Method for determining key values of movable rail switch frog

Abstract

The application discloses a method for determining key values of a movable heart rail frog, which comprises heart rail conversion calculation model determination, movable heart rail frog line type iterative calculation and key component value determination. The technical scheme provides a whole value determination method which is composed of three parts of a heart rail conversion model establishment method, a movable heart rail frog line type iterative calculation method and a key component value determination method. Compared with the existing method, the method of the application is closer to the actual working condition, and can make the structure size of the movable heart rail frog more accurate, the cooperation precision between each component higher and the frog structure more reasonable.

Description

Technical Field

[0001] This invention relates to the field of railways, and in particular to a method for determining key values ​​of a movable point frog. Background Technology

[0002] The close-fitting alignment of the frog rail / wing rail is part of the frog rail conversion displacement curve. Once the conversion displacement curve is determined, the working edge of the wing rail in the close-fitting area is determined. Under the traction of the switch machine, the frog rail can theoretically be converted to the same position as the working edge of the wing rail, achieving complete close fit. The existing frog rail conversion displacement curve design adopts the rigid body rotation method: based on the overall turnout alignment design scheme, frog rail conversion, turnout sleeper arrangement, and connecting component requirements, the theoretical tip, fixed end, and flexible bendable center positions of the long frog rail straight strand are determined respectively; an arc is drawn with the flexible bendable center as the center and the distance from the flexible bendable center to the theoretical tip of the long frog rail straight strand as the radius. The intersection of this arc with the working edge of the side strand is the theoretical tip of the long frog rail side strand; the line segment connecting the flexible bendable center and the theoretical tip of the long frog rail side strand is considered the straight strand working edge conversion displacement curve; the side strand working edge is rotated with the flexible bendable center as the rotation center, with the reference point being the theoretical tip of the long frog rail side strand and the target point being the theoretical tip of the long frog rail straight strand. The rotated curve is considered the side strand working edge conversion displacement curve.

[0003] Existing methods, based on experience, define the frog throat position as 120mm from the working edge of the straight lower rail and the working edge of the curved upper rail (this may be slightly adjusted according to the actual structure). The working edges (straight lower and curved upper rails) before the flexible bendable center are assumed to be rigid bodies. It is assumed that when the frog is switched under the traction of the switch machine, the working edges rigidly rotate based on the flexible bendable center, and the displacement only occurs before the flexible bendable center and is linear. However, the frog is actually an elastic body, and its cross-sectional structural characteristics vary significantly along the longitudinal direction of the track. These factors determine that the assumptions made by the existing design methods differ from reality. Using existing methods to design movable frogs will affect the accuracy of the frog's structural dimensions, and may even cause significant deviations in the structural dimensions of components. It is difficult to guarantee the accuracy of the dimensions of each component during manufacturing, resulting in a series of problems during the manufacturing and operation of the frog, such as poor frog / wing rail fit, excessive switching force, difficulty in assembling rail components and connectors, and high assembly stress in components. Furthermore, without changing the position of the frog throat and the flexible bendable center, the frog profile cannot be altered, thus preventing the optimization and improvement of the frog structure. Moreover, the positions of the flexible bendable center and the frog throat are mostly empirical values ​​and cannot be modified.

[0004] Therefore, a method for determining the key values ​​of a movable center point frog is needed to solve the above problems. Summary of the Invention

[0005] This invention addresses the problem in existing methods that simplify the flexible, bendable frog as a rigid body and use a rotation method to determine its displacement transition curve. However, since the frog is an elastic body with significant cross-sectional changes, there is a significant deviation between the actual and designed displacement transition curves. This invention provides a method for determining key values ​​of a movable frog, employing a method closer to actual working conditions. This results in more precise dimensions of the movable frog structure, higher precision in the fit between components, and a more rational frog structure, thus solving the aforementioned problems.

