A double-vane sealing device for axle end of a motor vehicle and axle end sealing design method

Abstract

The present invention belongs to the technical field of gearbox shaft end seals, and in particular relates to a double-blade seal device for the shaft end of a motor vehicle and a shaft end seal design method, comprising the following steps: S1, determining operating parameters; S2, designing a double-blade impeller; S3, designing a sealing structure; and S4, outputting the design results. The present invention has a good sealing effect, combining a double-blade impeller with an interlaced labyrinth seal to effectively improve the gearbox shaft end sealing performance; reduces operation and maintenance costs, and the structure can effectively extend the operation and maintenance interval and reduce operation and maintenance investment; has high reliability, and adopts a non-contact sealing form throughout, with a double-blade impeller structure having high reliability; and can automatically complete the design and three-dimensional modeling of the shaft end seal device based on the specified environmental parameters and external dimensions. The user can complete the design and adjustment of the shaft end seal device with one click based on reliability redundancy.

Description

Technical Field

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

[0002] As high-speed trains continue to increase in speed, the coverage of their lines continues to expand, and operating conditions are becoming increasingly complex. This places higher demands on the sealing performance of gearboxes, a key component of the power system. When trains pass through complex terrain such as tunnels at high speed, lubricating oil leaks from the shaft-end seals of the train gearboxes due to factors such as piston wind. Current gearbox shaft-end sealing structures primarily utilize a combination of contact seals and labyrinth seals. However, this structure suffers from the problem that as train speeds continue to increase, the frequency of contact seal replacement increases, increasing the operating and maintenance costs of the gearboxes. Another sealing method combines an oil slinger with a labyrinth seal. Although this structure utilizes non-contact sealing, its sealing effectiveness 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 shaft end sealing design method to solve the above problems and achieve the purpose of meeting the axle end sealing performance requirements of high-speed trains.

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

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

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

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

[0009] S4. Output the design results.

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

[0011] Based on the double-vane sealing device and the shaft end sealing design method of the 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-vane impeller and the blade structure parameter relationship model are combined.

[0012] In the invention, a double-vane sealing device for a motor vehicle axle end and a shaft end sealing design method are provided. When designing the middle spirally twisted blades, the structural parameters of the top diverter blades and the tail guide blades are combined.

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

[0014] Based on the double-vane sealing device and shaft end seal design method of a motor vehicle axle end 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 shaft 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 the double-vane sealing device and shaft end seal design method of a motor vehicle axle end, when outputting the design results, the parametric model file secondary development module of 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.

[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 dual-blade impeller structure and an interlaced labyrinth seal effectively improves the shaft-end sealing performance of high-speed train gearboxes. Fluid analysis results show that the device's turbulent eddy dissipation capacity and key plane lubricant leakage mass flow rate perform well, meeting the shaft-end sealing performance requirements of increasingly fast trains.

[0019] 2. High structural reliability. High-speed train shaft-end seals utilize a non-contact seal design. The dual-blade impeller effectively prevents fluid interaction between the gearbox and the outside, preventing lubricant leakage caused by large pressure differentials inside and outside the gearbox. This device effectively extends maintenance intervals for train gearbox shaft ends, achieving the goal of increasing vehicle operation and maintenance costs and efficiency.

[0020] 3. Rapid seal structure design. Based on basic data such as operating parameters and a database of shaft-end seal structures, the system automatically completes the design and 3D modeling of high-speed train shaft-end seals, including dual-blade impellers and staggered labyrinth seals. It also enables one-click adjustment of shaft-end seal design parameters 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 following briefly introduces the drawings required for use in the embodiments. Obviously, the drawings described below are only some embodiments of the present invention. Those skilled in the art can also derive other drawings based on these drawings without inventive work.

[0022] Figure 1 Flowchart of the present invention;

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

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

[0025] Figure 4 for Figure 3 sectional view of

[0026] Figure 5 This is a graph showing the relationship between the number of blades of the device of the present invention and the maximum value of the impeller turbulent eddy 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 seal ring; 4. Spring retaining ring 1; 5. Spring retaining ring 2; 6. Box body; 7. Cylindrical roller bearing; 8. Drive shaft. DETAILED DESCRIPTION

[0029] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. All other embodiments obtained by ordinary technicians in this field based on the embodiments of the present invention without making any creative efforts shall fall 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-vane sealing device and an axle end seal 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 two-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 the two-blade impeller: Refer to the established design goals to determine the impeller thickness, outer diameter, and relevant parameters of the interference fit with the drive shaft. Based on the requirements for the mid-blade split flow strength, determine the effective blade clearance and implement the triangular top split flow blade design.

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

[0035] S4. Output the design results.

[0036] Furthermore, S2 includes tail guide vane design, middle spiral twisted blade design, and 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 with the data in the blade structure parameter relationship model to complete the design of the tail guide vane.

[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 outlet side vortex center position.

[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 external dimensions of the shaft end seal and the turbulent 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 two-blade impeller based on 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 two-blade impeller according to the adjusted redundancy.

[0042] Furthermore, when outputting the design results, the parametric model file secondary development module of 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 sealing 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 sealing ring 3 is fitted on the outside 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 maintain a 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 at the top, a spirally twisted transition blade in the middle, and a trapezoidal guide blade at the tail. The turbulent eddy dissipation intensity is required to be relatively high on the side of the two-blade impeller 2 close to the cylindrical roller bearing 7, so the three-stage blade size at this location 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 external 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 gearbox shaft end sealing performance is further improved. When the two-blade impeller 2 rotates synchronously with the drive shaft 8 in both directions, 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 of 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 can be clearly seen in the fluid simulation result data. 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", "transverse", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating the orientation or position relationship, are based on the orientation or position relationship shown in the accompanying drawings, and are only for the convenience of describing the present invention, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0047] The embodiments described above are merely descriptions of preferred embodiments of the present invention and are not intended to limit the scope of the present invention. Without departing from the 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 scope of protection of the present invention.

Claims

1. A double-vane 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. Based on the operating parameters of the shaft end seal structure and the impeller parameters, design a database model to determine the turbulence dissipation intensity of the two-blade impeller, the turbulence dissipation requirements on both sides of the two-blade impeller, and the geometric dimensions of the seal structure. S2. Design of the double-blade impeller: design the thickness, outer diameter, and interference fit parameters of the double-blade impeller with the drive shaft based on the turbulence dissipation intensity of the double-blade impeller and the turbulence dissipation requirements on both sides of the double-blade impeller; S3. Sealing structure design: design the sealing cavity width, sealing cavity height and staggered depth according to the sealing structure geometric dimensions; S4. Output design results; S2 includes tail guide vane design, middle spiral twisted blade design, and outlet side blade adjustment; When designing the tail guide vane, the data from the flow field recirculation conditions on the bearing side of the double-bladed impeller and the blade structural parameter relationship model are combined; When designing the middle spiral twisted blade, the structural parameters of the top diverter blade and the tail guide blade are combined; 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.

2. A motor vehicle axle end double blade seal device and axle end seal 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 turbulent dissipation intensity, with reference to the data in the relational model.

3. The double-vane seal device and shaft end seal design method for a motor vehicle 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 based on the adjusted redundancy.

4. The double-vane seal device and shaft end seal design method for a motor vehicle according to claim 1, characterized in that: When outputting the design results, the parametric model file secondary development module of 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.

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