A design method for disc spring assembly of main bearing of tunnel boring machine

Abstract

The present invention provides a design method for a disc spring group of a main bearing of a tunnel boring machine, and belongs to the field of bearing technology. The design method for the disc spring group of a main bearing of a tunnel boring machine includes: calculating the maximum force of the auxiliary thrust roller according to the working parameters of the main bearing of the tunnel boring machine and the bearing structure parameters, regarding the maximum force of the auxiliary thrust roller as the force received by the disc spring group, and then selecting the disc spring specifications according to the structural dimensions of the auxiliary thrust raceway, and designing the number and combination of disc springs according to the load of the single disc spring of the selected specifications and the force received by the disc spring group. Since the force will be transmitted to the disc spring through the rolling body, the present invention regards the maximum force of the auxiliary thrust roller as the force received by the disc spring group, which provides a basis and premise for the specific selection of the disc spring, and then facilitates the determination of the specifications, quantity and combination of the disc springs, ensuring that the design form of the disc spring group can cope with the eccentric load generated by the combined action of the axial load and the overturning moment on the main bearing, and ensure the normal operation of the shield machine.

Description

Technical Field

[0001] The invention relates to a design method for a disc spring group of a main bearing of a tunneling machine, and belongs to the technical field of bearings. Background Art

[0002] In recent years, with the rapid development of my country's infrastructure, shield machines have been widely used as an advanced tunnel construction machine. They are generally installed in key parts of large equipment. Once a failure occurs, it will seriously affect production, and the corresponding maintenance and replacement work cycle is long, resulting in large economic losses. If you want to ensure safe and efficient work in special environments, you must have high reliability. The shield main bearing is a key basic component of the shield machine. It undertakes the slewing support task between the shield cutter system and the power system. Its structure and load conditions are complex, and it is easy to produce large stress and deformation, affecting the construction safety of the shield machine.

[0003] At present, there is no systematic method for mechanical performance analysis of shield main bearings at home and abroad. Due to the complex structure, large size, large number of rollers and complex loading conditions of shield main bearings, it is impossible to use the traditional bearing rated dynamic and static load and fatigue life calculation methods for selection and design. Due to the various formation conditions during the working process, the main bearings of the tunnel boring machine are often subjected to eccentric loads caused by the combined action of axial loads and overturning moments. The safety of the main bearings of the tunnel boring machine under eccentric loads is an issue that must be considered during the design and research process.

[0004] In this regard, the Chinese invention patent application with application publication number CN111734735A discloses an outer ring of a main bearing of a tunnel boring machine and a main bearing of a tunnel boring machine, wherein the outer ring includes an outer ring body and a ring raceway, and the mating surfaces of the outer ring body and the ring raceway are provided with a groove, and a disc spring is embedded in the groove. There is also a similar shield machine main bearing structure such as Figure 1 As shown, it includes an outer ring, an inner gear ring 7, rolling elements, a cage, etc. The outer ring and the cage are both split structures. The outer ring includes a main thrust outer ring 3, a secondary thrust outer ring 9, and a radial raceway outer ring 4, which are fixed to the shield body by bolts. A main thrust retaining ring 1 is fixed to the inner side of the main thrust outer ring 3. The rolling elements include a main thrust roller 2, a secondary thrust roller 11, and a radial roller 8. The main thrust roller 2 is located between the inner gear ring 7 and the main thrust outer ring 3, and a main thrust cage 5 is provided on the outside. The radial roller 8 is located between the inner gear ring 7 and the radial raceway outer ring 4, and a radial cage 6 is provided on the outside. The secondary thrust roller 11 is located between the inner gear ring 7 and the floating ring 12, and a secondary thrust cage 10 is provided on the outside. A disc spring 13 is installed between the floating ring 12 and the secondary thrust outer ring 9.

[0005] During the excavation process, when encountering uneven hard and soft strata, the disc spring 13 and the floating ring 12 provide an elastic support to the auxiliary thrust roller 11, thereby buffering the vibration of the auxiliary thrust roller 11, preventing damage caused by excessive internal force, and ensuring continuous use. When the main bearing of the shield machine is subjected to axial force, radial force and overturning moment, the auxiliary thrust roller 11 is also subjected to the central axial force F a and overturning moment M. Under the equivalent eccentric load under the combined load, when a single disc spring 13 is used, the deformation and load value often cannot meet the requirements. Therefore, several disc springs 13 are often used in combination of different types to meet the use requirements of the shield machine.

