperature. Short-term creep of a steel bar is larger than creep at normal temperature and tends to be unstable at higher temperature and stress. Tan [9] established and validated a theoretical model of yield strength, ultimate strength, elasticity modulus, and ultimate strain for the commonly used Q235 steel with temperature. Qiang et al. [10] conducted tensile tests and obtained the postfire elastic modulus, yield, ultimate strength, ductility, and stress-strain curves before proposing two separate sets of predictive equations for evaluating the mechanical properties of S460 and S690 steels after a fire. Wang et al. [11] proposed a new set of equations to predict the postfire mechanical properties of high-strength Q460 steel. Such postfire mechanical property assessments allow structural and fire engineers to make accurate predictions of the safety of high-strength Q460 steel buildings exposed to fire. Based on material properties generated from the research on the thermal and mechanical properties of steel at elevated temperatures, a number of code's specifications for fireresistant design have been developed, such as EN1993-1-2 [12], AS4100 [13], ANSI/AISC360-05 [14], BS 5950-1:2000 [15], and GB 51249-2017 [16]. In line with the steady-state test results for high-tensile steels, the elastic modulus is similar in the codes.
In addition to the effect of temperature, the influence of wire rope vibration during ladle hoisting should be considered. Additionally, the dynamic characteristics of the main beam of the casting crane are influenced by many factors; for example, the installation position and connection parameters of the cabin will affect the main beam dynamic characteristics and the vibration comfort of the human body. In addition, operation of the trolley has an impact on the deflection of the main beam, which will increase under increased temperature and affect the safety of the crane. erefore, it is necessary to analyze the influence of temperature on the crane during trolley operation.
Many engineering structures transport moving parts, such as vehicle-bridge systems, projectile-gun systems, weight-bridge crane systems, and slider rail systems, and can be simplified as a moving mass-beam model. In the crane dynamic system, the load state formed by wire rope, hanger, and crane is a major cause of crane vibration, which has been the topic of substantial in-depth research. Huang et al. [17] and Masoud and Nayfeh [18] studied the swing of lifting weights during lifting, simplified the system into a double swing vibration model, and eliminated vibration of the lifting weight by means of feedback control measures. Many studies have also analyzed the dynamic response of the main beam and swing angle of the crane during trolley operation.
A large body of research on the problems of various structures with linear behavior traversed by a moving mass and moving load has been conducted by Frýba [19], specifically for single and multispan beam structures. Regarding the problem of moving loads acting on a Bernoulli-Euler beam, Foda and Young [20] used a dynamic Green function approach to determine the response of a finite length, simply supported Bernoulli-Euler beam subjected to a moving mass traversing its span and analyzed the influences of travelling velocity variations and the ratio of moving mass to beam mass on the dynamic response. ey demonstrated the efficiency and simplicity of their method using several numerical examples. Kiani et al. [21,22] reported a numerical parametric investigation into the design parameters of multispan viscoelastic shear deformable beams subjected to a moving mass via the generalized moving least squares method and another comprehensive parametric investigation on the evaluation of design parameters, where the maximum deflection and bending moment of beams were analyzed. Regarding the problem of moving loads acting on thin beams with geometric nonlinearity, they also employed an efficient meshless method and the reproducing kernel particle method for a spatial discretization nonlinear beam [23].
Although many scholars have studied the influence of moving mass on the dynamic characteristics of the crane main beam, these studies have mainly focused on the situation where the vehicle has a higher moving speed and the moving mass can leave the simply supported beam. e crane structure and trolley operation mode have their own characteristics, yet previous literature does not typically consider the influence of installation location and cabin mode on the dynamic characteristics of the main beam during trolley operation. At the same time, vibrations can lead to occupational injuries for the hoistman. In the existing dynamic analysis of cranes, hoistman vibration is seldom considered, yet the operational comfort of the hoistman directly affects the accuracy and safety of crane operation. In addition, due to the long-term high-temperature working environment of the casting crane, research into the influence of temperature on the mechanical properties of steel has rarely been applied to the dynamic analysis of crane structure. Dynamic studies of crane structure do not consider the influence of temperature on the crane. erefore, this study firstly considers the installation location and connection mode of the cabin, as well as other factors, constructs a dynamic model of the main beam system during trolley operation, and discusses the dynamic response and safety of the main beam. e vibration response of the cabin is also obtained. Secondly, the hightemperature modulus of elasticity for Q355 alloy steel is obtained using material mechanical property testing equipment, and the constitutive equation of modulus elasticity is obtained by data fitting. Test results are validated through a comparison with previous studies. Finally, based on the constitutive equation, the vibration characteristics of the crane beam and cabin at high temperature and the safety of crane are analyzed. is method provides an important theoretical basis for metal structure design, kinematic-dynamic analysis, life prediction, and safety evaluation of casting cranes.