[0006] This invention provides a method for determining key values ​​of a movable point frog, comprising the following steps:

[0007] S1. Obtain the geometric features of the initial calculation model through the rigid body rotation method, and establish the orbital conversion calculation model based on the geometric features;

[0008] S2. Add the minimum distance between turnout rails under standard gauge and the maximum allowable positive tolerance of gauge in the turnout area to obtain the minimum flange groove width convergence value C;

[0009] S3, the calculation model for the conversion of the heart track is based on the existing dynamic path d. i The frog profile is obtained by solving the problem, and the corresponding minimum flange groove width t is calculated based on the frog profile. min ;

[0010] S4. Determine whether the absolute value of the minimum flange groove width convergence value C and the minimum flange groove width calculation value tmin is less than the allowable deviation a. If yes, proceed to step S6; otherwise, proceed to step S5.

[0011] S5. Determine the calculated value t of the minimum rim groove width. min If the minimum rim groove width convergence value C is greater than the minimum rim groove width, then reduce the dynamic stroke d. i After adjusting the value, calculate the minimum flange groove width t corresponding to the turnout line type. min Then proceed to step S4; otherwise, increase the stroke d. i After adjusting the value, calculate the minimum flange groove width t corresponding to the turnout line type. min Then proceed to step S4;

[0012] S6. Based on the calculated frog line type, calculate the geometric characteristic parameter values ​​of the long and short frog tracks, and update the frog track conversion calculation model through the geometric characteristic parameter values.

[0013] S7. Based on the updated track conversion calculation model, and using the traction point stroke d... i The initial frog profile is obtained by solving the problem, and the calculated value of the minimum flange groove width corresponding to the frog profile is obtained. tmin(i+1) ;

[0014] S8. Determine the convergence value C of the minimum rim groove width and the calculated value t of the minimum rim groove width. min(i+1) If the absolute value is less than the allowable deviation a, proceed to step S10; otherwise, proceed to step S9.

[0015] S9. Determine the calculated value t of the minimum rim groove width. min(i+1) If the minimum rim groove width convergence value C is greater than the minimum rim groove width, then reduce the dynamic stroke d. i After adjusting the numerical value, the minimum flange groove width t corresponding to the frog line calculation type is calculated. min(i+1) Then proceed to step S4; otherwise, increase the stroke d. i After adjusting the value, calculate the minimum flange groove width t corresponding to the turnout line type. min(i+1) Then proceed to step S4;

[0016] S10. Determine the conversion force F at each traction point of the track. i Is the rated switching force F of the switch machine at each traction point being output? is Minimum conversion force F when used with switch machines at each traction point ismin If the condition is met, proceed to step S12; otherwise, proceed to step S11.

[0017] S11. Determine the conversion force F at each traction point of the track. i The rated conversion force F output by the switch machine at each traction point is Minimum switching force F at each traction point switch machine ismin The numerical relationship between them, if the conversion force F at each traction point i The output rated switching force F of the switch machine at each traction point is greater than the rated switching force F. is Then, after increasing the width of the fork throat, proceed to step S1; if the conversion force F at each traction point... i Less than the minimum switching force F required for each traction point switch machine ismin Then reduce the width of the turnout throat and proceed to step S1;

[0018] S12. Output the current frog alignment as the optimal alignment for a movable point frog.

[0019] In the preferred embodiment of the method for determining key numerical values ​​of a movable point frog described in this invention, both the long and short point frogs are simulated using solid models in the point frog conversion calculation model. Coupled constraints are set in the close contact area of ​​the long point frog head and the close contact area of ​​the short point frog head. Frictional contact is set between the long point frog and the slide plate, and between the short point frog and the slide plate. Full constraints are set at the fixed end of the long point frog. Elastic supports are set at the heel end of the short point frog and the fork tip rail. Lateral displacement loads are set at the traction point.

[0020] The method for determining key values ​​of a movable point frog according to the present invention, as a preferred embodiment, further includes step S13 after step S12. Step S13 specifically involves determining key component data based on the optimal alignment of the movable point frog.