[0006] However, there is no design method for the disc spring group of the main bearing of the tunnel boring machine in the existing technology. It is usually a rough estimate, and multiple tests and verifications are required in the later stage. Therefore, it is necessary to establish a design method for the disc spring group in the main bearing of the tunnel boring machine to facilitate the determination of the specifications, quantity and combination of the disc springs, and ensure that the design of the disc spring group can cope with the eccentric load generated by the combined action of the axial load and the overturning moment on the main bearing, so as to ensure the normal operation of the shield machine. Summary of the invention

[0007] The object of the present invention is to provide a design method for a main bearing disc spring group of a tunnel boring machine, which can easily determine the specifications, quantity and combination form of the disc springs.

[0008] To achieve the above purpose, the design method of the disc spring group of the main bearing of the tunnel boring machine in the present invention adopts the following technical scheme:

[0009] A design method for a disc spring group of a main bearing of a tunnel boring machine, wherein the maximum force of a secondary thrust roller is calculated according to the working parameters of the main bearing of the tunnel boring machine and the bearing structure parameters, the maximum force of the secondary thrust roller is regarded as the force received by the disc spring group, and then the disc spring specification is selected according to the structural dimensions of the secondary thrust raceway, and the number and combination of disc springs are designed according to the load of a single disc spring of the selected specification and the force received by the disc spring group.

[0010] The beneficial effect of the above technical solution is that: the design method of the present invention first calculates the maximum force of the auxiliary thrust roller according to the operating parameters of the main bearing of the tunnel boring machine and the bearing structure parameters, and then regards the maximum force of the auxiliary thrust roller as the force received by the disc spring group, which provides a basis and premise for the specific selection of the disc spring; then the disc spring specification is selected according to the structural dimensions of the auxiliary thrust raceway to ensure that the diameter of the disc spring matches the structural dimensions of the auxiliary thrust raceway. Once the disc spring specification is determined, the load and other parameters of the single disc spring can be determined, and then the number and combination of disc springs are designed according to the load of the single disc spring of the selected specification and the force received by the disc spring group. The number and deformation displacement of disc springs under different combinations (including overlapping combinations, matching combinations, composite combinations, etc.) are different. According to the specific force considerations and the structural dimensions of the bearing ring itself, the disc spring combination is selected and the number of designed disc springs is calculated.

[0011] Therefore, the design method of the present invention can be used to easily determine the specifications, quantity and combination of disc springs, ensuring that the design of the disc spring group can cope with the eccentric load generated by the combined action of the axial load and overturning moment on the main bearing, thereby ensuring the normal operation of the tunnel boring machine.

[0012] Furthermore, the above working condition parameters include the axial load F a , radial load F r , overturning moment M.

[0013] The beneficial effect of the above technical solution is that it is convenient to calculate the maximum force of the auxiliary thrust roller.

[0014] Furthermore, the above-mentioned bearing structural parameters include the total number of rolling elements of the main thrust roller, the auxiliary thrust roller and the radial roller, the rolling element size and the distribution circle diameter.

[0015] The beneficial effect of the above technical solution is that it is convenient to calculate the maximum force of the auxiliary thrust roller.

[0016] Furthermore, when selecting the disc spring specifications, the diameter of the disc spring is selected to be less than or equal to half of the width of the secondary thrust raceway.

[0017] The beneficial effect of the above technical solution is to avoid the disc spring diameter being too large, which will lead to an excessively large installation groove size and affect the structural strength of the auxiliary thrust outer ring, and at the same time avoid the disc spring diameter being too large, which will affect the cooperation with the floating ring.

[0018] Furthermore, when selecting the specifications of disc springs, first select at least two specifications of disc springs, then determine the number and combination of disc springs of each specification based on the load of each selected specification of single disc springs and the force applied to the disc spring group, and finally select disc springs of appropriate specifications based on the structural dimensions of the bearing ring.

[0019] The beneficial effects of the above technical solution are: first, at least two specifications of disc springs are selected to expand the range of options, and finally, disc springs of appropriate specifications can be selected according to the structural dimensions of the bearing ring to improve the selection efficiency.

