Error adjustment methods for bearing mechanisms, transmission devices, and bearing mechanisms

Abstract

This application relates to the field of oilfield equipment technology, and in particular to a bearing mechanism, a transmission device, and an error adjustment method for the bearing mechanism. The bearing mechanism includes a first bearing assembly, a first spacer, a second bearing assembly, a second spacer, a first washer, and a second washer. The first bearing assembly is sleeved outside the first spacer, and the second bearing assembly is spaced apart from the first bearing assembly and sleeved outside the second bearing assembly. The two ends of the first washer abut against the first bearing assembly and the second spacer, respectively. The first washer is ringed around the second washer, and the two ends of the second washer abut against the first spacer and the second bearing assembly, respectively. When the first bearing assembly and the first spacer are subjected to an external force toward the second bearing assembly, the first bearing assembly transmits a portion of the external force to the second spacer through the first washer, and the first spacer transmits the other portion of the external force to the second bearing assembly through the second washer, so that the first bearing assembly and the second bearing assembly are subjected to force evenly, thereby extending the service life of the bearing mechanism.

Description

Technical Field

[0001] This application relates to the field of oil production equipment technology, and in particular to a bearing mechanism, a transmission device, and a method for adjusting the error of the bearing mechanism. Background Technology

[0002] Bearings are essential components in modern machinery. Their main function is to support rotating mechanical parts, reduce the coefficient of friction during movement, and ensure rotational accuracy. Bearing assemblies are used in various transmission devices, which are subjected to axial, radial, and circumferential forces during operation.

[0003] In the process of developing this application, the inventors discovered that when the transmission device is subjected to a large force in the axial direction, multiple bearing groups are often installed in series along the main shaft. However, this method can cause the first bearing group to be subjected to excessive force, affecting the operation of the bearing. Summary of the Invention

[0004] This application provides a bearing mechanism, a transmission device, and a method for adjusting the error of the bearing mechanism. This method can improve the current situation where multiple bearing groups are installed in series along the main shaft, which can lead to excessive force on the first bearing group and affect the operation of the bearing.

[0005] To solve the above-mentioned technical problems, this application adopts the following technical solution: A bearing mechanism is provided, including a first bearing assembly, a first spacer, a second bearing assembly, a second spacer, a first washer, and a second washer. The first bearing assembly is sleeved outside the first spacer. The second bearing assembly is axially spaced from the first bearing assembly. The second spacer is sleeved outside the second bearing assembly. The two ends of the first washer abut against the first bearing assembly and the second spacer, respectively. The first washer is circumferentially disposed outside the second washer, and the two ends of the second washer abut against the first spacer and the second bearing assembly, respectively. When the first bearing assembly and the first spacer are subjected to an external force toward the second bearing assembly, the first bearing assembly transmits a portion of the external force to the second spacer through the first washer, and the first spacer transmits another portion of the external force to the second bearing assembly through the second washer, thereby ensuring that the first bearing assembly and the second bearing assembly are subjected to uniform force.

[0006] In some embodiments, along the axial direction of the first bearing assembly, the first washer includes a first abutting portion and a second abutting portion connected together, the end of the first abutting portion opposite to the second abutting portion abutting with the first bearing assembly, the end of the second abutting portion opposite to the first abutting portion abutting with the second spacer, and the radial cross-sectional area of ​​the first abutting portion being larger than the radial cross-sectional area of ​​the second abutting portion; and / or along the axial direction of the second bearing assembly, the second washer includes a third abutting portion and a fourth abutting portion connected together, the end of the third abutting portion opposite to the fourth abutting portion abutting with the first spacer, the end of the fourth abutting portion opposite to the third abutting portion abutting with the second bearing assembly, and the radial cross-sectional area of ​​the third abutting portion being smaller than the radial cross-sectional area of ​​the fourth abutting portion.

[0007] In some embodiments, along the axial direction of the first bearing assembly, the first washer includes a first abutting portion, a first middle portion, and a second abutting portion connected in sequence. The end of the first abutting portion opposite to the second abutting portion abuts against the first bearing assembly, and the end of the second abutting portion opposite to the first abutting portion abuts against the second spacer. The radial cross-sectional area of ​​the first abutting portion is larger than the radial cross-sectional area of ​​the second abutting portion, and the radial cross-sectional area of ​​the first middle portion decreases sequentially from the end opposite to the second abutting portion towards the other end. Along the axial direction of the second bearing assembly, the second washer includes a third abutting portion, a second middle portion, and a fourth abutting portion connected in sequence. The end of the third abutting portion opposite to the fourth abutting portion abuts against the first spacer, and the end of the fourth abutting portion opposite to the third abutting portion abuts against the second bearing assembly. The radial cross-sectional area of ​​the third abutting portion is smaller than the radial cross-sectional area of ​​the fourth abutting portion, and the radial cross-sectional area of ​​the second middle portion increases sequentially from the end opposite to the fourth abutting portion towards the other end.

