Pipeline throwing force estimation method, system and device and storage medium

Abstract

The invention discloses a pipeline throwing force estimation method, system and device and a storage medium, and belongs to the technical field of mechanical property analysis. The method comprises the following steps: constructing a pipeline simplified model according to pre-acquired pipeline parameter data; according to the pipeline simplification model and pre-obtained anti-throwing piece parameter data, an anti-throwing piece simplification model is constructed; and calculating the throwing force of the pipeline by adopting a moment balance method, an energy balance method or a kinetic method based on the pipeline simplified model and the anti-throwing piece simplified model. According to the method, the pipeline simplified model and the anti-throwing piece simplified model are established, anti-throwing force calculation is converted into simple model calculation from heavy simulation material parameter design grid division and other processes, the calculation efficiency is improved, and the throwing force estimated value is efficiently obtained.

Description

Technical Field

[0001] The present invention belongs to the technical field of mechanical property analysis, and in particular relates to a pipeline whip force estimation method, system, device and storage medium. Background Art

[0002] The purpose of pipeline whip force estimation is to determine the magnitude of the whip force during the whip process, and roughly and conservatively obtain the displacement of the pipeline during the whip process, the force on the pipeline angle and U-shaped hoop and other pipeline anti-throw parts, so as to preliminarily determine the material, layout location and number of the pipeline U-shaped hoop anti-throw parts, thereby reducing the time consumed by simulation design. Therefore, fast and conservative calculation of pipeline whip force is of great significance for the calculation and research of mechanical properties in scenarios such as steam distribution pipelines.

[0003] The current method for estimating the impact force requires heavy simulation of material parameters to design mesh division, then simulate the mechanical characteristics of the pipeline based on the material parameters and mesh, and then perform calculation analysis based on the simulation results to complete the estimation of the impact force. This calculation process requires the use of professional simulation software, and the amount of data calculated is large and the calculation is time-consuming.

[0004] In view of this, how to overcome the defects of the prior art and solve the problem that the existing impact force estimation method is computationally cumbersome is a problem to be solved in this technical field. Summary of the invention

[0005] The purpose of the present invention is to overcome the deficiencies in the prior art and provide a pipeline whip force estimation method, system, device and storage medium to improve calculation efficiency and efficiently obtain whip force estimation values.

[0006] The present invention provides the following technical solutions:

[0007] In a first aspect, a method for estimating the pipeline impact force is provided, comprising: constructing a simplified pipeline model based on pre-acquired pipeline parameter data; constructing a simplified anti-throwing component model based on the simplified pipeline model and pre-acquired anti-throwing component parameter data; and calculating the pipeline impact force based on the simplified pipeline model and the simplified anti-throwing component model by using a torque balance method, an energy balance method or a dynamics method.

[0008] As an optional technical solution of the present invention, the pipeline parameter data includes pipeline length, pipeline outer radius, pipeline inner radius, pipeline yield stress, pipeline ultimate stress, pipeline tensile strength and injection force applied to the pipeline; the anti-throwing part parameter data includes the initial state bending radius of the anti-throwing part, the initial gap between the anti-throwing part and the pipeline and the length of the straight hoop section of the anti-throwing part.

[0009] As an optional technical solution of the present invention, the step of constructing a simplified pipeline model includes:

[0010] Calculate the plastic limit bending moment M of the pipeline p , expressed as:

[0011]

[0012] Among them, σ y represents the pipe yield stress, r o Represents the outer radius of the pipe, r i Indicates the inner radius of the pipe;

[0013] Calculate the full section yield length L of the pipeline s and dynamic plastic deformation length L p , expressed as:

[0014]

[0015] Where, F represents the jet force;

[0016] Calculate the ultimate bending moment M of the pipeline pe , expressed as:

[0017]

[0018] Among them, σ u Indicates the ultimate stress of the pipeline;

[0019] Calculation of the stress hardening length L of the pipeline based on the ultimate bending moment of the pipeline e , expressed as:

[0020]

[0021] Compare the pipe length L with the full section yield length L s , Dynamic plastic length L p and stress hardening length L e The size of the jet force is determined to determine the distance L1 from the jet force action point to the pipeline rotation point and the distance L2 from the anti-throwing part to the pipeline rotation point, so as to construct a simplified pipeline model.

[0022] As an optional technical solution of the present invention, during the swinging motion of the pipeline, the stage when the pipeline is not in contact with the anti-swinging member is regarded as the free swinging stage; the stage when the pipeline is in contact with the anti-swinging member and is tensioned is regarded as the restricted swinging stage;

[0023] The construction of the simplified model of the anti-throwing component comprises:

[0024] In the free swing stage, the total length L of the anti-swing member u0 It is expressed as:

[0025] L u0 =2h c +πb c ;

[0026] Among them, h c Indicates the length of the straight hoop section of the anti-throwing piece, b c Indicates the bending radius of the anti-throwing part in the initial state;

[0027] The initial center position H0 of the pipeline is expressed as:

[0028] H0=h c +b c -Gr o -d;

[0029] Where G represents the initial gap between the anti-throwing piece and the pipe, d represents the width of the cross section of the anti-throwing piece,

[0030] When the pipeline contacts the anti-throwing piece, the total length L of the anti-throwing piece u1 (α) is expressed as:

[0031] L u1 (α)=2[L1(α)+L2(α)+L3(α)];

[0032] Wherein, α represents the angle between the vertical line of the pipeline center and the straight hoop section of the anti-throwing piece, L1(α)+L2(α) represents the length of the straight hoop section of the anti-throwing piece after contact, L1(α)=b1(α)sin(α), b1(α)=(r0+d) / cos(α), L3(α) represents the half bending length of the anti-throwing piece after contact.