[0020] Furthermore, three specifications of disc springs are selected, one each from the A series, the B series and the C series.

[0021] The beneficial effects of the above technical solution are: a wider range of options and more room for choice.

[0022] Furthermore, a gasket is arranged in the disc spring installation groove of the auxiliary thrust outer ring, the gasket is located between the disc spring and the floating ring, and the protrusion of the gasket from the installation groove is greater than or equal to the deformation f of the single disc spring.

[0023] The beneficial effect of the above technical solution is that: through the cooperation between the gasket and the floating ring, the disc spring group can better cooperate with the floating ring, and the force on the disc spring group is more uniform. At the same time, the protrusion of the gasket from the installation groove is greater than or equal to the deformation f of the single disc spring, ensuring that the disc spring can deform smoothly.

[0024] Furthermore, the protrusion amount of the gasket from the mounting groove is 1 mm.

[0025] The beneficial effect of the above technical solution is that the value of the protrusion can meet the deformation requirements of most disc springs and facilitate the determination of the gasket size.

[0026] Furthermore, the combination form of the disc spring group is selected to be a superimposed combination, and the number of disc springs is greater than or equal to the value of the force applied to the disc spring group divided by the load of a single disc spring.

[0027] The beneficial effect of the above technical solution is that the disc spring group in the main bearing of the tunnel boring machine is mainly considered to have a stress effect, so a superimposed combination is selected, which makes it easier to calculate the number of disc springs. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] Figure 1 It is a schematic diagram of the main bearing structure of a shield machine in the prior art;

[0029] Figure 2 A flow chart of the design method of the present invention;

[0030] Figure 3 This is a result diagram of disc spring selection in Example 1 of the design method of the present invention.

[0031] In the figure: 1. main thrust retaining ring; 2. main thrust roller; 3. main thrust outer ring; 4. radial raceway outer ring; 5. main thrust retaining frame; 6. radial retaining frame; 7. inner gear ring; 8. radial roller; 9. auxiliary thrust outer ring; 10. auxiliary thrust retaining frame; 11. auxiliary thrust roller; 12. floating ring; 13. disc spring; 14. gasket. DETAILED DESCRIPTION

[0032] In order to make the purpose, technical scheme and advantages of the present invention clearer, the present invention is further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not used to limit the present invention, that is, the described embodiments are only part of the embodiments of the present invention, rather than all the embodiments. The components of the embodiments of the present invention described and shown in the drawings herein can be arranged and designed in various different configurations.

[0033] Therefore, the following detailed description of the embodiments of the present invention provided in the accompanying drawings is not intended to limit the scope of the invention claimed for protection, but merely represents selected embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without making creative work are within the scope of protection of the present invention.

[0034] It should be noted that relational terms such as "first" and "second" that may appear are only used to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any actual relationship or order between these entities or operations. Moreover, terms such as "include", "comprise" or any other variants thereof are intended to cover non-exclusive inclusion, so that a process, method, article or device that includes a series of elements includes not only those elements, but also other elements that are not explicitly listed, or also includes elements inherent to such process, method, article or device. In the absence of further restrictions, an element defined by a sentence such as "comprises a..." does not exclude the existence of other identical elements in the process, method, article or device that includes the element.

[0035] The features and performance of the present invention are further described in detail below in conjunction with the embodiments.

[0036] Embodiment 1 of the design method of the main bearing disc spring group of the tunnel boring machine in the present invention: The tunnel boring machine in this embodiment is Figure 1 The shield machine shown in the figure. The specific steps of the design method are as follows Figure 2 As shown, the first step is to determine the operating parameters of the shield machine main bearing, which include the axial load F a , radial load F r , overturning moment M, taking a domestic type of shield machine as an example, as shown in Table 1.

[0037] Table 1 Operating parameters of the main bearing of a domestic shield machine

[0038]

[0039] The second step is to determine the bearing structure parameters, combined with Figure 1 As shown in Table 2, the bearing structural parameters include the total number of rolling elements, rolling element size and distribution circle diameter of the main thrust roller 2, the auxiliary thrust roller 11 and the radial roller 8, as shown in Table 2.