[0008] In some embodiments, the first central portion includes an inner side facing the second washer. The second central portion includes an outer side facing the first washer. The inner side and the outer side are respectively angled relative to the axial direction of the first bearing assembly, and a gap is provided between the inner side and the outer side.

[0009] In some embodiments, the sum of the lengths of the first bearing assembly, the first washer, and the second spacer is L1, the sum of the lengths of the first spacer, the second washer, and the second bearing assembly is L2, the cross-sectional area of ​​the first spacer is A1, and the cross-sectional area of ​​the second spacer is A2. L1, A1, L2, and A2 satisfy: L1 / A1 = L2 / A2.

[0010] In some embodiments, the bearing mechanism further includes a third spacer sleeved outside the first bearing assembly; and / or the bearing mechanism further includes a fourth spacer sleeved outside the second bearing assembly.

[0011] To solve the above-mentioned technical problems, this application also adopts another technical solution, providing a transmission device, the transmission device including a main shaft and the above-mentioned bearing mechanism, the bearing mechanism being sleeved on the main shaft.

[0012] In some embodiments, the transmission device further includes a housing fitted over the bearing mechanism. The transmission device also includes a race disposed within the housing, with both ends of the race abutting against the housing and a second bearing assembly of the bearing mechanism, respectively; and / or the transmission device further includes a bushing fitted over the main shaft, with one end of the bushing abutting against a fourth spacer of the bearing mechanism.

[0013] To address the aforementioned technical problems, this application also employs another technical solution, providing a method for adjusting the error of the aforementioned bearing mechanism. The bearing mechanism includes a first bearing assembly and a second bearing assembly. The first bearing assembly includes the first bearing assembly, a first washer, and a second spacer. The second bearing assembly includes the first spacer, the second washer, and the second bearing assembly. The method includes: calculating the theoretical deformation of the first spacer and / or the second spacer under a preset load; measuring the cross-sectional area of ​​the first spacer and the cross-sectional area of ​​the second spacer, and calculating the ratio of the cross-sectional areas of the first spacer and the second spacer; calculating a length adjustment difference based on the theoretical deformation and the cross-sectional area ratio; and adjusting the length of the first washer and / or the second washer so that the length difference between the first bearing shaft assembly and the second bearing shaft assembly satisfies the length adjustment difference.

[0014] In some embodiments, the formula for calculating the theoretical deformation is:

[0015]

[0016] in, Let F be the theoretical deformation, l be the design length of the first spacer and / or the design length of the second spacer, E be the stiffness of the first spacer and / or the stiffness of the second spacer, and A be the design cross-sectional area of ​​the first spacer and / or the design cross-sectional area of ​​the second spacer.

[0017] In some embodiments, the formula for calculating the length adjustment difference is:

[0018]

[0019] Where A1 is the cross-sectional area of ​​the first spacer and A2 is the cross-sectional area of ​​the second spacer. The theoretical deformation amount is... Adjust the difference for the length.

[0020] The beneficial effects of this application embodiment are as follows: Unlike the prior art, this application embodiment provides a bearing mechanism including a first bearing assembly, a first spacer, a second bearing assembly, a second spacer, a first washer, and a second washer. The first bearing assembly is sleeved outside the first spacer. The second bearing assembly is axially spaced from the first bearing assembly. The second spacer is sleeved outside the second bearing assembly. The two ends of the first washer abut against the first bearing assembly and the second spacer, respectively. The first washer is circumferentially disposed outside the second washer, and the two ends of the second washer abut against the first spacer and the second bearing assembly, respectively. When the first bearing assembly and the first spacer are subjected to an external force toward the second bearing assembly, the first bearing assembly transmits a portion of the external force to the second spacer through the first washer, and the first spacer transmits another portion of the external force to the second bearing assembly through the second washer, thereby ensuring uniform force distribution between the first bearing assembly and the second bearing assembly. Through this structure, the first bearing assembly and the second bearing assembly can share the axial load, reducing the impact on bearing operation and ensuring uniform force distribution between them, thus extending the service life of the bearing mechanism. Attached Figure Description

[0021] To more clearly illustrate the technical solutions of the embodiments of this application, the drawings used in the embodiments of this application will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on the drawings without creative effort.

[0022] Figure 1 This is a perspective view of a bearing mechanism provided in one embodiment of this application;

[0023] Figure 2 This is provided by one embodiment of the present application. Figure 1 A-side cross-sectional view;

[0024] Figure 3 This is provided by one embodiment of the present application. Figure 2 Enlarged view of part B;

[0025] Figure 4 This is provided by one embodiment of the present application. Figure 2 Enlarged view of part C;

[0026] Figure 5This is provided by one embodiment of the present application. Figure 2 Enlarged view of part D;

[0027] Figure 6 This is a step diagram of the bearing mechanism calculation method provided in one embodiment of this application.