[0021] The method for determining key values ​​of a movable point frog according to the present invention, in a preferred embodiment, includes a long point frog, a short point frog, and a wing rail as key components.

[0022] The method for determining key values ​​of a movable point frog according to the present invention, as a preferred embodiment, involves determining the data for the long point frog as follows:

[0023] Based on the optimal alignment of the movable point frog, the length of the close-fitting section of the long point frog or the close-fitting section of the wing rail and the lateral displacement of the long point frog within the close-fitting section are determined. The alignment of the non-working side of the long point frog under the straight-rail opening state is obtained by superimposing the working side of the curved upper strand with the lateral displacement of the long point frog.

[0024] The method for determining key values ​​of a movable point frog according to the present invention, as a preferred embodiment, involves determining the data for the short point frog as follows:

[0025] Based on the optimal alignment of the movable point frog, the lateral displacement from the tip of the short point frog to the bending point at the rear end of the short point frog is determined. The alignment of the working edge from the tip of the short point frog to the bending point at the rear end is calculated by superimposing the working edge of the curved upper strand with the lateral displacement, under the condition of the straight strand being open.

[0026] The method for determining key values ​​of a movable center rail frog according to the present invention, as a preferred embodiment, includes a method for determining the data of the straight wing rail and a method for determining the data of the side wing rail.

[0027] The method for determining the data for the straight-strut wing rail is as follows:

[0028] The working edge profile of the supporting wheel section adopts the straight lower track working edge; the working edge profile of the closely attached section adopts the long core rail non-working edge profile when the straight track is open; the working edge profile of the top iron installation section is obtained by offsetting the short core rail working edge profile when the straight track is open; the profile of the spacer iron installation section is obtained by offsetting the fork and point rail working edges.

[0029] The method for determining the data of the side rail is as follows: the working edge profile of the supporting wheel section is the working edge profile of the curved upper rail; the working edge profile of the close-fitting section adopts the displacement curve of the working edge of the straight lower rail; the working edge profile of the top iron installation section is obtained by offsetting the displacement curve of the working edge of the straight lower rail; the profile of the rail installation spacer section is obtained by offsetting the working edge of the straight lower rail.

[0030] The beneficial effects of this invention are as follows:

[0031] This technical solution provides an overall numerical determination method consisting of three parts: a method for establishing a conversion model of the point rail, an iterative calculation method for the movable point rail frog line type, and a method for determining the numerical values ​​of key components. Compared with existing methods, the method of this invention is closer to the actual working conditions, which can make the movable point rail frog structure more accurate, the fit between various components more precise, and the frog structure more reasonable. Attached Figure Description

[0032] Figure 1 A flowchart illustrating a method for determining key numerical values ​​of a movable center rail frog. Detailed Implementation

[0033] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present invention. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments.

[0034] Example 1

[0035] like Figure 1 As shown, a method for determining key numerical values ​​of a movable point frog is proposed. A calculation model for point frog conversion is established based on finite element theory. The long and short points frogs are simulated using solid elements with a density of 7850 kg / m³. 3 The elastic modulus is taken as 2.1 × 10⁻⁶. 11 Pa, Poisson's ratio is taken as 0.3; full constraint is applied to the fixed end of the long core rail; the rotation angle of the short core rail is constrained, allowing it to slide only along the contact surface with the fork and the tip rail; lateral displacement loads corresponding to the stroke of the traction point are applied at the first and second traction points respectively; frictional contact is set between the long and short core rails and the slide plate, and the friction coefficient is taken as 0.25; coupling constraint is set on the close-fitting section of the long and short core rail heads to restrict the displacement of the two along the tangential and normal directions of the contact surface; the stiffness of the buckle plate and top iron support is taken as 100kN / mm.

