Motor vehicle axle end double-blade sealing device and axle end sealing design method

Abstract

The invention belongs to the technical field of gearbox shaft end sealing, and particularly relates to a motor vehicle shaft end double-blade sealing device and a shaft end sealing design method.The method comprises the following steps that S1, working condition parameters are determined; s2, designing a double-blade impeller; s3, designing a sealing structure; and S4, outputting a design result. The sealing effect is good, the double-blade impeller and the staggered labyrinth seal are combined, and the sealing performance of the shaft end of the gearbox is effectively improved; the operation and maintenance cost is reduced, and the operation and maintenance interval can be effectively prolonged and the operation and maintenance investment is reduced; the reliability is high, a non-contact sealing mode is adopted completely, and the reliability of the double-blade impeller structure is high; and the design and three-dimensional modeling work of the shaft end sealing device can be automatically completed according to the determined environmental parameters and boundary dimension requirements, and a user can complete the design adjustment work of the shaft end sealing device through one key based on reliability redundancy.

Description

Technical Field

[0001] The invention belongs to the technical field of gearbox shaft end seals, and in particular relates to a motor vehicle shaft end double-blade seal device and a shaft end seal design method. Background Art

[0002] As the speed of high-speed trains continues to increase, the line radiation range continues to expand, and the operating conditions are becoming more and more complex. This puts higher requirements on the sealing performance of the gearbox, an important component of the power system. When the train passes through complex terrain such as tunnels at high speed, affected by factors such as piston wind, there is lubricating oil leakage in the shaft end seal of the train gearbox. The current gearbox shaft end sealing structure mainly adopts a combination of contact seals and labyrinth seals. However, as the speed of the train increases further, the frequency of replacement of the contact seals continues to increase, increasing the operation and maintenance cost of the gearbox. Another sealing method combines an oil thrower ring with a labyrinth seal. Although this structure adopts non-contact sealing, its sealing effect needs to be improved.

[0003] Therefore, it is necessary to design a double-vane sealing device at the axle end of a motor vehicle and an axle end sealing design method to solve the above problems. Summary of the invention

[0004] The purpose of the present invention is to provide a double-vane sealing device for the axle end of a motor vehicle and a method for designing an axle end seal to solve the above-mentioned problems and achieve the purpose of meeting the axle end sealing performance requirements of high-speed trains.

[0005] To achieve the above object, the present invention provides the following solution: a double-vane sealing device at the axle end of a motor vehicle and a design method for the axle end seal, comprising the following steps:

[0006] S1. Determine the operating parameters, design a database model based on the operating parameters of the shaft end seal structure and the impeller parameters, determine the turbulence dissipation intensity of the double-blade impeller, the turbulence dissipation requirements on both sides of the double-blade impeller, and the geometric dimensions of the seal structure;

[0007] S2. Design of double-blade impeller: design the thickness, outer diameter and interference fit parameters of the double-blade impeller with the transmission shaft according to the turbulence dissipation intensity of the double-blade impeller and the turbulence dissipation requirements on both sides of the double-blade impeller;

[0008] S3. Design of sealing structure: design of sealing cavity width, sealing cavity height and staggered depth according to the geometric dimensions of the sealing structure;

[0009] S4. Output the design results.

[0010] Based on the double-blade sealing device at the axle end of a motor vehicle and the axle end sealing design method of the present invention, S2 includes a tail guide blade design, a middle spiral twisted blade design, and an outlet side blade adjustment.

[0011] Based on the double-blade sealing device and shaft end sealing design method of a motor vehicle axle end of the present invention, when designing the tail guide vane, the data in the flow field reflow condition on the bearing side of the double-blade impeller and the blade structure parameter relationship model are combined.

[0012] Based on the double-blade sealing device at the axle end of a motor vehicle and the axle end sealing design method of the present invention, the structural parameters of the top diverter blade and the tail guide blade are combined when designing the middle spiral twisted blade.

[0013] Based on the double-vane sealing device at the axle end of a motor vehicle and the axle end sealing design method of the present invention, when adjusting the outlet side blades, the tail guide vane structure in the outlet side blades is adjusted in combination with the sealing structure and the center position of the outlet side vortex.