[0033] The center position H(α) of the pipeline after the pipeline contacts the anti-throwing member is expressed as:

[0034]

[0035] When in contact, the total length of the anti-throwing member is L u1 When (α) is equal to the total length Lu0 of the anti-throwing member, it is at the critical point of the anti-throwing member tensioning. The distance between the initial center position of the pipeline and the center position of the pipeline at the critical point is taken as the equivalent gap G effect , expressed as:

[0036] G effect =H(α0)-H0;

[0037] Among them, α0 represents the angle between the vertical line of the pipeline center and the straight hoop section of the anti-throwing piece when it is at the critical point;

[0038] The turning angle θ1 of the pipeline at the critical point is expressed as:

[0039]

[0040] Wherein, L2 represents the distance from the anti-throwing part to the rotation point of the pipeline;

[0041] After the critical point, the limiting whipping stage is reached. The distance h(θ) between the center position of the pipeline in the limiting whipping stage and the initial center position of the pipeline is expressed as:

[0042] h(θ)=θ×L2;

[0043] Among them, θ represents the radian of the pipe's rotation angle;

[0044] In the limited whipping stage, the center position of the pipeline H(θ) is expressed as:

[0045] H(θ)=h(θ)+H0;

[0046] According to H(α)=H(θ), we can get the expression of α with respect to θ:

[0047]

[0048] According to the expression of α with respect to θ, the average deformation ε(θ) of the anti-throwing member in the limiting throw-off stage is calculated and expressed as:

[0049]

[0050] Among them, L u1 (θ) represents the total length of the anti-throwing component in the stage of limiting the swinging;

[0051] In the stage of limiting the swinging, the swinging force load F acting on the anti-swinging part r (θ) is expressed as:

[0052]

[0053] Where M represents the number of anti-throwing parts, σ(θ) represents the average stress of the anti-throwing parts, which is calculated by the average deformation ε(θ);

[0054] The simplified model of the anti-throwing component is expressed as:

[0055]

[0056] As an optional technical solution of the present invention, the method of calculating the whipping force of the pipeline by using the moment balance method includes:

[0057] Calculate the breaking moment M of the pipeline r , expressed as:

[0058]

[0059] Among them, R m Indicates the average radius of the pipe, R m =(ro +r i ) / 2,σ r Indicates the tensile strength of the pipe;

[0060] Based on the pipeline's rupture moment M r Calculate the pipe's fracture length L r , expressed as:

[0061]

[0062] Where, F represents the jet force;

[0063] According to the simplified pipeline model, the distance L1 from the jet force action point to the pipeline rotation point and the distance L2 from the anti-throwing part to the pipeline rotation point are obtained to calculate the pipeline's swing force F R , expressed as:

[0064]

[0065] Where K represents the power amplification factor.

[0066] As an optional technical solution of the present invention, the method of calculating the whipping force of the pipeline by using the energy balance method includes:

[0067] In the free swinging stage, calculate the external work E done by the jet force W1 , expressed as:

[0068] E w1 = FL1θ0;

[0069] Calculate the energy E absorbed by the plastic locking hinge p1 , expressed as:

[0070] E p1 =M p θ0;

[0071] Where F represents the injection force, θ0 represents the initial arc of the pipeline rotation angle, L1 represents the distance from the injection force application point to the pipeline rotation point, and M p represents the plastic limit bending moment;

[0072] Calculate the kinetic energy E of the pipeline during the free slamming stage k1 , expressed as:

[0073] E k1 =E w1 -E p1 ;

[0074] In the limited swing stage, calculate the external work E done by the jet force w2 , expressed as:

[0075] E w2= FL1(θ-θ0);

[0076] Calculate the energy E absorbed by the plastic locking hinge p2 , expressed as:

[0077] E p2 =M p (θ-θ0);

[0078] Among them, θ represents the radian of the pipe's rotation angle;

[0079] The sum of the kinetic energy of the pipe E k It is expressed as:

[0080] E k =E k1 +E k2 ;

[0081] When the sum of the kinetic energy of the pipe's impact E k When all of them are converted into the local plastic deformation performance of the pipeline, the impact force reaches the maximum value, which is expressed as:

[0082] E pipe =E k ;

[0083] Among them, E pipe It indicates the kinetic energy of the impact converted from the maximum impact force;

[0084] Convert the maximum impact force into impact kinetic energy E pipe , expressed as:

[0085]

[0086] Wherein, G represents the initial gap between the anti-throwing component and the pipeline;

[0087] The distance h(θ′) between the center position of the pipeline and the initial center position of the pipeline when the swing force reaches the maximum value is obtained by solving the problem. The maximum swing force P is calculated based on the simplified model of the anti-swing component. max , expressed as:

[0088] P max =F r (θ′).