Metal Elastic Modulus Analysis
Casting cranes operate in a high-temperature environment lifting molten metal for a long duration. e metal material characteristics of the crane are greatly affected by the temperature field, which will have a substantial impact on the structural performance and operational lifetime of the crane. erefore, mechanical properties of metal materials are experimentally tested and dynamic responses of the crane system are analyzed at high temperature.

Trial Objective.
Casting cranes are mainly used for lifting ladles containing molten metal. Because of the working location and specific characteristics, there are high requirements for the dynamic characteristics and safety of these cranes. In addition, due to the large size and complex structure of casting cranes, temperature affects the elastic modulus and dynamic structure of the main beam material.
is could directly lead to a reduction in the safety factor, which poses a significant threat to the economy and staff safety. erefore, a test bed is applied to obtain the influence of temperature on the elastic modulus of the steel material and the relationship with time.

Specimen Design.
e specimen material is Q355 lowalloy, high-strength steel. e main chemical composition of this material according to the product quality specifications is shown in Table 1. Because of its elemental content, it is characterized as a qualified product. e processing dimensions of the specimens are strictly in accordance with the requirements of ISO 6892-1 [24] and ISO 783-1 [25]. e thickness, standard distance length, and total length of parallel sections are 3 mm, 100 mm, and 120 mm, respectively. e radius of the transition zone between parallel sections and clamping sections is 18 mm. e clamping length of the pin-shaft connection at both ends of the specimen is 45 mm, and the diameter of the shaft hole is 8 mm. e shape and other dimensions of the specimens are shown in Figure 1. e processing accuracy of the specimens must meet the following requirements: (1) e absolute error of pin joint processing is less than 0.05 mm (2) e absolute error of standard distance processing is less than 0.5 mm (3) e absolute error of thickness processing is less than 0.05 mm 2.3. Test Procedure 2.3.1. Composition of the Test System. e equipment for testing the mechanical properties of the Q355 alloy steel at different temperatures includes three main systems: a structural loading system, a temperature control system, and a data acquisition system. e composition of the test system is shown in Figure 2, and a photograph of the test bench is shown in Figure 3. e main test equipment includes a computer-controlled electronic universal testing machine (UTM6000), electronic extensometer (YSJ50/25-ZC), hightemperature furnace, temperature control device (WGDN-7300L), the material test system, and a DC power supply.