[0014] Based on the double-blade sealing device at the axle end of a motor vehicle and the axle end seal design method of the present invention, when designing the sealing structure, the parameters of the sealing cavity width, sealing cavity height and staggered depth in the staggered labyrinth sealing mechanism are designed according to the geometric outer dimensions of the axle end seal and the turbulent dissipation intensity, with reference to the data in the relationship model.

[0015] Based on the double-blade sealing device and shaft end sealing design method of a motor vehicle axle end of the present invention, redundancy adjustment is performed after the sealing structure design is completed, the redundancy parameter is 1.2, and the structural parameter adjustment of the double-blade impeller is completed according to the adjusted redundancy.

[0016] Based on a double-blade sealing device at the axle end of a motor vehicle and a design method for an axle end seal of the present invention, when outputting the design results, a secondary development module of a parametric model file of Creo software is used to complete the three-dimensional parametric modeling of the axle end seal using the determined axle end seal structure design parameters, and output the three-dimensional model corresponding to all the designed model structure parameters and thresholds.

[0017] Compared with the prior art, the present invention has the following advantages and technical effects:

[0018] 1. Excellent sealing performance. The combination of a double-blade impeller structure and an interlaced labyrinth seal can effectively improve the shaft end sealing performance of high-speed train gearboxes. Based on the results of fluid analysis, it is found that the device has good performance in parameters such as turbulent eddy dissipation capacity and key plane lubricating oil leakage mass flow rate, which can meet the shaft end sealing performance requirements of continuously increasing train speeds;

[0019] 2. High structural reliability. The shaft end sealing structure of high-speed trains all adopts non-contact sealing. The double-blade impeller can effectively resist the interaction of fluids inside and outside the gearbox and prevent lubricating oil leakage caused by the large pressure difference inside and outside the gearbox. This device can effectively extend the maintenance interval of the shaft end of the train gearbox and achieve the goal of increasing the cost and efficiency of vehicle operation and maintenance.

[0020] 3. Rapid design of sealing structure. Based on basic data such as operating parameters and the shaft end sealing structure database, the design and 3D modeling of the shaft end sealing structure of high-speed trains, including double-blade impellers and staggered labyrinth sealing structures, can be automatically completed. The one-button shaft end sealing structure design parameter adjustment function can also be realized based on reliability redundancy parameters. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments are briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative labor:

[0022] Figure 1 It is a flow chart of the present invention;

[0023] Figure 2 A schematic diagram of a device designed according to the method of the present invention;

[0024] Figure 3 A schematic diagram of a double-blade impeller of the present invention;

[0025] Figure 4 for Figure 3 A cross-sectional view of

[0026] Figure 5 The figure is a relationship diagram between the number of blades of the device of the present invention and the maximum value of the impeller turbulent vortex dissipation and the mass flow rate of the lubricating oil leakage at the outlet;

[0027] Figure 6 This is a cloud diagram of turbulent vortex dissipation on the bearing side of a double-blade impeller with different numbers of blades according to the present invention.

[0028] Among them, 1. Bearing end cover; 2. Double-blade impeller; 3. Staggered labyrinth sealing ring; 4. Spring retaining ring 1; 5. Spring retaining ring 2; 6. Box body; 7. Cylindrical roller bearing; 8. Transmission shaft. DETAILED DESCRIPTION

[0029] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0030] In order to make the above-mentioned objects, features and advantages of the present invention more obvious and easy to understand, the present invention is further described in detail below with reference to the accompanying drawings and specific embodiments.