[0028] The attached figures are labeled as follows:

[0029] Detailed Implementation

[0030] To facilitate understanding of this application, a more detailed description is provided below with reference to the accompanying drawings and specific embodiments. It should be noted that when an element is described as being "fixed to" another element, it can be directly on the other element, or one or more intermediate elements may exist between them. When an element is described as being "connected" to another element, it can be directly connected to the other element, or one or more intermediate elements may exist between them. The terms "vertical," "horizontal," "left," "right," and similar expressions used in this specification are for illustrative purposes only.

[0031] Unless otherwise defined, all technical and scientific terms used in this specification have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to limit the scope of this application. The term "and / or" as used in this specification includes any and all combinations of one or more of the associated listed items.

[0032] In practical applications of various transmission devices, when the transmission device is subjected to a large axial force, multiple sets of bearings are typically mounted on the spindle. This allows the axial force on the spindle to be evenly distributed across the bearing sets, reducing the force on the spindle and improving its operational stability. However, in this structure, the bearing sets closer to the source of the force will experience relatively large forces, while those farther away will experience relatively small forces. This can easily lead to fatigue damage in some bearing sets, severely affecting the transmission efficiency of the spindle.

[0033] Based on this, this application adopts a technical solution, please refer to... Figure 1 and Figure 2This application provides a bearing mechanism 100, including a first bearing assembly 110, a first spacer 120, a second bearing assembly 130, a second spacer 140, a first washer 150, and a second washer 160. The first bearing assembly 110 is sleeved outside the first spacer 120. The second bearing assembly 130 is axially spaced from the first bearing assembly 110. The second spacer 140 is sleeved outside the second bearing assembly 130. The two ends of the first washer 150 abut against the first bearing assembly 110 and the second spacer 140, respectively. The first washer 150 is circumferentially disposed around the second washer 160, and the two ends of the second washer 160 abut against the first spacer 120 and the second bearing assembly 130, respectively. When the first bearing assembly 110 and the first spacer 120 are subjected to an external force toward the second bearing assembly 130, the first bearing assembly 110 transmits a portion of the external force to the second spacer 140 through the first washer 150, and the first spacer 120 transmits another portion of the external force to the second bearing assembly 130 through the second washer 160, so that the first bearing assembly 110 and the second bearing assembly 130 are subjected to force evenly.

[0034] It is understood that when the first bearing assembly 110 is subjected to an axial external force, at least part of the external force is transmitted along the direction of the first bearing assembly 110, the first washer 150, and the second spacer 140; another part of the external force is transmitted along the direction of the first spacer 120, the second washer 160, and the second bearing assembly 130. Optionally, the first bearing assembly 110 and the first spacer 120 may be subjected to an external force first, and the other may then share the remaining load, or they may be subjected to external forces simultaneously; that is, by shortening the distance between the first bearing assembly 110 and the second bearing assembly 130, the load is evenly distributed between the first bearing assembly 110 and the second bearing assembly 130, thereby improving the load-bearing capacity of the bearing mechanism 100.

[0035] In some embodiments, see [link to relevant documentation]. Figure 2 and Figure 3In conjunction with other accompanying drawings, along the axial direction of the first bearing assembly 110, the first washer 150 includes a first abutting portion 151 and a second abutting portion 152 connected together. The end of the first abutting portion 151 opposite to the second abutting portion 152 abuts against the first bearing assembly 110, and the end of the second abutting portion 152 opposite to the first abutting portion 151 abuts against the second spacer 140. The radial cross-sectional area of ​​the first abutting portion 151 is larger than the radial cross-sectional area of ​​the second abutting portion 152. And / or along the axial direction of the second bearing assembly 130, the second washer 160 includes a third abutting portion 161 and a fourth abutting portion 162 connected together. The end of the third abutting portion 161 opposite to the fourth abutting portion 162 abuts against the first spacer 120, and the end of the fourth abutting portion 162 opposite to the third abutting portion 161 abuts against the second bearing assembly 130. The radial cross-sectional area of ​​the third abutting portion 161 is smaller than the radial cross-sectional area of ​​the fourth abutting portion 162. It is understandable that the relatively large radial cross-sectional area of ​​the first abutment portion 151 is to abut against the first bearing assembly 110, thereby increasing the contact area and reducing stress concentration. The radial cross-sectional area of ​​the second abutment portion 152 should be less than or equal to the radial cross-sectional area of ​​the second spacer 140, so that when the component force is transmitted to the second spacer 140, the force will not be transmitted to the second bearing assembly 130 adjacent to the second spacer 140. This reduces the impact of the component force on the transmission path of the first bearing assembly 110, the first washer 150 and the second spacer 140 on the load-bearing effect of the second bearing assembly 130, thereby improving the stability of the load distribution. Regarding the third abutment portion 161 and the fourth abutment portion 162, the radial cross-sectional area of ​​the fourth abutment portion 162 is relatively large to abut against the second bearing assembly 130, thereby increasing the contact area and reducing stress concentration. The radial cross-sectional area of ​​the third abutment portion 161 should be less than or equal to the radial cross-sectional area of ​​the first spacer 120, so that when the force component is transmitted from the first spacer 120 to the second washer 160, the second washer 160 will not be subjected to the force component from the first bearing assembly 110. This reduces the impact of the force component along the transmission path of the first spacer 120, the second washer 160, and the second bearing assembly 130 on the load-bearing effect of the second washer 160 and the second bearing assembly 130, thereby improving the stability of the load distribution. It should be noted that the first washer 150 and the second washer 160 can be a structure composed of multiple washers with different radial cross-sectional areas, or washers with a stepped profile. That is, it is only necessary to make the radial cross-sectional area of ​​the first abutment portion 151 greater than the radial cross-sectional area of ​​the second abutment portion 152, and the radial cross-sectional area of ​​the fourth abutment portion 162 greater than the radial cross-sectional area of ​​the third abutment portion 161.