[0089] As an optional technical solution of the present invention, the method of calculating the whipping force of the pipeline by using a dynamic method includes:

[0090] In the free-throwing stage, the angular acceleration C1 of the pipeline end motion is calculated and expressed as:

[0091]

[0092] Among them, M prepresents the plastic limit bending moment, L2 represents the distance from the anti-throwing part to the pipeline rotation point, F represents the injection force, and I represents the pipeline inertia moment. m represents the mass per unit length of the pipeline, and L1 represents the distance from the point of action of the jet force to the point of rotation of the pipeline;

[0093] Calculate the initial arc of the pipeline rotation angle θ0 during the free whipping stage, expressed as:

[0094]

[0095] Wherein, G represents the initial gap between the anti-throwing component and the pipeline;

[0096] Calculate the angular velocity ω1 of the pipe end motion during the free whipping stage, expressed as:

[0097]

[0098] In the limiting whipping stage, the deformation length x(n) of the anti-swinging member after the pipeline rotates n units is calculated and expressed as:

[0099] x(n)-G effect =L2nΔθ;

[0100] Among them, Δθ represents the angular radian of each rotation unit of the pipeline, G effect represents the equivalent gap;

[0101] Based on the simplified model of the anti-throwing member, the anti-throwing member deformation length x(n) after the pipeline rotates n units is used to obtain the impact force load F after the pipeline rotates n units. r (n);

[0102] The angular acceleration C(n) of the end of the pipeline after the pipeline rotates n units is expressed as:

[0103]

[0104] The angular velocity ω(n) is iteratively calculated based on the angular acceleration C(n), expressed as:

[0105]

[0106] When |ω(n)|≤set value, n=n1, the maximum deformation length x(n1) of the anti-throwing part is obtained;

[0107] Based on the simplified model of the anti-throwing member, the maximum impact force load F is obtained according to the maximum deformation length x(n1) of the anti-throwing member. r (θ′), then the maximum impact force F Rmax It is expressed as:

[0108] F Rmax =F r(θ′).

[0109] In a second aspect, a pipeline whip force estimation system is provided, comprising: a pipeline simplified model construction module, for constructing a pipeline simplified model according to pre-acquired pipeline parameter data;

[0110] A simplified model of an anti-throwing component; a construction module, used to construct a simplified model of an anti-throwing component according to the simplified pipeline model and pre-acquired anti-throwing component parameter data;

[0111] The calculation module is used to calculate the impact force of the pipeline based on the simplified model of the pipeline and the simplified model of the anti-throwing component by using the moment balance method, the energy balance method or the dynamic method.

[0112] In a third aspect, a pipeline impact force estimation device is provided, comprising a processor and a storage medium; the storage medium is used to store instructions; the processor is used to operate according to the instructions to execute the steps of the pipeline impact force estimation method described in the first aspect.

[0113] In a fourth aspect, a computer-readable storage medium is provided, on which a computer program is stored, and when the program is executed by a processor, the steps of the pipeline impact force estimation method described in the first aspect are implemented.

[0114] Compared with the prior art, the present invention has the following beneficial effects:

[0115] A pipeline impact force estimation method provided by the present invention establishes a simplified pipeline model and a simplified anti-throwing component model, and transforms the anti-throwing force calculation from a heavy simulation material parameter design grid division process to a simple model for calculation, thereby improving the calculation efficiency and efficiently obtaining the estimated value of the impact force. BRIEF DESCRIPTION OF THE DRAWINGS

[0116] Figure 1 is a flow chart of a pipeline whip force estimation method according to an embodiment of the present invention;

[0117] Figure 2 is a schematic diagram of a pipeline cantilever arm model in an embodiment of the present invention;

[0118] Figure 3 is a schematic diagram of a simplified pipeline model in an embodiment of the present invention;

[0119] Figure 4 is a schematic diagram of a pipeline and an anti-throwing member in an embodiment of the present invention;

[0120] Figure 5 is a schematic diagram of a spring model of an anti-throwing member in an embodiment of the present invention;

[0121] Figure 6 4 is a load-displacement relationship curve diagram of the anti-throwing component in the embodiment of the present invention.

[0122] Description in the figure: 1. Pipe; 2. Anti-throwing parts. DETAILED DESCRIPTION

[0123] The present invention will be further described below in conjunction with the accompanying drawings. The following embodiments are only used to more clearly illustrate the technical solution of the present invention, and cannot be used to limit the protection scope of the present invention.

[0124] Example 1

[0125] This embodiment provides a pipeline whip force estimation method, which is applied to steam distribution pipelines. Figure 1 As shown, the specific steps include:

[0126] Step 1: Construct a simplified pipeline model based on the pre-acquired pipeline parameter data.