[0036] The calculated displacement curves obtained from the solution model deviate from the design displacement curves. The maximum displacement deviation in the movable region of the long frog rail (from the tip of the long frog rail to the fixed end) is 6.64 mm, located at the center of the elastic bendable structure, and the calculated displacement is greater than the existing design displacement. The maximum displacement deviation in the frog rail / wing rail close-fitting section is 1.06 mm, located at the end of the close-fitting section, and the calculated displacement is greater than the design displacement; the displacement deviation at the tip of the frog rail is 0.36 mm, and the calculated displacement is less than the design displacement.

[0037] The minimum flange groove width obtained from the model solution is 90.7 mm, while the average minimum flange groove width of the five sets of frogs measured in the actual test is 90.9 mm, with little difference between the two. However, compared with the minimum flange groove width limit of 73 mm for the movable point rail frog area (the sum of the maximum gauge tolerance + 8 mm and 65 mm), the safety margin is too large.

[0038] The calculation results show that when the existing design method is used, the frog cannot be switched to a position where it is completely in contact with the wing rail; the safety margin of the minimum wheel flange groove width of the frog is too large and can be appropriately reduced to reduce the switching force at the traction point.

[0039] Based on the established center rail conversion model and the above calculation results, the center rail conversion displacement curve of the No. 18 movable center rail frog is optimized.

[0040] First, the minimum flange groove width of the turnout determined by the frog displacement curve must meet the requirements. Based on the given minimum flange groove width limit (73mm), considering a safety margin of 3mm, it is more reasonable to set the target value of the minimum flange groove width at 76mm.

[0041] Secondly, among the key structural parameters of the turnout, the second traction point stroke has the most significant impact on the minimum flange groove width, and the two are positively correlated. Therefore, it is proposed to change the point-of-flight transition displacement curve by reducing the second traction point stroke, so that the calculated value of the minimum flange groove width is reduced to the target value. As mentioned earlier, changing the point-of-flight transition displacement curve changes the key structural parameters of the point-of-flight transition model. However, under the condition that the second traction point stroke value is the same, the change in the model's key structural parameters will, in turn, affect the point-of-flight transition displacement curve. Therefore, a successive approximation method is used for solution. Specifically, the second traction point stroke of the established point-of-flight transition model is reduced to reduce the minimum flange groove width to the target value. The calculation model is then corrected using the key structural parameters determined by the calculated displacement curve. A verification calculation is performed under the condition that the second traction point stroke value remains unchanged. The calculation is terminated when the minimum flange groove width meets the requirement (the deviation between the calculated value and the verification value ≤ 0.2 mm). If it does not meet the requirement, the above adjustment, correction, and verification calculation process is repeated until the requirement is met.

[0042] Based on this, the design calculation conditions are shown in the table below.

[0043] Numerical calculation working condition

[0044]

[0045] The minimum flange groove width for different working conditions is shown in the table below. The safety margin for the minimum flange groove width in working condition 2 is still too large, while the minimum flange groove width in working condition 3 is close to the target value. Working condition 3 is selected for the next calculation.

[0046] Minimum flange groove width for operating conditions 1-3

[0047]

[0048] Based on the key structural parameters obtained from the displacement curve calculated under working condition 3, a modified model 1 was established, and working condition 4 was added for supplementary calculation, and the calculation was performed again.

[0049] Key structural parameters of the initial model and the modified model 1

[0050]

[0051] Numerical calculation working condition 4

[0052]

[0053] The calculation results of the minimum flange groove width for working condition 4 are shown in the table below. Compared with working condition 3, the deviation of the calculation results of the minimum flange groove width reaches 2.7mm, which is less than the limit requirement.

[0054] Minimum rim groove width for operating condition 4

[0055]

[0056] The second traction point stroke of the modified model 1 was adjusted to 50mm, and calculations were performed for supplementary working condition 5.

[0057] Numerical calculation case 5

[0058]

[0059] The calculation results for the minimum flange groove width under working condition 5 are shown in the table below, and the minimum flange groove width meets the requirements.