[0036] In other embodiments, please refer to Figure 3 and Figure 4In conjunction with other accompanying drawings, along the axial direction of the first bearing assembly 110, the first washer 150 includes a first abutting portion 151, a first middle portion 153, and a second abutting portion 152 connected in sequence. The end of the first abutting portion 151 opposite to the second abutting portion 152 abuts against the first bearing assembly 110, and the end of the second abutting portion 152 opposite to the first abutting portion 151 abuts against the second spacer 140. The radial cross-sectional area of ​​the first abutting portion 151 is larger than the radial cross-sectional area of ​​the second abutting portion 152, and the radial cross-sectional area of ​​the first middle portion 153 decreases sequentially from the end opposite to the second abutting portion 152 toward the other end. Along the axial direction of the second bearing assembly 130, the second washer 160 includes a third abutment portion 161, a second middle portion 163, and a fourth abutment portion 162 connected in sequence. The end of the third abutment portion 161 opposite to the fourth abutment portion 162 abuts against the first spacer 120, and the end of the fourth abutment portion 162 opposite to the third abutment portion 161 abuts against the second bearing assembly 130. The radial cross-sectional area of ​​the third abutment portion 161 is smaller than the radial cross-sectional area of ​​the fourth abutment portion 162, and the radial cross-sectional area of ​​the second middle portion 163 increases sequentially from the end opposite to the fourth abutment portion 162 towards the other end. Unlike the previous embodiment, a first middle portion 153 is provided to prevent a large transition in cross-sectional area within the first washer 150, thereby reducing stress concentration within the first washer 150. Similarly, a second middle portion 163 is provided to prevent a large transition in cross-sectional area within the second washer 160, thereby reducing stress concentration within the second washer 160.

[0037] Further, please refer to Figure 4 The first central portion 153 includes an inner side surface 1531, which faces the second washer 160. The second central portion 163 includes an outer side surface 1631, which faces the first washer 150. The inner side surface 1531 and the outer side surface 1631 are respectively angled relative to the axial direction of the first bearing assembly 110, and a gap is provided between the inner side surface 1531 and the outer side surface 1631. By providing the gap, the first washer 150 and the second washer 160 are separated, thereby separating the force transmission path of the first bearing assembly 110, the first washer 150 and the second spacer 140 from the force transmission path of the first spacer 120, the second washer 160 and the second bearing assembly 130, so that the first bearing assembly 110 and the second bearing assembly 130 share the load and each bears the load independently, thereby optimizing the load distribution inside the bearing mechanism 100. Optionally, the inner surface 1531 and the outer surface 1631 can be parallel surfaces that are curved.

[0038] In some embodiments, the sum of the lengths of the first bearing assembly 110, the first washer 150, and the second spacer 140 is L1, and the sum of the lengths of the first spacer 120, the second washer 160, and the second bearing assembly 130 is L2. The cross-sectional area of ​​the first spacer 120 is A1, and the cross-sectional area of ​​the second spacer 140 is A2. L1, A1, L2, and A2 satisfy: L1 / A1 = L2 / A2. It is understood that in the actual design, manufacturing, and assembly process, errors are prone to exist between the various parts, which in turn affect the load distribution of the above structure. Therefore, when L1 / A1 = L2 / A2 is satisfied, the load distribution inside the bearing mechanism 100 can be effectively improved, thereby increasing the load-bearing capacity.

[0039] In some embodiments, please refer to Figure 3 and Figure 4 The bearing mechanism 100 also includes a third spacer 111, which is sleeved outside the first bearing assembly 110; and / or the bearing mechanism 100 also includes a fourth spacer 131, which is sleeved outside the second bearing assembly 130. By providing the third spacer 111, the first bearing assembly 110 can be separated from other structures on the side of the first bearing assembly 110 opposite to the first spacer 120, thereby reducing frictional resistance and improving transmission efficiency. Similarly, by providing the fourth spacer 131, the second bearing assembly 130 can be separated from other structures on the side of the second bearing assembly 130 opposite to the second spacer 140, thereby reducing frictional resistance and improving transmission efficiency.