[0127] In this embodiment, Figure 2 As shown, the pipeline is modeled as a cantilever beam. When the pipeline is made of rigid-plastic material and has a small deformation, the steam injection load borne by the pipeline will determine the deformation state and rotation point of the pipeline. Based on the rigid-plastic dynamic response analysis of the cantilever beam under a constant step load, the characteristic lengths on the cantilever beam corresponding to the pipeline can be obtained. In actual implementation, the characteristic length of the pipeline is determined by the pipeline parameter data, thereby constructing a simplified pipeline model. Among them, the pipeline parameter data includes pipeline length, pipeline outer radius, pipeline inner radius, pipeline yield stress, pipeline ultimate stress, pipeline tensile strength and injection force applied to the pipeline. The specific construction process includes:

[0128] 1.1. Calculate the plastic limit bending moment M of the pipeline p , expressed as:

[0129]

[0130] Among them, σ y represents the pipe yield stress, r o Represents the outer radius of the pipe, r i Indicates the inner radius of the pipe.

[0131] 1.2. Calculate the full section yield length L of the pipeline s and dynamic plastic deformation length L p , expressed as:

[0132]

[0133] Wherein, F represents the ejection force.

[0134] 1.3. Calculate the ultimate bending moment M of the pipeline pe , expressed as:

[0135]

[0136] Among them, σ u Indicates the ultimate stress of the pipeline.

[0137] 1.4. Calculation of the stress hardening length L of the pipeline based on the ultimate bending moment of the pipeline e , expressed as:

[0138]

[0139] Compare the pipe length L with the full section yield length L s , Dynamic plastic length L p and stress hardening length L e The size of is determined to determine the distance L1 from the injection force action point to the pipeline rotation point and the distance L2 from the anti-throwing part to the pipeline rotation point, so as to construct a simplified pipeline model. See Table 1 for details:

[0140]

[0141] The constructed simplified pipeline model is as follows Figure 3 As shown, the A end of the pipe is the rotation point, the B end is the free end, L1 represents the distance between the injection force point generated by the steam injection head and the rotation point of the pipe, L2 represents the distance from the anti-throwing part to the rotation point, F represents the injection force generated by the injection head, and F R It indicates the whipping force, i.e. the whipping force borne by the pipeline. The direction of the arrow is the direction of the jetting force and the whipping force borne by the pipeline. The distance from the anti-swinging part to the pipeline rotation point is L2 = L1-D, where D indicates the distance between the anti-swinging part and the jetting point.

[0142] Step 2: Construct a simplified model of the anti-throwing component based on the simplified pipeline model and the pre-acquired anti-throwing component parameter data.

[0143] like Figure 4 As shown, in a common implementation scenario, the pipeline 1 will be fixed by the anti-throwing part 2, and there is a certain gap between the pipeline 1 and the anti-throwing part 2. During the swinging movement of the pipeline, the stage when the pipeline is not in contact with the anti-throwing part is regarded as the free swinging stage; the stage when the pipeline is in contact with the anti-throwing part and is tensioned is regarded as the restricted swinging stage. In these two stages, the mechanical properties borne by the pipeline will change. Modeling is performed according to the anti-throwing part parameter data, and then the anti-throwing force is estimated based on the simplified model of the anti-throwing part. Among them, the anti-throwing part parameter data includes the initial bending radius of the anti-throwing part, the initial gap between the anti-throwing part and the pipeline, and the length of the straight hoop section of the anti-throwing part.

[0144] The anti-swinging parts of the main steam pipeline are U-shaped hoops, Ω-shaped hoops or U-bar hoops. These types of anti-swinging parts have similar mechanical properties in terms of anti-swinging. In this embodiment, the anti-swinging parts are regarded as U-shaped hoops during modeling. Figure 5 The spring model shown in the figure is used to build a simplified model of the anti-throwing part based on the mechanical model of the spring. The specific construction process is as follows:

[0145] 2.1. In the free swinging stage, the total length L of the anti-swinging member u0 It is expressed as:

[0146] L u0 =2h c +πb c ;

[0147] Among them, h c Indicates the length of the straight hoop section of the anti-throwing piece, b c Indicates the bending radius of the anti-throwing component in the initial state.

[0148] The initial center position H0 of the pipeline is expressed as:

[0149] H0=h c +b c -Gr o -d;

[0150] Wherein, G represents the initial gap between the anti-throwing piece and the pipeline, and d represents the width of the cross section of the anti-throwing piece.

[0151] 2.2. When the pipe contacts the anti-throwing piece, the total length L of the anti-throwing piece u1 (α) is expressed as:

[0152] L u1 (α)=2[L1(α)+L2(α)+L3(α)];

[0153] Wherein, α represents the angle between the vertical line of the pipeline center and the straight hoop section of the anti-throwing piece, L1(α)+L2(α) represents the length of the straight hoop section of the anti-throwing piece after contact, L1(α)=b1(α)sin(α), b1(α)=(r0+d) / cos(α), L3(α) represents the half bending length of the anti-throwing piece after contact.

[0154] When the pipeline contacts the anti-throwing member, the center position H(α) of the pipeline is expressed as:

[0155]

[0156] When in contact, the total length of the anti-throwing member is L u1 When (α) is equal to the total length Lu0 of the anti-throwing member, it is at the critical point of the anti-throwing member tensioning. The distance between the initial center position of the pipeline and the center position of the pipeline at the critical point is taken as the equivalent gap G effect , expressed as:

[0157] G effect=H(α0)-H0;

[0158] Among them, α0 represents the angle between the vertical line of the pipeline center and the straight hoop section of the anti-throwing device at the critical point.