[0060] Minimum rim groove width for operating condition 5

[0061]

[0062] Based on the key structural parameters obtained from the displacement curve calculated under working condition 5, a modified model 2 was established, and working condition 6 was added for supplementary calculation, and the calculation was performed again.

[0063] Key structural parameters of modified model 1 and modified model 2

[0064]

[0065] Numerical calculation case 6

[0066]

[0067] The calculated results of the minimum flange groove width for working condition 6 are shown in the table below. Compared with working condition 5, the deviation of the minimum flange groove width is 0.1mm (≤0.2mm), and it is 0.2mm larger than the target value, which meets the requirements. At this point, the iterative simulation ends, and the traction stroke and calculated displacement curve for working condition 6 are the final optimization results.

[0068] Minimum rim groove width for operating condition 6

[0069]

[0070] The key structural parameters obtained from the displacement curve calculated using working condition 6 are compared with the key structural parameter values ​​of the modified model 2, and the differences between the two are minimal.

[0071] Comparison of key structural parameters

[0072]

[0073] In addition, the calculated displacement difference between the long and short core rails in working condition 6 shows that within 2.4m from the tip of the short core rail, the displacements of the long and short core rails are basically the same; within 2.4m to 5.4m from the tip, the displacement of the long core rail gradually becomes greater than that of the short core rail, with the maximum displacement difference being 1.02mm, which occurs at 5.4m from the tip of the short core rail; from 5.4m from the tip of the short core rail to the fixed end of the long core rail, the displacement difference gradually decreases to 0.

[0074] In summary, the minimum flange groove width is used as the key parameter for determining the displacement curve of the frog. Based on the established frog conversion model, a successive approximation method is used for solving the problem. The minimum flange groove width in working condition 6 meets the requirements; therefore, the displacement curve calculated in working condition 6 is selected as the optimized design scheme for the frog conversion displacement curve of the No. 18 movable frog. Furthermore, there is a displacement difference of up to 1.02 mm between the long and short frogs, which should be considered in the structural design.

[0075] Further, design methods for key components of movable point frogs:

[0076] After the frog's displacement curve is determined, the structural design of key components is carried out. Compared with the lateral direction, the vertical speed of the movable frog is higher (currently the highest speed for vertical frog crossing is 350km / h), and the requirements for the geometric tolerances of the frog in the vertical direction are also higher. Considering the above factors, the key components of the movable frog are designed for vertical operation.

[0077] (1) Long central track

[0078] The long point rail is a key component of the movable point rail frog. It is assembled with the short point rail to form the movable point rail. Under the traction of the switch machine, it is closely attached to different side rails to provide continuous support for the wheels. Determining the non-working side profile of the long point rail in the straight-running state is the key to the design of the long point rail.

[0079] The design method is as follows: Based on the displacement curve of the straight working side and the working side of the center rail calculated above, the length of the close-fitting section of the long center rail / wing rail (from the theoretical tip of the center rail to the 71.3mm cross-section) and the lateral displacement Δy of the long center rail within the close-fitting section can be determined. c (x c ), where x c Let Δy be the longitudinal coordinate of the frog along the long track when it is open in a straight direction. cThe lateral displacement of the long center rail at different longitudinal positions is represented. The closely fitted section of the long center rail / wing rail is discretized along the longitudinal direction of the track into n segments, with a total of n+1 nodes. The coordinates of each node are x and y. c1 x c2 x c3 ... x cn+1 The corresponding lateral displacements are Δy c (x c1 ), Δy c (x c2 ), Δy c (x c3 ), ..., Δy c (x cn+1 Using the same method, the working edges of the side rails within the close-fitting section of the long center rail / wing rail are discretized, and the lateral coordinates y of each node of the working edge of the side rail can be obtained. c (x c1 ), y c (x c2 ), y c (x c3 ), ..., y c (x cn+1 For each discrete node P ci (i = 1, 2, 3, ..., n+1), respectively based on the coordinates y of its side working edge. c (x ci ) and the converted lateral displacement Δy c (x ci The lateral coordinates y of each node on the non-working side of the long center track under the straight track opening state are obtained by superposition calculation. zc (x ci ).