[0040] Based on the aforementioned bearing mechanism 100, please refer to Figure 1 and Figure 5 In conjunction with other accompanying drawings, and the aforementioned transmission device 1000, the transmission device 1000 further includes a main shaft 500. A bearing mechanism 100 is sleeved on the main shaft 500, thereby enabling the main shaft 500 to fully utilize the bearing mechanism 100 to uniformly distribute the load when subjected to external forces in its axial direction, thereby improving the axial force-bearing capacity of the main shaft 500.

[0041] For the aforementioned transmission device 1000, please refer to Figure 1 and Figure 5In conjunction with other accompanying drawings, the transmission device 1000 further includes a housing 200, a bearing ring 300, and a bushing 400. The housing 200 is fitted over the bearing mechanism 100. The transmission device 1000 also includes a bearing ring 300, which is disposed within the housing 200, with both ends of the bearing ring 300 abutting against the housing 200 and the second bearing assembly 130 of the bearing mechanism 100, respectively; and / or the transmission device 1000 also includes a bushing 400, which is fitted over the main shaft 500, with one end of the bushing abutting against the fourth spacer 131 of the bearing mechanism 100. It should be noted that the housing 200 is provided with a receiving cavity 210, which is used to receive the aforementioned main shaft 500 and bearing mechanism 100. It is understood that a clearance space is provided between the third spacer 111 and the housing 200, and another clearance space is provided between the second spacer 140 and the housing 200. The first spacer 120 is at least partially recessed in the axial direction of the main shaft 500 to form a clearance space, thereby reducing the contact area between the first spacer 120 and the housing 200, thus reducing the circumferential frictional resistance between the first spacer 120 and the housing 200, and reducing wear on the first spacer 120 or the housing 200. Correspondingly, the second spacer 140 is at least partially recessed in the direction of the housing 200 to form a clearance space, thereby reducing the contact area between the second spacer 140 and the main shaft 500, thus reducing the frictional resistance between the second spacer 140 and the main shaft 500, and reducing wear on the second spacer 140 or the main shaft 500. It is understood that lubricating oil, lubricant, etc., can also be added within the clearance space to further improve the isolation performance of the first spacer 120 and / or the second spacer 140, and reduce the noise generated by vibration when the main shaft 500 rotates. It is understood that clearance spaces are also provided between the first spacer 120 and the main shaft 500, and between the fourth spacer 131 and the main shaft 500, which function similarly to the clearance spaces mentioned above, and will not be described in detail here. The bearing ring 300 is disposed within the housing 200, and both ends of the bearing ring 300 abut against the housing 200 and the second bearing assembly 130 of the bearing mechanism 100, respectively. By providing the bearing ring 300, the bearing mechanism 100 is mounted on the main shaft 500. Optionally, the housing 200 is also provided with a limiting part 220, which is located on the side of the bearing ring 300 away from the second bearing assembly 130, thereby further bearing force through the bearing ring 300. The transmission device 1000 also includes a bushing 400, which is sleeved on the main shaft 500, with one end of the bushing 400 abutting against the fourth spacer 131 of the bearing mechanism 100, thereby mounting the bearing mechanism 100 on the main shaft 500.

[0042] Please refer to the above description of housing 200 and seat ring 300. Figure 5The above-mentioned force transmission path will be further explained in conjunction with other accompanying drawings. The first bearing assembly 110, the first washer 150, and the second spacer 140 are connected to form a first load-bearing shaft assembly, allowing the first load-bearing shaft assembly to share a portion of the external force. Specifically, when the end of the first bearing assembly 110 away from the second bearing assembly 130 is subjected to an external force, a portion of the force is transmitted to the housing 200 through the first bearing assembly 110, the first washer 150, and the second spacer 140. The first spacer 120, the second washer 160, and the second bearing assembly 130 are connected to form a second load-bearing shaft assembly, allowing the second load-bearing shaft assembly to share another portion of the external force. Specifically, the other portion of the force is transmitted to the housing 200 through the first spacer 120, the second washer 160, the second bearing assembly 130, and the seat ring 300; thereby optimizing the load distribution of the transmission device 1000.

[0043] As mentioned above, axial errors are inevitable in the actual manufacturing and installation of the bearing mechanism 100. Therefore, this application also provides an error adjustment method for the bearing mechanism 100, used to calculate the aforementioned bearing mechanism 100. The bearing mechanism 100 includes the aforementioned first bearing shaft group and second bearing shaft group, wherein the first bearing shaft group includes a first bearing group 110, a first washer 150, and a second spacer 140, and the second bearing shaft group includes a first spacer 120, a second washer 2+0, and a second bearing group 130. For specific calculation methods, please refer to the following text and... Figure 6 , and in conjunction with other accompanying figures.

[0044] S01: Calculate the theoretical deformation of the first spacer 120 and / or the second spacer 140 under the preset load;

[0045] S02: Measure the cross-sectional area of ​​the first spacer 120 and the cross-sectional area of ​​the second spacer 140, and calculate the ratio of the cross-sectional area of ​​the first spacer 120 to the cross-sectional area of ​​the second spacer 140.