[0159] The turning angle θ1 of the pipeline at the critical point is expressed as:

[0160]

[0161] Wherein, L2 represents the distance from the anti-throwing member to the rotation point of the pipeline.

[0162] After the critical point, the limiting whipping stage is reached. The distance h(θ) between the center position of the pipeline in the limiting whipping stage and the initial center position of the pipeline is expressed as:

[0163] h(θ)=θ×L2;

[0164] Where θ represents the rotation angle of the pipe in radians.

[0165] 2.3. In the limited whipping stage, the center position H(θ) of the pipeline is expressed as:

[0166] H(θ)=h(θ)+H0;

[0167] According to H(α)=H(θ), we can get the expression of α with respect to θ:

[0168]

[0169] According to the expression of α with respect to θ, the average deformation ε(θ) of the anti-throwing member in the limiting throw-off stage is calculated and expressed as:

[0170]

[0171] Among them, L u1 (θ) represents the total length of the anti-swing component during the swing-off limiting stage.

[0172] In the stage of limiting the swinging, the swinging force load F acting on the anti-swinging part r (θ) is expressed as:

[0173]

[0174] Where M represents the number of anti-throwing parts, σ(θ) represents the average stress of the anti-throwing parts, which is calculated by the average deformation ε(θ);

[0175] The simplified model of the anti-throwing component is expressed as:

[0176]

[0177] According to the simplified model of the anti-throwing part, the load-displacement curve of the anti-throwing part is obtained as follows: Figure 6 shown.

[0178] Step 3: Based on the simplified pipeline model and the simplified anti-throwing component model, the thrust force of the pipeline is calculated by using a moment balance method, an energy balance method or a dynamics method.

[0179] (1) The moment balance method is used to calculate the pipeline's impact force. Based on the simplified model of the pipeline and the simplified model of the anti-throwing component, the statics method is used in combination with different magnification factors to calculate the impact force. Specifically, it includes:

[0180] Calculate the pipe breaking moment M r , expressed as:

[0181]

[0182] Among them, R m Indicates the average radius of the pipe, R m =(r o +r i ) / 2,σ r Indicates the tensile strength of the pipe.

[0183] Based on the pipeline's rupture moment M r Calculate the pipe's fracture length L r , expressed as:

[0184]

[0185] Wherein, F represents the ejection force.

[0186] According to the simplified pipeline model, the distance L1 from the injection force action point to the pipeline rotation point and the distance L2 from the anti-throwing part to the pipeline rotation point are obtained to calculate the pipeline's swing force F R , expressed as:

[0187]

[0188] Where K represents the power amplification factor.

[0189] (2) The energy balance method is used to calculate the pipeline's whipping force, specifically including:

[0190] In the free swinging stage, calculate the external work E done by the jet force W1 , expressed as:

[0191] E w1 = FL1θ0;

[0192] Calculate the energy E absorbed by the plastic locking hinge p1 , expressed as:

[0193] E p1 =Mp θ0;

[0194] Where F represents the injection force, θ0 represents the initial arc of the pipeline rotation angle, L1 represents the distance from the injection force application point to the pipeline rotation point, and M p represents the plastic limit bending moment.

[0195] Calculate the kinetic energy E of the pipeline during the free slamming stage k1 , expressed as:

[0196] E k1 =E w1 -E p1 ;

[0197] In the limited swing stage, calculate the external work E done by the jet force w2 , expressed as:

[0198] E w2 = FL1(θ-θ0);

[0199] Calculate the energy E absorbed by the plastic locking hinge p2 , expressed as:

[0200] E p2 =M p (θ-θ0);

[0201] Where θ represents the rotation angle of the pipe in radians.

[0202] The sum of the kinetic energy of the pipe E k It is expressed as:

[0203] E k =E k1 +E k2 ;

[0204] When the sum of the kinetic energy of the pipe's impact E k When all of them are converted into the local plastic deformation performance of the pipeline, the impact force reaches the maximum value, which is expressed as:

[0205] E pipe =E k ;

[0206] Among them, E pipe It indicates the kinetic energy of the impact converted from the maximum impact force.

[0207] Convert the maximum impact force into impact kinetic energy E pipe , expressed as:

[0208]

[0209] Wherein, G represents the initial gap between the anti-throwing part and the pipeline.

[0210] The distance h(θ′) between the center position of the pipeline and the initial center position of the pipeline when the swing force reaches the maximum value is obtained by solving the problem. The maximum swing force P is calculated based on the simplified model of the anti-swing component. max , expressed as:

[0211] P max =F r (θ′).

[0212] (3) The method of calculating the pipeline's impact force using the dynamics method specifically includes:

[0213] In the free-throwing stage, the angular acceleration C1 of the pipeline end motion is calculated and expressed as:

[0214]

[0215] Among them, M p represents the plastic limit bending moment, L2 represents the distance from the anti-throwing part to the pipeline rotation point, F represents the injection force, and I represents the pipeline inertia moment. m represents the mass per unit length of the pipeline, and L1 represents the distance from the point of action of the injection force to the point of rotation of the pipeline.