[0040] Table 2 Structural parameters of the main bearing of a domestic shield machine

[0041] parameter Main thrust roller Auxiliary thrust roller Radial Roller Total number of rolling elements 210 150 220 Rolling element size (mm) Φ100×100 Φ70×70 Φ50×80 Distribution circle diameter (mm) Φ4265 Φ4400 Φ4540

[0042] The third step is to calculate the maximum force of the secondary thrust roller 11 according to the determined working parameters and bearing structure parameters, and calculate the maximum rolling element load Q of the secondary thrust roller = 17127N. The specific calculation method is the existing technology, such as the calculation method disclosed in Li Yunfeng's paper "Calibration Calculation Method of Three-row Roller Turntable Bearing" (China Mechanical Engineering, 2018, No. 3), or Zhang Tao's paper "Research on the Safety of Main Bearing of Shield Machine under Eccentric Load" (Mechanical Engineering and Automation, 2021, No. 3). The specific calculation process will not be described in detail in this invention.

[0043] According to the bearing structure, the force is transmitted to the disc spring through the rolling element. Therefore, the calculated maximum force of the secondary thrust roller is regarded as the force exerted on the disc spring group. This provides a basis and premise for the specific selection of the disc spring. Otherwise, the subsequent calculation and selection cannot be carried out due to the unclear force exerted on the disc spring group.

[0044] The fourth step is to select the disc spring specifications according to the structural dimensions of the auxiliary thrust raceway to ensure that the diameter D of the disc spring matches the structural dimensions of the auxiliary thrust raceway. Figure 1 On the side of the middle floating ring 12 facing the auxiliary thrust roller 11, the auxiliary thrust raceway width is H=96, and the diameter of the disc spring 13 is selected to be less than or equal to half of the auxiliary thrust raceway width, that is, D≤H / 2. Therefore, according to "GB / T 1972-2005 Disc Spring", the disc spring diameter D=45 can be selected, and three specifications of disc springs are selected, one each of the A series, B series and C series, namely A45, B45 and C45.

[0045] The fifth step is to determine the number and combination of disc springs of each specification according to the load of each selected specification of single disc spring and the force of the disc spring group. The combination of disc springs includes superimposed combination, matched combination, composite combination, etc. The number of disc springs and deformation displacement under different combinations are different. Since the main consideration in the present invention is the force of the disc spring group, the superimposed combination is selected, while the matched combination pays more attention to the displacement. According to "GB / T 1972-2005 Disc Spring", the load F and deformation f corresponding to single disc springs of different specifications are shown in Table 3.

[0046] Table 3 Load F and deformation f corresponding to single disc springs of different specifications

[0047] series A45 B45 C45 F / N 7720 3660 1890 f / mm 0.75 0.98 1.65

[0048] Therefore, under a certain overlapping combination, the number of disc springs should be greater than or equal to the value of the force on the disc spring group divided by the load of a single disc spring, that is, the number of disc springs n ≥ Q / F, that is:

[0049] If A45 specification is selected, n≥17127 / 7720=2.21, n is 3;

[0050] If B45 specification is selected, n≥17127 / 3660=4.67, n is 5;

[0051] If the C45 specification is selected, n≥17127 / 1890=9.06, and n is 10.

[0052] Finally, according to the structural dimensions of the bearing ring, a disc spring of appropriate specifications is selected. If a large number of disc springs need to be installed, the auxiliary thrust outer ring 9 is required to have sufficient size. In this embodiment, according to the structural dimensions of the bearing ring of a certain type of shield machine mentioned above, three disc springs of A45 specifications are selected for superposition and combination. Figure 3 As shown, a gasket 14 is arranged in the disc spring installation groove of the secondary thrust outer ring 9, and the gasket 14 is located between the disc spring 13 and the floating ring 12, so that the force of the disc spring group is more uniform, and at the same time, the protrusion of the gasket 14 from the installation groove is greater than or equal to the deformation f of the single disc spring, ensuring that the disc spring can be deformed smoothly. Since the A45 specification is selected in this embodiment, the protrusion of the gasket 14 is 1mm.

[0053] At this point, the design of the disc spring group of the main bearing of a certain type of shield machine has been completed. The design method of the present invention can be used to easily determine the specifications, quantity and combination of the disc springs, ensuring that the design of the disc spring group can cope with the eccentric load generated by the combined action of the axial load and the overturning moment on the main bearing, thereby ensuring the normal operation of the shield machine.