Test Method.
Firstly, the test equipment is installed and debugged to ensure the safety and accuracy of the test process. Secondly, the specimens are installed on the test machine and maintained in a vertical position. In the temperature measurement system, the coordinates of the high-temperature furnace are adjusted to ensure that the entire specimen is within the high-temperature furnace. e temperature of the specimen is controlled and kept constant for 10 min before the test. Finally, the elastic modulus of the specimens is tested using the loading system, and the test data and images are displayed in the material test software of the electronic universal testing machine. Casting cranes are mainly used for lifting ladle containing molten metal that will have strong thermal radiation to the crane, which will affect the mechanical properties of the main beam structure. erefore, in the design of crane, a layer of insulation board made of asbestos mesh is usually applied at the bottom of the main beam, which effectively prevents the partial radiation of temperature field to main beam. erefore, the maximum temperature of the main beam will not exceed 600°C, and it is even less likely to reach 1000°C. In the test, considering the influence of temperature field on the mechanical properties for main beam structure, the highest test temperature is chosen to be 600°C.  Figure 4. It can be seen from the gure that the stress-strain curves of the tensile specimens vary considerably at di erent temperatures. With the increase in temperature, the yield strength and elastic modulus of Q355 alloy steel show a downward trend. In particular, when T > 400°C, the yield strength reduces sharply. At T 600°C, the yield strength is 165 MPa, which is 46.2% of the yield strength (357 MPa) at room temperature.
Deformation of the material prior to yielding is very small, but there is an approximate linear segment. According to the de nition of the elasticity modulus at room temperature, the high-temperature stress-strain curve can be obtained as the slope of the approximate straight line when the material is deformed. In general, the ratio of stress to strain is the elastic modulus in the range of 0.01-0.1%. e measured elastic moduli are listed in Table 2. Table 2 reveals that the variation of elasticity modulus with temperature is similar to that of strength. With increasing temperatures, the modulus of elasticity decreases gradually. e change of elasticity modulus is reduced in the range of 20-300°C as the temperature increases, and the elasticity modulus decreases at a faster rate at 300-600°C than 20-300°C. At the European Conference on Building Steel Structures, the following expressions were proposed for the relationship between the elastic modulus and temperature of steel structures, as shown in equation (1) [27]; Australian code AS4100 [13] and Trahair [28] suggested that equation (2) is used to calculate the elastic modulus of metal steel structures under di erent temperature environments: (2)

Advances in Civil Engineering
In [7][8][9]26], the elastic modulus and mechanical properties of steel structures at different temperatures were measured experimentally. e equations for elastic modulus calculation at different temperatures, obtained by fitting these discrete data, are shown below (equations (3)- (6)): As mentioned in the Technical Specification for Fire Protection of Building Steel Structures (GB 51249-2017), the elastic modulus of ordinary steel at high temperature can be calculated according to the following equation [16]: In Eurocode 3 [12], steel elastic modulus at different temperatures is given. Based on four polynomial fitting methods, the elastic modulus of ordinary steel at high temperature can be calculated according to the following equation: e elastic modulus of Q355 steel cannot be tested at each corresponding temperature due to the limitations of the experimental conditions. erefore, based on the elastic modulus obtained from the tensile test at the corresponding temperature, the constitutive equations for the elastic modulus of Q355 By comparing the predicted values of the constitutive equation with the experimental data, it is found that the maximum error is 0.21%, and the predicted results are satisfactory. By comparing the experimental data from the literature with the tting equation of this study, the relationship between the elastic modulus of metals and temperature is obtained ( Figure 5). e tting curve of the constitutive equation for the elastic modulus of Q355 steel very closely coincides with the experimental value, which reveals the complex nonlinear relationship between temperature and elastic modulus in Q355 steel. At the same time, the experimental and predicted results in this study are consistent with those in other literature. Within a certain temperature range, the trend of the curve is that the elastic modulus of steel decreases with the temperature increase.

Crane Dynamic Model considering Cabin Factors
Typically, the installation position of the cabin is located on the side of the main beam of the crane, which is equivalent to hanging a centralized mass on the main beam. With the continuous advancement of intelligent processes, the installation position and installation mode of the cabin are constantly changing. e design of the cabin is related to the physical health, mental health, and operation accuracy of the hoistman. Existing crane models do not take into account the mass m p and swing angle θ x of the payload; thus, without considering factors such as cab weight, connection mode, and installation position, the existing mathematical model cannot replicate the actual working conditions of the crane. erefore, a physical model that more closely simulates the actual working conditions of the crane ( Figure 6) is proposed [29]. According to the crane system dynamics model during the operation of trolley shown in Figure 6, the forces on the system mainly include the gravity loads, inertial force, structural elastic force, and dissipative force of each component. e gravity of the system is composed of the gravity of trolley, payload, main beam, and cabin. e inertial force of the system is made up of the inertial force along the Z-axis of trolley, the cabin, main beam, and the inertial force of payload along the Z-axis and swinging inertial force around the Y-axis. e structural elastic force of the system includes the elastic force of the main beam along the Z-axis and the elastic force between cabin and main beam. e dissipative force of the system is consisted of dissipative forces of main beam structure and connection structure between cabin and main beam.