[0031] Reference Figures 1 to 6 As shown, the present invention provides a motor vehicle axle end double blade sealing device and an axle end sealing design method, comprising the following steps:

[0032] S1. Determine the operating parameters. Based on the operating parameters of the shaft end seal structure and referring to the relevant empirical relationship model in the impeller parameter design database, determine the design objectives such as the turbulence dissipation intensity range that the double-blade impeller in the shaft end seal structure needs to achieve, the turbulence dissipation requirements on both sides of the impeller, and the minimum geometric external dimensions of the overall seal structure;

[0033] S2. Design of double-blade impeller: refer to the determined design goals, determine the relevant parameters of impeller thickness, outer diameter, and interference fit with the transmission shaft, determine the effective gap of the blades based on the requirements of the shunt strength in the middle of the blades, and realize the design of the triangular top shunt blades;

[0034] S3. Design of sealing structure: design of sealing cavity width, sealing cavity height and staggered depth according to the geometric dimensions of the sealing structure;

[0035] S4. Output the design results.

[0036] Furthermore, S2 includes a tail guide vane design, a middle spiral twisted blade design, and an outlet side blade adjustment.

[0037] Furthermore, when designing the tail guide vane, the backflow condition requirements of the impeller bearing side flow field are combined and the tail guide vane design is completed by referring to the data in the blade structure parameter relationship model.

[0038] Furthermore, when designing the middle spiral twisted blade, since the three-stage blades all adopt a transition streamlined design, the design of the middle spiral twisted transition blade can be completed based on the structural parameters such as the top diverter blade and the tail guide blade.

[0039] Furthermore, when adjusting the outlet side blades, the tail guide vane structure of the outlet side blades is optimized in consideration of the coordination with the staggered labyrinth seal structure and the adjustment of the center position of the outlet side vortex.

[0040] Furthermore, when designing the sealing structure, the design of parameters such as the sealing cavity width, height, and staggered depth in the staggered labyrinth sealing structure is completed based on the minimum geometric outer dimensions of the shaft end seal and the turbulence dissipation intensity, with reference to the data in the relationship model.

[0041] Furthermore, redundancy is adjusted after the sealing structure design is completed. The default structural reliability redundancy in the relational model is 1.2. Users can adjust the parameters of all structures of the double-blade impeller according to the external dimension range of the shaft end sealing structure and related reliability requirements. The relational model will automatically complete the adjustment of the parameters of all structures of the double-blade impeller according to the adjusted redundancy.

[0042] Furthermore, when outputting the design results, the parametric model file secondary development module of the Creo software is used to complete the three-dimensional parametric modeling of the shaft end seal using the determined shaft end seal structure design parameters, and output the three-dimensional model corresponding to all the designed model structure parameters and thresholds.

[0043] The sealing device designed based on the design method of the present invention includes a bearing end cover 1, a double-blade impeller 2, an interlaced labyrinth seal ring 3, a spring retaining ring 1 4, a spring retaining ring 2 5, a housing 6, a cylindrical roller bearing 7 and a transmission shaft 8. The transmission shaft 8 is fitted with a cylindrical roller bearing 7 by interference fit, and is also fitted with a double-blade impeller 2 and a spring retaining ring 2 5 in sequence; an interlaced labyrinth seal ring 3 is fitted on the outer side of the double-blade impeller 2 by interference fit, and is axially fixed by a spring retaining ring 1 4. The blades in the double-blade impeller 2 adopt a symmetrical structure to ensure that the double-blade impeller 2 can ensure the sealing effect when rotating in both directions with the transmission shaft 8. The blades are composed of a three-stage structure, specifically including a triangular splitter blade top, a spiral twisted transition blade in the middle, and a trapezoidal guide blade at the tail. The side of the double-blade impeller 2 close to the cylindrical roller bearing 7 requires a relatively high turbulent eddy dissipation intensity, so the three-stage blade size there is relatively large, and the turbulent eddy dissipation intensity of the blade close to the outlet side is relatively low, so the blade size can be reduced, and an interlaced labyrinth sealing ring 3 is arranged inside the blade to reduce the outer size of the shaft end sealing device. Since the interlaced labyrinth sealing ring 3 and the bearing end cover 1 form an interlaced labyrinth sealing structure, the shaft end sealing performance of the gearbox is further improved. When the double-blade impeller 2 rotates synchronously in both directions with the transmission shaft 8, the blades stir the mixed fluid inside the bearing end cover 1, forming a fluid flow trend toward both sides of the impeller in the middle of the impeller, effectively preventing the lubricating oil inside the gearbox from flowing out from the cylindrical roller bearing 7, and also inhibiting the fluid outside the gearbox from flowing into the gearbox through the labyrinth sealing structure.