[0046] S03: The length adjustment difference is calculated based on the ratio of theoretical deformation to cross-sectional area;

[0047] S04: Adjust the length of the first washer 150 and / or the length of the second washer 160 so that the difference in length between the first bearing shaft group and the second bearing shaft group meets the length adjustment difference value.

[0048] In some embodiments, the formula for calculating the theoretical deformation of the first spacer 120 and / or the second spacer 140 is as follows:

[0049]

[0050] in, F is the theoretical deformation, l is the design length of the first spacer 120 and / or the design length of the second spacer 140, E is the stiffness of the first spacer 120 and / or the stiffness of the second spacer 140, and A is the design cross-sectional area of ​​the first spacer 120 and / or the design cross-sectional area of ​​the second spacer 140.

[0051] To ensure uniform force distribution on the first bearing assembly 110 and the second bearing assembly 130, the bearing mechanism 100 is designed such that the preset load borne by the first bearing shaft assembly and the preset load borne by the second bearing shaft assembly are equal, the designed length borne by the first bearing shaft assembly and the designed length borne by the second bearing shaft assembly are equal, the designed length of the first spacer 120 and the designed length of the second spacer 140 are equal, the stiffness of the first spacer 120 and the stiffness of the second spacer 140 are equal, and the designed cross-sectional area of ​​the first spacer 120 and the designed cross-sectional area of ​​the second spacer 140 are also equal. Therefore, the theoretical deformation of the first spacer 120 and the theoretical deformation of the second spacer 140 are equal.

[0052] In practical applications, the actual load borne by the first bearing shaft assembly is F1, the actual load borne by the second bearing shaft assembly is F2, the actual length of the first spacer 120 is l1, the actual length of the second spacer 140 is l2, the actual cross-sectional area of ​​the first spacer 120 is A1, the actual cross-sectional area of ​​the second spacer 140 is A2, the actual stiffness of the first spacer 120 is E1, the actual stiffness of the second spacer 140 is E2, and the deformation of the first spacer 120 under load is... 1. The actual deformation of the second spacer 140 under stress is: 2.

[0053] To ensure that the first bearing assembly 110 and the second bearing assembly 130 are subjected to uniform force, the actual load borne by the first bearing shaft assembly and the actual load borne by the second bearing shaft assembly must be equal (F1=F2), that is, the deformation of the first spacer 120 under force is equal to the actual deformation of the second spacer 140 under force. 1= 2) Since the actual stiffness E1 of the first spacer 120 and the actual stiffness E2 of the second spacer 140 are equal (E1=E2), the ratio of the actual length of the first spacer 120 to the actual cross-sectional area of ​​the first spacer 120 must be equal to the ratio of the actual length of the second spacer 140 to the actual cross-sectional area of ​​the second spacer 140 (l1 / A1=l2 / A2).

[0054] During the production process, due to machining errors, the actual cross-sectional area A1 of the first spacer 120 and the actual cross-sectional area A2 of the second spacer 140 may not be equal, and the actual length l1 of the first spacer 120 and the actual length l2 of the second spacer may also not be equal. Furthermore, due to assembly errors, the actual total length of the first bearing shaft assembly and the actual total length of the second bearing shaft assembly may also not be equal. As a result, when the bearing mechanism bears a load, it is impossible to ensure that the first bearing shaft assembly and the second bearing shaft assembly are subjected to uniform force. Therefore, the uneven force distribution caused by machining errors can be compensated by adjusting the length of the first washer 150 and / or the length of the second washer 160, thereby adjusting the actual total length of the first bearing shaft assembly and / or the actual total length of the second bearing shaft assembly.

[0055] When designing the bearing mechanism 100, the preset total load borne by the bearing mechanism 100 is Nt. Therefore, the preset loads on the first bearing shaft group and the second bearing shaft group are respectively... The deformation of the first and second bearing shaft groups is equal and both are Then, the force on the first or second bearing shaft group for every 1μm deformation is... .

[0056] However, assuming that the total length L1 of the first bearing shaft group is 10 μm longer than the total length L2 of the second bearing shaft group (i.e., L1 - L2 = 10 μm), the first bearing shaft group will be subjected to the load first. At this time, the second bearing shaft group is not subjected to load.

[0057] In the axial direction of the bearing mechanism 100, when the first bearing shaft assembly is compressed to the level of the first bearing assembly 110 and the second spacer 140, the first bearing shaft assembly and the second bearing bearing are simultaneously subjected to force. At this time, the magnitude of the force on the first bearing shaft assembly is... The force on the second bearing shaft assembly is about half of the total load. That is, the first and second bearing shafts deform synchronously, with the same amount of deformation. This leads to the following relationship:

[0058]

[0059] Further derivation yields:

[0060]

[0061] The final result is:

[0062]

[0063] When the actual cross-sectional area of ​​the first spacer 120 is not equal to that of the second spacer 140 due to errors, the value of l0 that needs to be adjusted can be calculated by the proportional relationship obtained from the final result above, where l0 is the length difference between the total length of the first bearing shaft group and the total length of the second bearing shaft group.