Description of the System Model.
A casting crane consists of a frame structure, trolley running mechanism, cab, and lifting weight. According to the size and structural characteristics of components and to simplify the calculation process, the dynamic vibration model of the casting crane system is based on the following assumptions: (1) As a exible body, the main beam only considers vertical vibration, assuming that all dampers in the elastic body are viscous dampers, and the dampers in the beam have little in uence on structural vibration [30]. Typically, the damping ratio is 0.1-0.7%。. (2) e cabin is simpli ed as a lumped mass, only considering vertical vibration, and the connection between cabin and main beam is simpli ed as a spring and damping system with greater sti ness. (3) e suspension rope is assumed to be a mass-free rigid suspension rope according to the actual operational characteristics of the bridge crane load operation. (4) e lifting weight is simpli ed as a swinging concentrated mass, which is suspended on the mass block by a rigid suspension rope without mass. It moves together with the mass block and swings in the plane.   Based on the properties of the Euler-Bernoulli beam, the model of trolley travel on the crane beam can be simplified to that of a moving mass on a simply supported beam. at is to say, the bending stiffness is calculated without considering the shear stiffness and torsional stiffness of the beam. e definitions of the parameter symbols used in Figure 6 are given in Table 3.

Motion Equations of Crane System.
e continuous mass of crane structure is distributed along the axial direction of structure and belongs to the system of infinite degrees of freedom. Its dynamic characteristics and responses are generally difficult to be solved. In engineering, the continuous system of distributed quality is often discretized and transformed into a multi-degree-of-freedom discrete system for analysis to obtain a realistic approximate solution. Modal superposition is a fast solution to solve the linear dynamic problem and conduct the transient analysis of the effective solution method. It is obtained by multiplying each mode shape by modal analysis and multiplying the coefficients to calculate the dynamic response.
Many literatures use the modal assumption method to give the vibration displacement of the main beam under the action of moving mass. e calculation accuracy of the modal superposition method in dynamic response analysis of the main beam can meet the engineering calculation accuracy requirements [31]. e vibration of the main beam can be considered as the sum of multiple modal vibrations. e system is simplified to the N + 2-degree-of-freedom system, rather than a continuous system. As a part of the system, the crane girder structure is simplified into a simply supported homogeneous continuous subsystem. is subsystem is used as the research object to study the response of the main beam structure system at different temperatures under the impact of trolley operation. When the modal order N of the crane main beam approaches positive infinity, the response result is infinitely approximated to the exact solution. When N is a certain value, the response result of the crane main beam is an approximate solution. Based on the regular mode function of the simply supported beam and principle of main beam vibration under moving mass in literatures [32,33], when the trolley runs at maximum speed, V m , on the main beam, the elastic displacement curve of the position x in the Z direction of the main beam at time t can be expressed as follows [34,35]: where ϕ i (x) � sin(iπx/l b ) is the ith modal of the simply supported beam and q i (t) and N are the generalized coordinates and coordinate numbers of the elastic displacement of the main beam, respectively. e coordinate vectors can be defined according to the simplified physical model shown in Figure 1. erefore, the position vector of an elemental mass of the beam, � r b , the position vector of the carriage, � r c , the position vector of the payload, � r p , and the position vector of the crane cabin, � r d , can be expressed as follows: Assuming that the total kinetic energy of the system is T, the energy of the two main beams is T b , the kinetic energy of the running trolley is T c , and the kinetic energy of the lifting weight is T p ; thus, the kinetic energy of each part of the system can be expressed as follows: In the coupled system model, the system potential energy includes the elastic strain energy of the main beam, the elastic potential energy of the spring between the main beam and cabin, and the work done by the gravity of the trolley, cabin, and lifting weight itself. erefore, the potential energy in the system, U, can be expressed as follows: e dissipated energy in the system, D, can be expressed as follows: e Lagrange equation of nonconservative systems can be expressed as follows: 1, 2, . . . , n), (15) where zD/z _ y i is the damping force caused by the energy dissipation function D, F i only represents the generalized excitation force of external action, y i is the generalized coordinate, and _ y i is the generalized velocity. According to equation (15) and the modal assumption principle, the main beam is simplified to the j-order modal superposition form. erefore, the number of vibration equations for the main beam is j, and the vibration differential equation can be unified into the following form: According to equation (16), the differential equation of vibration for the main beam can be deduced as follows: where M, C, and K are the mass matrix, damping matrix, and stiffness matrix, respectively; € q(t), _ q(t), and q(t) are the acceleration vector, velocity vector, and displacement vector of the system, respectively; and F(t) is a load vector. e mass matrix, damping matrix, stiffness matrix, and excitation force vector in the system vibration equation can be expressed as follows: According to equation (15), the differential equation of payload swing can be deduced as follows: and the differential equation of cabin vibration is given as follows:

Procedure and Reliability Analysis of the Solution.
Nonlinear factors exist widely in engineering and include the nonlinearity of materials such as nonlinear forces, motion nonlinearity, nonlinear constitutive relationships, and geometric nonlinearity such as large elastic deformation. From a mathematical point of view, equation (17) is a second-order ordinary differential equation, which can be solved by the Runge-Kutta method. However, when the order of the matrix in the motion equation is large, the efficiency of this method is very low. e mode superposition method and direct integration method can effectively overcome the shortcomings of a slow solution process and improve calculation efficiency. ese two methods are widely used in engineering to solve the numerical solution of dynamic problems. Formula (16) constitutes a two-dimensional system of second-order nonlinear time-varying differential equations. e direct integration method is effective for second-order nonlinear vibration systems, which has been verified in many studies [36,37]. In this study, the Newmark direct integration method is used to approximate the vibration response of the system. Under the action of a moving trolley, the flow chart of the dynamic response of the main beam and cabin is shown in Figure 7, and the calculation process is as follows: (1) Firstly, the system motion equation is established according to the system model and Lagrange equation, and the initial values of the vibration responses for the main beam are set to € q 0 , _ q 0 , and q 0 , Advances in Civil Engineering the initial values of the swing angle of the payload € θ x0 , _ θ x0 , and θ x0 are set to zero, and the initial values of cabin vibration response € z d0 , _ z d0 , and z d0 are all zero. e dynamic responses € q Δt , _ q Δt , and q Δt at Δt time in equation (17) are calculated based on the Newmark method.
(2) e results obtained in the first step are substituted into equations (23) and (24), and the payload angle responses € θ xΔt , _ θ xΔt , and θ xΔt of the crane are calculated by the Newmark method. e cabin vibration responses are also obtained.
(3) e results obtained in Step (2) are substituted as the initial value of the next iteration into Step (1) to calculate the vibration response of the main beam at the next moment, and Step (2) is repeated. Calculation Steps (1) and (2) are iterated until the preset termination time, and the numerical solutions of the beam, swing angle of the crane, and cabin vibration are obtained. (4) e convergence of calculation results € q(t), € θ x (t), and € z d (t) is tested. If they do not converge, return to Step (2) for further analysis and calculation.

Verification of Main Girder Vibration Response.
To further confirm the reliability of the presented formulae and the developed computer programs, a pinned-pinned beam subjected to a moving mass m � 70 kg and constant speed of V mx � 3.34 m/s was also investigated. e length of the beam was L b � 10 m, the cross-sectional area was A � 9.0024 × 10 − 4 m 2 , and second moment of area was I � 1.04 × 10 − 6 m 4 . e mass density was ρ � 7820 kg/m 3 , and Young's modulus was E � 2.068 × 10 11 N/m 2 . e above information of the beam was almost the same as references [38,39]. Figure 2 shows the time histories for the vertical central displacements of the pinned-pinned beam. In reference [39], the influence of the moving mass on the midpoint shape of the simply supported beam was solved by using finite element theory. Additionally, in reference [38], the dynamic response of the middle point of the main beam was solved under a modal assumption. However, in this study, the timedomain response of the midpoint vibration of the main beam was solved by combining the modal hypothesis with the energy conservation of the system. As can be seen from Figure 8, three calculation results were consistent with the underlying trend. Since the differences between the last three curves were small, the formulations and computer programs developed in this study should be available for calculating the dynamic responses of a structure due to a moving load.