[0216] Calculate the initial arc of the pipeline rotation angle θ0 during the free whipping stage, expressed as:

[0217]

[0218] Wherein, G represents the initial gap between the anti-throwing component and the pipeline;

[0219] Calculate the angular velocity ω1 of the pipe end motion during the free whipping stage, expressed as:

[0220]

[0221] In the limiting whipping stage, the deformation length x(n) of the anti-swinging member after the pipeline rotates n units is calculated and expressed as:

[0222] x(n)-G effect =L2nΔθ;

[0223] Among them, Δθ represents the angular radian of each rotation unit of the pipeline, G effect Indicates the equivalent gap.

[0224] Based on the simplified model of the anti-throwing member, the anti-throwing member deformation length x(n) after the pipeline rotates n units is used to obtain the impact force load F after the pipeline rotates n units. r (n);

[0225] The angular acceleration C(n) of the end of the pipeline after the pipeline rotates n units is expressed as:

[0226]

[0227] The angular velocity ω(n) is iteratively calculated based on the angular acceleration C(n), expressed as:

[0228]

[0229] When |ω(n)|≤set value, n=n1, the maximum deformation length x(n1) of the anti-throwing part is obtained;

[0230] Based on the simplified model of the anti-throwing member, according to the maximum deformation length x(n1) of the anti-throwing member, find Figure 6 The ordinate corresponding to x(n1) gives the maximum impact force load F r (θ′), then the maximum impact force F Rmax It is expressed as:

[0231] F Rmax =F r (θ′).

[0232] In this embodiment, the pipeline parameter data pipeline length L = 2713mm, pipeline yield stress σ y =198MPa, pipeline ultimate stress σ u =470MPa, pipe outer radius r o =162.5mm, pipe inner radius r i =147.5mm, injection force F = 430600.426224N, distance between anti-throwing piece and injection point D = 650mm to construct a simplified pipeline model, and use the anti-throwing piece parameter data to determine the length of the straight hoop section of the anti-throwing piece h c =250mm, initial bending radius of anti-throwing piece b c =202.5mm, the initial gap between the anti-throwing piece and the pipe G=30mm to build a simplified model of the anti-throwing piece. Based on the constructed model, three methods were used to estimate the impact force, and the results are as follows: the impact force estimated by the moment balance method is 849407.869373N; the impact force estimated by the energy balance method is 1399593.087098N; the impact force estimated by the dynamics method is 1405325.648887N.

[0233] Example 2

[0234] This embodiment provides a pipeline whip force estimation system, including:

[0235] The pipeline simplification model building module is used to build a pipeline simplification model according to pre-acquired pipeline parameter data.

[0236] A simplified model of an anti-throwing component; and a construction module, used to construct a simplified model of an anti-throwing component based on the simplified pipeline model and pre-acquired anti-throwing component parameter data.

[0237] The calculation module is used to calculate the impact force of the pipeline based on the simplified model of the pipeline and the simplified model of the anti-throwing component by using the moment balance method, the energy balance method or the dynamic method.

[0238] Example 3

[0239] This embodiment provides a pipeline impact force estimation device, including a processor and a storage medium; the storage medium is used to store instructions; the processor is used to operate according to the instructions to execute the steps of the pipeline impact force estimation method described in Example 1.

[0240] Example 4

[0241] This embodiment provides a computer-readable storage medium on which a computer program is stored. When the program is executed by a processor, the steps of the pipeline whip force estimation method described in Embodiment 1 are implemented.

[0242] Those skilled in the art will appreciate that the embodiments of the present application may be provided as methods, systems, or computer program products. Therefore, the present application may adopt the form of a complete hardware embodiment, a complete software embodiment, or an embodiment in combination with software and hardware. Moreover, the present application may adopt the form of a computer program product implemented on one or more computer-usable storage media (including but not limited to disk storage, CD-ROM, optical storage, etc.) that contain computer-usable program code.

[0243] The present application is described with reference to the flowcharts and / or block diagrams of the methods, devices (systems), and computer program products according to the embodiments of the present application. It should be understood that each process and / or box in the flowchart and / or block diagram, as well as the combination of the processes and / or boxes in the flowchart and / or block diagram, can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, a special-purpose computer, an embedded processor, or other programmable data processing device to generate a machine, so that the instructions executed by the processor of the computer or other programmable data processing device generate instructions for implementing the processes in the flowchart and / or block diagram. Figure 1 A process or multiple processes and / or boxes Figure 1 A device that provides the functions specified in a block or multiple blocks.

[0244] These computer program instructions may also be stored in a computer readable memory capable of directing a computer or other programmable data processing device to operate in a specific manner, so that the instructions stored in the computer readable memory produce an article of manufacture including an instruction device, which implements the process Figure 1 A process or multiple processes and / or boxes Figure 1 A function specified in one or more boxes.

[0245] These computer program instructions can also be loaded onto a computer or other programmable data processing device so that a series of operating steps are executed on the computer or other programmable device to produce a computer-implemented process, thereby providing instructions for implementing the process. Figure 1 A process or multiple processes and / or boxes Figure 1 The steps for the functions specified in one or more boxes.