[0064] Based on the above theory, this application also provides an illustrative embodiment. This embodiment is only for the convenience of readers to understand and use the error adjustment method provided in this application, and does not limit the actual structure.

[0065] The bearing mechanism 100 is designed and calculated to withstand a total load of 8T. The first and second bearing shaft groups are evenly distributed with the total load in a 1:1 ratio, and each bears a component force of 4T. Therefore, the total design length of the first spacer 120 is 0.115m, the material stiffness of the first spacer 120 is 210GPa, and the cross-sectional area of ​​the first spacer 120 is 421mm². 2 Thus, the theoretical deformation of the first spacer 120 is 52 μm; correspondingly, the total design length of the second spacer 140 is 0.115 m, the material stiffness of the second spacer 140 is 210 GPa, and the cross-sectional area of ​​the second spacer 140 is 421 mm². 2 Thus, the theoretical deformation of the second spacer 140 is 52 μm.

[0066] When actual manufacturing errors exist in this illustrative embodiment, the cross-sectional area of ​​the first spacer 120 and the cross-sectional area of ​​the second spacer 140 differ as follows: At this time, it is necessary to calculate the length difference that the first spacer 120 and the second spacer 140 need to be adjusted so that the first spacer 120 and the second spacer 140 equally share the total load of 8T. Substituting the above You can get Thus, l0 = 1.3 μm, which means that the total length of the first spacer 120 needs to be 1.3 μm longer than the total length of the second spacer 140.

[0067] This application aims to provide a bearing mechanism 100, including a first bearing assembly 110, a first spacer 120, a second bearing assembly 130, a second spacer 140, a first washer 150, and a second washer 160. The first bearing assembly 110 is sleeved outside the first spacer 120. The second bearing assembly 130 is axially spaced from the first bearing assembly 110. The second spacer 140 is sleeved outside the second bearing assembly 130. The two ends of the first washer 150 abut against the first bearing assembly 110 and the second spacer 140, respectively. The first washer 150 is circumferentially disposed around the second washer 160, and the two ends of the second washer 160 abut against the first spacer 120 and the second bearing assembly 130, respectively. When the first bearing assembly 110 and the first spacer 120 are subjected to an external force toward the second bearing assembly 130, the first bearing assembly 110 transmits a portion of the external force to the second spacer 140 through the first washer 150, and the first spacer 120 transmits the other portion of the external force to the second bearing assembly 130 through the second washer 160, so that the first bearing assembly 110 and the second bearing assembly 130 are subjected to force evenly. Through this structure, the first bearing assembly 110 and the second bearing assembly 130 can share the axial load, reducing the impact on bearing operation.

[0068] Based on the same inventive concept, this application also provides a transmission device 1000, which includes a bearing mechanism 100 and a main shaft 500. The structure and function of the bearing mechanism 100 and the main shaft 500 can be referred to the above embodiments, and will not be repeated here.

[0069] Based on the same inventive concept, this application also provides an error adjustment method for a transmission device 1000, which is applied to the bearing mechanism 100 and the main shaft. For the error adjustment method, please refer to the above embodiments, which will not be described in detail here.

[0070] It should be noted that while preferred embodiments of this application are provided in the specification and accompanying drawings, this application can be implemented in many different forms and is not limited to the embodiments described herein. These embodiments are not intended to impose additional limitations on the content of this application; their purpose is to provide a more thorough and comprehensive understanding of the disclosure of this application. Furthermore, the above-described technical features can be combined with each other to form various embodiments not listed above, all of which are considered to be within the scope of this application's specification. Moreover, those skilled in the art can make improvements or modifications based on the above description, and all such improvements and modifications should fall within the protection scope of the appended claims.

Claims

1. A bearing mechanism, characterized in that, include: First bearing assembly; The first spacer sleeve, the first bearing assembly is sleeved outside the first spacer sleeve; The second bearing assembly is arranged axially at a distance from the first bearing assembly; The second spacer is sleeved outside the second bearing assembly; A first washer, the two ends of which abut against the first bearing assembly and the second spacer, respectively; along the axial direction of the first bearing assembly, the first washer includes a first abutting portion and a second abutting portion connected together, the end of the first abutting portion away from the second abutting portion abuts against the first bearing assembly, the end of the second abutting portion away from the first abutting portion abuts against the second spacer, and the radial cross-sectional area of ​​the first abutting portion is larger than the radial cross-sectional area of ​​the second abutting portion; The second washer, wherein the first washer is disposed around the second washer, and the two ends of the second washer respectively abut against the first spacer and the second bearing assembly; Along the axial direction of the second bearing assembly, the second washer includes a third abutting portion and a fourth abutting portion connected together. The end of the third abutting portion opposite to the fourth abutting portion abuts against the first spacer, and the end of the fourth abutting portion opposite to the third abutting portion abuts against the second bearing assembly. The radial cross-sectional area of ​​the third abutting portion is smaller than the radial cross-sectional area of ​​the fourth abutting portion. When the first bearing assembly and the first spacer are subjected to an external force toward the second bearing assembly, the first bearing assembly transmits a portion of the external force to the second spacer through the first washer, and the first spacer transmits another portion of the external force to the second bearing assembly through the second washer, so that the first bearing assembly and the second bearing assembly are subjected to force evenly.