Verification of Swing Angle.
e payload swing is affected by the carriage traverse acceleration and the length of the wire rope. e reliability of the presented formulae and the developed computer programs were further confirmed with regard to the swing angle. A pinned-pinned beam was subjected to a moving mass of m c � 97.9 kg and a payload mass of m p � 97.9kg. e beam had a length of l b � 6 m, cross-sectional area of A � 2.04 × 10 − 2 m 2 , and second moment of area I � 2.13 × 10 − 7 m 4 . e mass density was ρ � 8000 kg/m 3 , and Young's modulus was E � 2.11 × 10 11 N/m 2 . In practice, the carriage starts with an initial velocity of zero and accelerates to a particular speed, which could be held constant for some time before decelerating to rest. In all cases, the terminal times of the intervals were t 1 � 15 s, t 2 � 45 s, and t 3 � 60 s, the speed during the constant speed phase was V � 0.1333 m/s, and the  deceleration phase occurred over the last meter of the motion. e initial displacements for each swing angle were θ x (0) − 0.01(rad). e mass of the cabin, connection sti ness, and damping, were all set to zero. By ignoring the structural damping e ect, the factors were considered to be consistent with those reported in [31]. From Figure 9, it can be seen that the results of this study are similar to those reported in [31], which proves the validity of the calculation principle and procedure.

Engineering Applications
A 100/40t − 28.5 m casting crane as an example is selected. During service, rail defects are caused by foundation subsidence, which leads to strong hoistman vibration and equipment damage. e initial parameters of the crane vibration system are listed in Table 4.

Trolley Operation Modes.
Compared with other cranes, the ladle lifted by the casting crane is a very dangerous piece of equipment. e excessive speed of operation can produce an excessive swing angle of the ladle, which greatly reduces the safety of the production process. e relevant operating parameters of the trolley can be found in the standard [40,41], and the maximum speed of the trolley is 63 m/min. However, the running speed may be larger than this value in special cases. e maximum speed of the trolley is less than that of other cranes at approximately 80 m/min. According to the operation speed of the casting crane provided by a certain company and combined with the most dangerous working conditions, three running speed modes of the trolley system are shown in Figure 10 based on literature [39,42]. ree modes of operation that have a higher frequency of occurrence in actual crane operation are derived from a company. e acceleration and deceleration time of the trolley is set to 5 s, and the trajectory of the trolley extends from the limit position on one side to the limit position on the other side. e maximum running speed of the trolley is set to V 3 m 1.2 m/s. If the trolley runs safely in this mode, the stability of the other two modes can be guaranteed, thus ensuring trolley safety during operation. e results in the following sections are based on these three modes of trolley operation.

Main Beam Dynamic Response to Temperature.
Because temperature has a large in uence on the elastic modulus and mechanical properties of metal structures, and the casting crane operates under high temperature, it is necessary to analyze the dynamic characteristics of the main girder under the action of temperature. According to the literature [26], the elastic modulus of the main beam decreases substantially at temperatures above   300°C, so the midspan displacement of the main beam is signi cantly increased. erefore, the temperature of the main beam in the midspan response calculation should be above 300°C. e parameters of the crane are selected, and the dynamic response of the main girder in the midspan is calculated according to the elastic modulus at di erent temperatures obtained from the test (Figure 11). e maximum displacement of the main girder beam is 7 mm and 11 mm at 20°C and 600°C, respectively. e vertical center displacement of the main beam increases by 57.1% at 600°C than 20°C. More importantly, when the crane runs at full load, the increase of midspan displacement may directly lead to deformation of the crane beam that exceeds the maximum allowable displacement of the crane; this poses a major threat to humans and property. erefore, the in uence of temperature on the dynamic characteristics of the main beam must be considered during the design stage of the crane.
Under the initial parameters of Table 4, equation (9) is employed to calculate the elastic modulus at di erent temperatures, and the dynamic characteristics of the main beam are obtained by varying the temperature, as shown in Figure 12. With increasing temperature, the maximum midspan displacement of the main beam increases gradually.
is is because high temperature tends to decrease the elastic modulus of the main beam, resulting in a reduction of main beam sti ness, which causes an increase of the midspan displacement amplitude of the main beam during trolley operation.