[0246] The above is only a preferred embodiment of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the technical principles of the present invention. These improvements and modifications should also be regarded as the scope of protection of the present invention.

Claims

1. A method for estimating pipeline whipping force, characterized in that: include: Construct a simplified pipeline model based on the pre-acquired pipeline parameter data; Constructing a simplified model of the anti-throwing component according to the simplified pipeline model and the pre-acquired anti-throwing component parameter data; Based on the simplified pipeline model and the simplified anti-throwing component model, the thrust force of the pipeline is calculated by using a moment balance method, an energy balance method or a dynamics method.

2. The method for estimating pipeline whipping force according to claim 1, characterized in that: The pipeline parameter data includes pipeline length, pipeline outer radius, pipeline inner radius, pipeline yield stress, pipeline ultimate stress, pipeline tensile strength and injection force applied to the pipeline; The anti-throwing piece parameter data include the anti-throwing piece's initial bending radius, the initial gap between the anti-throwing piece and the pipeline, and the length of the anti-throwing piece's straight hoop section.

3. The method for estimating pipeline whipping force according to claim 1, characterized in that: The construction pipeline simplifies the model, including: Calculate the plastic limit bending moment M of the pipeline p , expressed as: Among them, σ y represents the pipe yield stress, r o Represents the outer radius of the pipe, r i Indicates the inner radius of the pipe; Calculate the full section yield length L of the pipeline s and dynamic plastic deformation length L p , expressed as: Where, F represents the jet force; Calculate the ultimate bending moment M of the pipeline pe , expressed as: Among them, σ u Indicates the ultimate stress of the pipeline; Calculation of the stress hardening length L of the pipeline based on the ultimate bending moment of the pipeline e , expressed as: Compare the pipe length L with the full section yield length L s , Dynamic plastic length L p and stress hardening length L e The size of the jet force is determined to determine the distance L1 from the jet force action point to the pipeline rotation point and the distance L2 from the anti-throwing part to the pipeline rotation point, so as to construct a simplified pipeline model.

4. The pipeline whip force estimation method according to claim 1, characterized in that: During the swinging motion of the pipeline, the stage when the pipeline is not in contact with the anti-swinging piece is regarded as the free swinging stage; the stage when the pipeline is in contact with the anti-swinging piece and is tensioned is regarded as the restricted swinging stage; The construction of the simplified model of the anti-throwing component comprises: In the free swing stage, the total length L of the anti-swing member u0 It is expressed as: L u0 =2h c +πb c ; Among them, h c Indicates the length of the straight hoop section of the anti-throwing piece, b c Indicates the bending radius of the anti-throwing part in the initial state; The initial center position H0 of the pipeline is expressed as: H0=h c +b c -G-r o -d; Wherein, G represents the initial gap between the anti-throwing piece and the pipe, and d represents the width of the cross section of the anti-throwing piece; When the pipeline contacts the anti-throwing piece, the total length L of the anti-throwing piece u1 (α) is expressed as: L u1 (a)=2[L1(a)+L2(a)+L3(a)]; Wherein, α represents the angle between the vertical line of the pipeline center and the straight hoop section of the anti-throwing piece, L1(α)+L2(α) represents the length of the straight hoop section of the anti-throwing piece after contact, L1(α)=b1(α)sin(α), b1(α)=(r0+d) / cos(α ) , L3(α) represents the half bending length of the anti-throwing piece after contact, When the pipeline contacts the anti-throwing member, the center position H(α) of the pipeline is expressed as: The total length L of the anti-throwing member after contact u1 (α) and the total length of the anti-throwing member L u0 When the gap is equal, it is at the critical point of the tension of the anti-throwing part, and the distance between the initial center position of the pipeline and the center position of the pipeline at the critical point is taken as the equivalent gap G effect , expressed as: G effect =H(α0)-H0; Among them, α0 represents the angle between the vertical line of the pipeline center and the straight hoop section of the anti-throwing piece when it is at the critical point; The turning angle θ1 of the pipeline at the critical point is expressed as: Wherein, L2 represents the distance from the anti-throwing part to the rotation point of the pipeline; After the critical point, the limiting whipping stage is reached. The distance h(θ) between the center position of the pipeline in the limiting whipping stage and the initial center position of the pipeline is expressed as: h(θ)=θ×L2; Among them, θ represents the radian of the pipe's rotation angle; In the limited whipping stage, the center position of the pipeline H(θ) is expressed as: H(θ)=h(θ)+H0; According to H(α)=H(θ), we can get the expression of α with respect to θ: According to the expression of α with respect to θ, the average deformation ε(θ) of the anti-throwing member in the limiting throw-off stage is calculated and expressed as: Among them, L u1 (θ) represents the total length of the anti-throwing component in the stage of limiting the swinging; In the stage of limiting the swinging, the swinging force load F acting on the anti-swinging part r (θ) is expressed as: Where M represents the number of anti-throwing parts, σ(θ) represents the average stress of the anti-throwing parts, which is calculated by the average deformation ε(θ); The simplified model of the anti-throwing component is expressed as:

5. The method for estimating pipeline whipping force according to claim 4, characterized in that: The method of calculating the whipping force of the pipeline by using the moment balance method includes: Calculate the breaking moment M of the pipeline r , expressed as: Among them, R m Indicates the average radius of the pipe, R m =(r o +r i ) / 2,σ r Indicates the tensile strength of the pipe; Based on the pipeline's rupture moment M r Calculate the pipe's fracture length L r , expressed as: Where, F represents the jet force; According to the simplified pipeline model, the distance L1 from the injection force action point to the pipeline rotation point and the distance L2 from the anti-throwing part to the pipeline rotation point are obtained to calculate the pipeline's swing force F R , expressed as: Where K represents the power amplification factor.