[0080] y zc (x ci )=y c (x ci )-Δy c (x ci ), i = 1, 2, 3, ..., n+1

[0081] Based on the straight-line open state, the coordinates (x) of each node on the non-working side of the long-center track are... ci ,y zc (x ci By fitting each node with a spline curve, the non-working side profile of the long center rail under the straight-line opening state is obtained.

[0082] The design methods for other structures of the long central track can refer to existing design methods.

[0083] (2) Short center rail

[0084] The short and long mandrels are assembled as a whole via connecting parts. The tip of the short mandrel to its 72.2mm cross-section is in close contact with the long mandrel; the rear bend point to its heel is in close contact with the fork tip rail. During conversion, the profile from the rear bend point to the heel remains unchanged. When the straight strand is in operation, the non-working edge of the section where the short and long mandrels are in close contact is a horizontal line. Determining the working edge profile from the tip of the short mandrel to the rear bend point in the straight strand operation state is the key to the design of the short mandrel.

[0085] Based on the displacement curve of the working edge of the short mandrel calculated above, the lateral displacement Δy from the tip of the short mandrel to the bending point at the rear end of the short mandrel can be determined. d (x d ), where x d Let Δy be the longitudinal coordinate of the short center rail along the track when the frog is open in the straight direction. d This represents the lateral displacement at different positions on the short track. Using the same discretization method as the long track, the short track from its tip to the rear bend point is discretized longitudinally into n segments, totaling n+1 nodes. The coordinates of each node are xi, xj, and xi, respectively. d1 x d2 x d3 ... x dn+1 The corresponding lateral displacements are Δy d (x d1 ), Δy d (x d2 ), Δy d (x d3 ), ..., Δy d (x dn+1 Discretizing the working edges of the side strands within the range corresponding to the tip of the short center rail to the rear bending point yields the lateral coordinate y of the working edge of the side strand at each node. d (x d1 ), y d (x d2 ), y d (x d3 ), ..., y d (x dn+1 For each discrete node P) di (i = 1, 2, 3, ..., n+1), respectively based on the coordinates y of its side working edge. d (x di ) and the converted lateral displacement Δy d (x di The lateral coordinates y of each node on the working side from the tip of the short guide rail to the rear bending point are obtained by superposition calculation under the straight-strut open state. zd (x di ).

[0086] y zd (x di )=y d (xdi )-Δy d (x di ), i = 1, 2, 3, ..., n+1

[0087] Based on the straight-line opening state, the coordinates (x) of each node on the working side of the short-rail system are as follows: di ,y zd (x di By fitting each node with a spline curve, the working edge shape of the short center rail under the straight-strut open state is obtained.

[0088] The design methods for other structures of the short-circuit guide can refer to existing design methods.

[0089] (3) Wing rail

[0090] The movable frog's wing rail is divided into straight wing rail and side wing rail. The wing rail that is in close contact with the frog when the frog is in straight position is called the straight wing rail, and the wing rail that is in close contact with the frog when the frog is in side position is called the side wing rail. According to different functions, the working edges of the wing rails are divided into: wheel support section, close contact section, connecting section, top iron mounting section, and spacer iron mounting section. Determining the working edges of each wing rail section is crucial to the wing rail design.

[0091] The design method for the working side of the straight track wing rail is as follows: the working side profile of the supporting wheel section adopts the working side profile of the straight track wing rail; in order to closely fit the center rail in the straight track open state, the working side profile of the closely fitted section adopts the non-working side profile of the long center rail in the straight track open state as described above; in order to reduce the specifications of the top iron, the working side profile of the top iron installation section is obtained by offsetting the working side profile of the short center rail in the straight track open state as described above; in order to simplify the spacer structure, the profile of the spacer installation section is obtained by offsetting the working side profile of the fork and switch rail (the working side profile of the fork and switch rail is determined by the overall profile of the turnout).