[0044] Reference Figure 5 As shown in the figure, the maximum turbulent eddy dissipation intensity of the double-blade impeller close to the bearing side plane and the mass flow rate of lubricating oil leakage at the outlet of the sealing device under different blade numbers in the fluid simulation result data can be clearly seen. When the number of impeller blades is 2, the sealing performance of the shaft end sealing device of the high-speed train gearbox is the best.

[0045] Reference Figure 6 As shown in the figure, the turbulent vortex dissipation cloud diagram can also prove that when a double-blade impeller structure is adopted, the turbulent vortex dissipation intensity of the impeller close to the bearing side plane is the largest and the shaft end sealing effect is the best.

[0046] In the description of the present invention, it should be understood that the terms "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside" and "outside" etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present invention.

[0047] The embodiments described above are only descriptions of the preferred embodiments of the present invention, and are not intended to limit the scope of the present invention. Without departing from the design spirit of the present invention, various modifications and improvements made to the technical solutions of the present invention by ordinary technicians in this field should fall within the protection scope of the present invention.

Claims

1. A double-blade sealing device for axle end of a motor vehicle and a design method for axle end sealing, characterized in that: The following steps are involved: S1. Determine the operating parameters, design a database model based on the operating parameters of the shaft end seal structure and the impeller parameters, determine the turbulence dissipation intensity of the double-blade impeller, the turbulence dissipation requirements on both sides of the double-blade impeller, and the geometric dimensions of the seal structure; S2. Design of double-blade impeller: design the thickness, outer diameter and interference fit parameters of the double-blade impeller with the transmission shaft according to the turbulence dissipation intensity of the double-blade impeller and the turbulence dissipation requirements on both sides of the double-blade impeller; S3. Design of sealing structure: design of sealing cavity width, sealing cavity height and staggered depth according to the geometric dimensions of the sealing structure; S4. Output the design results.

2. A motor vehicle axle end double blade sealing device and axle end sealing design method according to claim 1, characterized in that: S2 includes the tail guide vane design, the middle spiral twisted blade design, and the outlet side blade adjustment.

3. A motor vehicle axle end double blade sealing device and axle end sealing design method according to claim 2, characterized in that: When designing the tail guide vane, the data in the flow field reflow conditions on the bearing side of the double-blade impeller and the blade structural parameter relationship model are combined.

4. A motor vehicle axle end double blade sealing device and axle end sealing design method according to claim 2, characterized in that: When designing the middle spiral twisted blade, the structural parameters of the top diverter blade and the tail guide blade are combined.

5. A motor vehicle axle end double blade sealing device and axle end sealing design method according to claim 2, characterized in that: When adjusting the outlet side blades, the tail guide vane structure of the outlet side blades is adjusted in combination with the sealing structure and the center position of the outlet side vortex.

6. A motor vehicle axle end double blade sealing device and axle end sealing design method according to claim 1, characterized in that: When designing the sealing structure, the parameters of the sealing cavity width, sealing cavity height and staggered depth in the staggered labyrinth sealing mechanism are designed based on the geometric outer dimensions of the shaft end seal and the turbulence dissipation intensity, with reference to the data in the relationship model.

7. A motor vehicle axle end double blade seal device and axle end seal design method according to claim 1, characterized in that: After the sealing structure design is completed, the redundancy is adjusted, and the redundancy parameter is 1.

2. The structural parameter adjustment of the double-blade impeller is completed according to the adjusted redundancy.

8. The double-vane seal device at the axle end of a motor vehicle and the axle end seal design method according to claim 1, characterized in that: When outputting the design results, based on the parametric model file secondary development module of Creo software, the determined shaft end seal structure design parameters are used to complete the three-dimensional parametric modeling of the shaft end seal, and the three-dimensional model corresponding to all the designed model structure parameters and thresholds is output.

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