Cabin Displacement Response.
e cabin vibration response at di erent temperatures is shown in Figure 13. e maximum amplitude of cabin vibration is 3 mm and 4.3 mm at 20°C and 600°C, respectively. e vibration displacement of the cabin increases by 32.5% with increasing temperature. e amplitude of cabin vibration will have a clear impact on human vibration comfort.

Cabin Acceleration Response.
e acceleration response results are shown in Figure 14, indicating that the maximum acceleration of the cabin is 2.45 m/s 2 , 2.25 m/s 2 , 2.25 m/s 2 , and 2.5 m/s 2 at 20°C, 300°C, 400°C, and 600°C, respectively. Although temperature has a signi cant in uence on vibrational displacement of the main beam and cabin, the in uence of temperature on vibrational acceleration of the cabin, which directly a ects the comfort of the hoistman, is not signi cant.

In uence of Yield Strength on Crane Structure Safety.
e yield strength will have a certain in uence on the safety of crane metal structures. According to the design method of metal structure for the mechanical equipment, the calculated stress of the dangerous position for the casting crane can be calculated according to the following equation: where σ is the calculated stress of the structure, N is the axial force of the structure, A j is the net area of the structural calculation section, M is the basic bending moment of the calculated section, w j is the net bending section coe cient of the calculated section, and [σ] is the allowable stress. When the ratio of yield strength to ultimate strength is greater than or equal to 0.7, the allowable stress of crane metal structure can be obtained according to the following equation: where σ s is the yield strength of steel, σ b is the ultimate strength of steel, and n i is the safety factor. Since the casting

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Advances in Civil Engineering  crane is in a room without wind, based on load combination A, the value of n i is 1.48 [43].
Equation (26) is used to calculate the allowable stress of the cast crane metal structure at different temperatures. Based on test results in Section 2.3.3 of the manuscript, the structural stress and safety evaluation results of the main beam at different temperatures are shown in Table 5.
As presented in Table 5, the safety margin of crane structure decreases with increasing temperature. When the temperature reaches 600°C, the safety margin is − 28.6 MPa, and the structure is in a failure state. erefore, in consideration of safety, the casting crane should try to avoid the radiation effect of high temperature on the structure so as to improve the safety margin of the crane.

Conclusion
(1) e elastic modulus values of Q355 steel at 20°C, 100°C, 200°C, 300°C, 400°C, and 600°C were measured using a metal elastic modulus test bed. e constitutive equation for the elastic modulus at different temperatures was obtained by a polynomial fitting method, which provided a theoretical basis for analyzing the influence of temperature on crane beam vibration. (2) e vibration model of a flexible beam-cabin-trolleycrane system based on temperature was established, and the dynamic characteristics of the beam at different temperatures were analyzed. With increasing temperature, the maximum midspan displacement of the main beam increased gradually. e midspan deflection of the main beam increased by 14.3%, 21.4%, and 57.1% at 300°C, 400°C, and 600°C, respectively. (3) e dynamic characteristics of the cabin during trolley operation at different temperatures were analyzed. Cabin vibrational displacement increased with increasing temperature and increased by 32.5% at 600°C. However, the influence of temperature on cabin vibrational acceleration is not significant. (4) When the crane runs at full load, the increase of midspan displacement may directly cause beam deformation to exceed the maximum allowable displacement of the crane, which poses a major threat to humans and property. erefore, the influence of temperature on the dynamic characteristics of the girder must be considered during the design stage of casting cranes.
(5) In a certain temperature range, the yield strength and tensile strength of metal structures decrease with increasing temperature, and the safety margin of crane metal structures decreases with increasing temperature. erefore, in order to increasing the safety margin of structure, a layer of insulation board made of asbestos mesh should be applied at the bottom of the main beam, which effectively prevents the partial radiation of temperature field to the main beam.

Data Availability
e data used to support the findings of this study are included within the article.

Conflicts of Interest
e authors declare no conflicts of interest.