[0092] The design method for the working edge of the side rail is as follows: the working edge profile of the supporting wheel section is the working edge profile of the frog side rail; in order to closely fit the frog rail when the side rail is open, the working edge profile of the closely fitted section adopts the displacement curve calculated by the straight rail working edge described above; in order to reduce the specifications of the top iron, the working edge profile of the wing rail top iron installation section is obtained by offsetting the displacement curve calculated by the straight rail working edge; in order to simplify the spacer structure, the profile of the wing rail spacer installation section is obtained by offsetting the straight rail working edge.

[0093] Once the working edge is determined, the working edge of the connecting section should be adjusted according to the specific structure, and the positions of the bending points should be arranged reasonably to ensure that the bending angle of each bending point is uniform and facilitates production.

[0094] (4) Connecting components between long and short central rails

[0095] The core rail assembly consists of a long core rail, a short core rail, and connecting components (spacers, top rails, etc.) connected together by high-strength bolts.

[0096] Due to the displacement difference during the conversion between long and short core rails, the components that connect the long and short core rails into a whole should be located in areas where the displacement difference between the long and short core rails is small. The top iron located at the rear end of the core rail assembly has a smaller size when the straight strand is open than when the side strand is open due to the displacement difference during the conversion between the long and short core rails. To avoid affecting the straightness of the straight working edge, its size should be designed according to the straight strand opening. Therefore, when converting to the side strand, there is a gap between the top iron and the web of the long core rail.

[0097] The above description is only a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in the present invention, based on the technical solution and inventive concept of the present invention, should be covered within the scope of protection of the present invention.

Claims

1. A method for determining key numerical values ​​of a movable point frog, characterized in that: Includes the following steps: S1. Obtain the geometric features of the initial calculation model through the rigid body rotation method, and establish the orbital conversion calculation model based on the geometric features; S2. Add the minimum distance between turnout rails under standard gauge and the maximum allowable positive tolerance of gauge in the turnout area to obtain the minimum flange groove width convergence value C; S3, the calculation model for the conversion of the heart track is based on the existing dynamic path d. i The frog profile is obtained by solving the problem, and the corresponding minimum flange groove width t is calculated based on the frog profile. min ; S4. Determine whether the absolute value of the minimum flange groove width convergence value C and the calculated value tmin is less than the allowable deviation a. If yes, proceed to step S6; otherwise, proceed to step S5. S5. Determine the calculated value t of the minimum rim groove width. min If the minimum rim groove width convergence value C is greater than the minimum rim groove width, then reduce the dynamic stroke d. i After adjusting the value, calculate the minimum flange groove width t corresponding to the turnout profile. min Then proceed to step S4; otherwise, increase the stroke d. i After adjusting the value, calculate the minimum flange groove width t corresponding to the turnout profile. min Then proceed to step S4; S6. Based on the calculated frog line shape, calculate the geometric characteristic parameter values ​​of the long and short center tracks, and update the center track conversion calculation model using the geometric characteristic parameter values. S7. Based on the updated orbital conversion calculation model, and using the traction point stroke d... i The initial frog profile is obtained by solving the problem, and the calculated value of the minimum flange groove width corresponding to the frog profile is obtained. tmin(i+1) ; S8. Determine the convergence value C of the minimum rim groove width and the calculated value t of the minimum rim groove width. min(i+1) If the absolute value is less than the allowable deviation a, proceed to step S10. Otherwise, proceed to step S9; S9. Determine the calculated value t of the minimum rim groove width. min(i+1) If the minimum rim groove width convergence value C is greater than the minimum rim groove width, then reduce the dynamic stroke d. i After adjusting the numerical value, the minimum flange groove width t corresponding to the frog line calculation type is calculated. min(i+1) Then proceed to step S4; otherwise, increase the stroke d. i After adjusting the value, calculate the minimum flange groove width t corresponding to the turnout profile. min(i+1) Then proceed to step S4; S10. Determine the conversion force F at each traction point of the track. i Is the rated switching force F of the switch machine at each traction point being output? is Minimum conversion force F when used with switch machines at each traction point ismin If the condition is between, then proceed to step S12; Otherwise, proceed to step S11; S11. Determine the conversion force F at each traction point of the track. i The rated conversion force F output by the switch machine at each traction point is Minimum switching force F at each traction point switch machine ismin The numerical relationship between them, if the conversion force F at each traction point i The output rated switching force F of the switch machine at each traction point is greater than the rated switching force F. is Then, after increasing the width of the fork throat, proceed to step S1; if the conversion force F at each traction point... i Less than the minimum switching force F required for each traction point switch machine ismin Then reduce the width of the turnout throat and proceed to step S1; S12. Output the current frog alignment as the optimal alignment for a movable point frog.