[0054] In other embodiments of the design method of the main bearing disc spring group of the tunnel boring machine: the design method of the present invention is also applicable to hard rock tunnel boring machines (TBM).

[0055] In other embodiments of the design method of the main bearing disc spring group of the tunnel boring machine: if the disc spring of specification B45 is finally selected, the protrusion of the gasket from the mounting groove can be 1.2mm or 1.3mm; if the disc spring of specification C45 is finally selected, the protrusion of the gasket from the mounting groove can be 1.9mm or 2mm.

[0056] In other embodiments of the design method of the disc spring group of the main bearing of the tunnel boring machine: a gasket may not be provided, and the disc spring is in direct contact with the floating ring.

[0057] In other embodiments of the design method of the disc spring group of the main bearing of the tunnel boring machine: when selecting the disc spring specifications, two specifications of disc springs can be selected as alternatives, or one can be selected first and then replaced if it is not suitable.

[0058] In other embodiments of the design method of the disc spring group of the main bearing of the tunnel boring machine: when selecting the disc spring specifications, if the size is appropriate, the diameter of the disc spring can also be equal to half the width of the secondary thrust raceway. Of course, if there is no suitable optional value that is less than or equal to half the width of the secondary thrust raceway, a size slightly larger than half the width of the secondary thrust raceway can also be selected.

[0059] In other embodiments of the design method of the disc spring group of the main bearing of the tunnel boring machine: according to different calculation methods, the required operating parameters and bearing structure parameters of the main bearing of the tunnel boring machine may be different, but these operating parameters and bearing structure parameters are existing data and can be selected and determined according to needs.

[0060] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. The patent protection scope of the present invention shall be based on the claims. All equivalent structural changes made using the contents of the description and drawings of the present invention should also be included in the protection scope of the present invention.

Claims

1. A design method for a disc spring assembly of a main bearing of a tunnel boring machine, characterized in that: The maximum force of the auxiliary thrust roller is calculated according to the working parameters and bearing structure parameters of the main bearing of the tunnel boring machine. The maximum force of the auxiliary thrust roller is regarded as the force received by the disc spring group. Then, the disc spring specifications are selected according to the structural dimensions of the auxiliary thrust raceway. The number and combination of disc springs are designed according to the load of the single disc spring of the selected specifications and the force received by the disc spring group. A gasket is arranged in the disc spring installation groove of the auxiliary thrust outer ring. The gasket is located between the disc spring and the floating ring. The protrusion of the gasket from the disc spring installation groove is greater than or equal to the deformation f of the single disc spring to ensure that the disc spring can deform smoothly.

2. The design method of the main bearing disc spring assembly of the tunnel boring machine according to claim 1 is characterized in that: The above working parameters include the axial load F a , radial load F r , overturning moment M.

3. The design method of the disc spring assembly of the main bearing of the tunnel boring machine according to claim 1 or 2, characterized in that: The above bearing structural parameters include the total number of rolling elements of the main thrust roller, the auxiliary thrust roller and the radial roller, the rolling element size and the distribution circle diameter.

4. The design method of the main bearing disc spring assembly of the tunnel boring machine according to claim 1 or 2, characterized in that: When selecting the disc spring specifications, choose a disc spring with a diameter less than or equal to half the width of the auxiliary thrust raceway.

5. The design method of the disc spring assembly of the main bearing of the tunnel boring machine according to claim 1 or 2, characterized in that: When selecting the disc spring specifications, first select at least two specifications of disc springs, then determine the number and combination of disc springs of each specification based on the load of each selected specification of single disc spring and the force applied to the disc spring group, and finally select the disc spring of appropriate specifications based on the structural dimensions of the bearing ring.

6. The design method of the disc spring assembly of the main bearing of the tunnel boring machine according to claim 5 is characterized in that: Select three specifications of disc springs, one each from the A series, B series, and C series.

7. The design method of the main bearing disc spring assembly of a tunnel boring machine according to claim 1, characterized in that: The protrusion of the gasket from the mounting groove is 1 mm.

8. The design method of the main bearing disc spring assembly of a tunnel boring machine according to claim 1 or 2, characterized in that: The disc spring group is selected to be a superimposed combination, and the number of disc springs is greater than or equal to the force applied to the disc spring group divided by the load of a single disc spring.

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