2. The bearing mechanism according to claim 1, characterized in that, Along the axial direction of the first bearing assembly, the first washer includes a first abutting portion, a first middle portion, and a second abutting portion connected in sequence. The end of the first abutting portion opposite to the second abutting portion abuts against the first bearing assembly, and the end of the second abutting portion opposite to the first abutting portion abuts against the second spacer. The radial cross-sectional area of ​​the first abutting portion is larger than the radial cross-sectional area of ​​the second abutting portion, and the radial cross-sectional area of ​​the first middle portion decreases sequentially from the end opposite to the second abutting portion toward the other end. Along the axial direction of the second bearing assembly, the second washer includes a third abutting portion, a second middle portion, and a fourth abutting portion connected in sequence. The end of the third abutting portion opposite to the fourth abutting portion abuts against the first spacer, and the end of the fourth abutting portion opposite to the third abutting portion abuts against the second bearing assembly. The radial cross-sectional area of ​​the third abutting portion is smaller than the radial cross-sectional area of ​​the fourth abutting portion, and the radial cross-sectional area of ​​the second middle portion increases sequentially from the end opposite to the fourth abutting portion toward the other end.

3. The bearing mechanism according to claim 2, characterized in that, The first middle portion includes an inner side surface, which is disposed facing the second washer; The second middle portion includes an outer side surface, which is disposed facing the first washer; The inner side and the outer side are respectively set at an angle relative to the axial direction of the first bearing assembly, and a gap is provided between the inner side and the outer side.

4. The bearing mechanism according to any one of claims 1-3, characterized in that, The sum of the lengths of the first bearing assembly, the first washer, and the second spacer is L1; the sum of the lengths of the first spacer, the second washer, and the second bearing assembly is L2; ​​the cross-sectional area of ​​the first spacer is A1; and the cross-sectional area of ​​the second spacer is A2. L1, A1, L2, and A2 satisfy: L1 / A1 = L2 / A2.

5. The bearing mechanism according to any one of claims 1-3, characterized in that, The bearing mechanism further includes a third spacer, which is sleeved outside the first bearing assembly; and / or The bearing mechanism further includes a fourth spacer, and the second bearing assembly is sleeved outside the fourth spacer.

6. A transmission device, characterized in that, include: spindle; The bearing mechanism as described in any one of claims 1-4, wherein the bearing mechanism is sleeved on the main shaft.

7. The transmission device according to claim 6, characterized in that, The transmission device also includes a housing, which is fitted over the bearing mechanism; The transmission device further includes a bearing ring disposed within the housing, with both ends of the bearing ring abutting against the housing and the second bearing assembly of the bearing mechanism, respectively; and / or The transmission device also includes a bushing, which is sleeved on the main shaft, and one end of the bushing abuts against the fourth spacer of the bearing mechanism.

8. A method for adjusting the error of a bearing mechanism, characterized in that, A method for adjusting the bearing mechanism according to any one of claims 1-7, the bearing mechanism comprising a first bearing shaft assembly and a second bearing shaft assembly, the first bearing shaft assembly comprising a first bearing assembly, a first washer, and a second spacer, the second bearing shaft assembly comprising the first spacer, the second washer, and the second bearing assembly; the method comprising: The theoretical deformation of the first spacer and / or the second spacer under a preset load is calculated. Measure the cross-sectional area of ​​the first spacer and the cross-sectional area of ​​the second spacer, and calculate the ratio of the cross-sectional area of ​​the first spacer to the cross-sectional area of ​​the second spacer. The length adjustment difference is calculated based on the theoretical deformation and the ratio of the cross-sectional area. Adjust the length of the first washer and / or the length of the second washer so that the difference in length between the first bearing shaft group and the second bearing shaft group satisfies the length adjustment difference value.

9. The method according to claim 8, characterized in that, The formula for calculating the theoretical deformation is: in, Let F be the theoretical deformation, l be the design length of the first spacer and / or the design length of the second spacer, E be the stiffness of the first spacer and / or the stiffness of the second spacer, and A be the design cross-sectional area of ​​the first spacer and / or the design cross-sectional area of ​​the second spacer.

10. The method according to claim 8, characterized in that, The formula for calculating the length adjustment difference is: Where A1 is the actual cross-sectional area of ​​the first spacer and A2 is the actual cross-sectional area of ​​the second spacer. The theoretical deformation amount is... Adjust the difference for the length.

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