2. The method for determining key values ​​of a movable point frog according to claim 1, characterized in that: In the calculation model for the conversion of the core rail, both the long core rail and the short core rail are simulated using solid models. The close contact area of ​​the long core rail head and the close contact area of ​​the short core rail head are set with coupling constraints. Frictional contact is set between the long core rail and the slide plate, and between the short core rail and the slide plate. The fixed end of the long core rail is set with full constraints. Elastic supports are set at the heel end of the short core rail and the fork tip rail. Lateral displacement load is set at the traction point.

3. The method for determining key values ​​of a movable point frog according to claim 1, characterized in that: The method for determining key values ​​of the movable point frog also includes step S13 after step S12. Step S13 specifically involves determining key component data based on the optimal alignment of the movable point frog.

4. The method for determining key values ​​of a movable point frog according to claim 3, characterized in that: The key components include the long center rail, the short center rail, and the wing rail.

5. The method for determining key values ​​of a movable point frog according to claim 4, characterized in that: The method for determining the data of the long central track is as follows: Based on the optimal alignment of the movable point rail frog, the length of the close-fitting section of the long point rail or the close-fitting section of the wing rail and the lateral displacement of the long point rail within the close-fitting section are determined. The alignment of the non-working side of the long point rail in the straight-rail open state is obtained by superimposing the working side of the curved upper strand with the lateral displacement of the long point rail.

6. The method for determining key values ​​of a movable point frog according to claim 4, characterized in that: The method for determining the data of the short-track is as follows: Based on the optimal alignment of the movable point rail frog, the lateral displacement from the tip of the short point rail to the bending point at the rear end of the short point rail is determined; the alignment of the working edge from the tip of the short point rail to the bending point at the rear end of the short point rail in the straight rail open state is calculated by superimposing the lateral displacement with the working edge of the curved upper rail.

7. The method for determining key numerical values ​​of a movable point frog according to claim 4, characterized in that: The data determination method for the wing rails includes a data determination method for the straight wing rail and a data determination method for the lateral wing rail; The method for determining the data for the straight-strut wing rail is as follows: The working edge profile of the supporting wheel section adopts the straight lower track working edge; the working edge profile of the close-fitting section adopts the non-working edge profile of the long core rail when the straight track is open; the working edge profile of the top iron installation section is obtained by offsetting the working edge profile of the short core rail when the straight track is open; the profile of the spacer iron installation section is obtained by offsetting the working edge profile of the fork and point rail. The method for determining the data of the side rail is as follows: the working edge profile of the supporting wheel section is the working edge profile of the curved upper rail; the working edge profile of the close-fitting section adopts the displacement curve of the working edge of the straight lower rail; the working edge profile of the top iron installation section is obtained by offsetting the displacement curve of the working edge of the straight lower rail; the profile of the rail installation spacer section is obtained by offsetting the working edge of the straight lower rail.

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