6. The method for estimating pipeline whipping force according to claim 4, characterized in that: The energy balance method is used to calculate the pipeline's whipping force, including: In the free swinging stage, calculate the external work E done by the jet force W1 , expressed as: It is w1 =FL1θ0; Calculate the energy E absorbed by the plastic locking hinge p1 , expressed as: It is p1 =M p θ0; Where F represents the injection force, θ0 represents the initial arc of the pipeline rotation angle, L1 represents the distance from the injection force application point to the pipeline rotation point, and M p represents the plastic limit bending moment; Calculate the kinetic energy E of the pipeline during the free slamming stage k1 , expressed as: AND k1 =And w1 -AND p1 ; In the limited swing stage, calculate the external work E done by the jet force w2 , expressed as: E w2 =FL1(θ-θ0); Calculate the energy E absorbed by the plastic locking hinge p2 , expressed as: E p2 =M p (θ-θ0); Among them, θ represents the radian of the pipe's rotation angle; The sum of the kinetic energy of the pipe E k It is expressed as: AND k =And k1 +E k2 ; When the sum of the kinetic energy of the pipe's impact is E k When all of them are converted into the local plastic deformation performance of the pipeline, the impact force reaches the maximum value, which is expressed as: AND pipe =And k ; Among them, E pipe It indicates the kinetic energy of the impact converted from the maximum impact force; Convert the maximum impact force into impact kinetic energy E pipe , expressed as: Wherein, G represents the initial gap between the anti-throwing component and the pipeline; The distance h(θ′) between the center position of the pipeline and the initial center position of the pipeline when the swing force reaches the maximum value is solved, and the maximum swing force P is calculated according to the simplified model of the anti-swing component. max , expressed as: P max =F r (θ′).

7. The method for estimating pipeline whipping force according to claim 4, characterized in that: The method of calculating the whipping force of the pipeline by using the dynamic method includes: In the free-throwing stage, the angular acceleration C1 of the pipeline end motion is calculated and expressed as: Among them, M p represents the plastic limit bending moment, L2 represents the distance from the anti-throwing part to the pipeline rotation point, F represents the injection force, and I represents the pipeline inertia moment. m represents the mass per unit length of the pipeline, and L1 represents the distance from the point of action of the jet force to the point of rotation of the pipeline; Calculate the initial arc of the pipeline rotation angle θ0 during the free whipping stage, expressed as: Wherein, G represents the initial gap between the anti-throwing component and the pipeline; Calculate the angular velocity ω1 of the pipe end motion during the free whipping stage, expressed as: In the limiting whipping stage, the deformation length x(n) of the anti-swinging member after the pipeline rotates n units is calculated and expressed as: x(n)-G effect =L2nΔθ; Among them, Δθ represents the angular radian of each rotation unit of the pipeline, G effect Indicates the equivalent gap; Based on the simplified model of the anti-throwing member, the anti-throwing member deformation length x(n) after the pipeline rotates n units is used to obtain the impact force load F after the pipeline rotates n units. r (n); The angular acceleration C(n) of the end of the pipeline after the pipeline rotates n units is expressed as: The angular velocity ω(n) is iteratively calculated based on the angular acceleration C(n), expressed as: When |ω(n)|≤set value, n=n1, the maximum deformation length x(n1) of the anti-throwing part is obtained; Based on the simplified model of the anti-throwing member, the maximum impact force load F is obtained according to the maximum deformation length x(n1) of the anti-throwing member. r (θ′), then the maximum impact force F Rmax It is expressed as: F Rmax =F r (θ′).

8. A pipeline whip force estimation system, characterized in that: include: A pipeline simplification model building module is used to build a pipeline simplification model based on pre-acquired pipeline parameter data; A simplified model of an anti-throwing component; a construction module, used to construct a simplified model of an anti-throwing component according to the simplified pipeline model and pre-acquired anti-throwing component parameter data; The calculation module is used to calculate the impact force of the pipeline based on the simplified model of the pipeline and the simplified model of the anti-throwing component by using the moment balance method, the energy balance method or the dynamic method.

9. A pipeline whipping force estimation device, characterized in that: including processor and storage medium; The storage medium is used to store instructions; The processor is used to operate according to the instructions to execute the steps of the pipeline whip force estimation method according to any one of claims 1 to 7.

10. A computer-readable storage medium having a computer program stored thereon, characterized in that: When the program is executed by a processor, the steps of the pipeline whipping force estimation method according to any one of claims 1 to 7 are implemented.

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