Bearing mechanism, transmission device, and error adjustment method for bearing mechanism

Abstract

The embodiment of the invention relates to the technical field of oil extraction equipment, in particular to a bearing mechanism, a transmission device and an error adjustment method of the bearing mechanism, and the bearing mechanism comprises a first bearing pack, a first spacer bush, a second bearing pack, a second spacer bush, a first gasket and a second gasket. The first bearing set is sleeved outside the first spacer bush, the second bearing set and the first bearing set are arranged in a spaced mode, the second bearing set is sleeved outside the second bearing set, and the two ends of the first gasket abut against the first bearing set and the second spacer bush respectively. The first gasket is annularly arranged outside the second gasket, and the two ends of the second gasket abut against the first spacer bush and the second bearing set correspondingly. When the first bearing pack and the first spacer bush bear external force towards the second bearing pack, the first bearing pack transmits a part of the external force to the second spacer bush through the first gasket, and the first spacer bush transmits the other part of the external force to the second bearing pack through the second gasket, so that the first bearing pack and the second bearing pack are uniformly stressed; therefore, the service life of the bearing mechanism is prolonged.

Description

Technical Field

[0001] The embodiments of the present application relate to the technical field of oil production equipment, and in particular to a bearing mechanism, a transmission device, and a method for adjusting the error of the bearing mechanism. Background Art

[0002] Bearing is an important component in modern mechanical equipment. Its main function is to support the mechanical rotating body, reduce the friction coefficient during its movement, and ensure its rotation accuracy. Bearing groups are used in a variety of transmission devices, which are subject to axial, radial and circumferential forces during use.

[0003] In the process of realizing the present application, the inventors found that when the transmission device is subjected to large axial forces, multiple bearing groups are often installed in series along the main shaft. However, this method will cause the first bearing group to be subjected to excessive force, affecting the operation of the bearing. Summary of the invention

[0004] The embodiments of the present application provide a bearing mechanism, a transmission device and a method for adjusting the error of a bearing mechanism, which can improve the current situation in which multiple bearing groups are installed in series along the main shaft, which causes excessive force on the first bearing group and affects the operation of the bearing.

[0005] In order to solve the above technical problems, a technical solution adopted in the present application is: to provide a bearing mechanism, including a first bearing group, a first spacer, a second bearing group, a second spacer, a first washer and a second washer. The first bearing group is sleeved outside the first spacer. The second bearing group is spaced apart from the first bearing group in the axial direction. The second spacer is sleeved outside the second bearing group. The two ends of the first washer abut against the first bearing group and the second spacer, respectively. The first washer is arranged outside the second washer, and the two ends of the second washer abut against the first spacer and the second bearing group, respectively. When the first bearing group and the first spacer are subjected to an external force toward the second bearing group, the first bearing group transfers part of the external force to the second spacer through the first washer, and the first spacer transfers another part of the external force to the second bearing group through the second washer, so that the first bearing group and the second bearing group are subjected to uniform force.

[0006] In some embodiments, along the axial direction of the first bearing group, the first washer includes a first abutment portion and a second abutment portion connected to each other, an end of the first abutment portion facing away from the second abutment portion abuts against the first bearing group, an end of the second abutment portion facing away from the first abutment portion abuts against the second spacer sleeve, and a radial cross-sectional area of ​​the first abutment portion is greater than a radial cross-sectional area of ​​the second abutment portion; and / or along the axial direction of the second bearing group, the second washer includes a third abutment portion and a fourth abutment portion connected to each other, an end of the third abutment portion facing away from the fourth abutment portion abuts against the first spacer sleeve, an end of the fourth abutment portion facing away from the third abutment portion abuts against the second bearing group, and a radial cross-sectional area of ​​the third abutment portion is smaller than a radial cross-sectional area of ​​the fourth abutment portion.

[0007] In some embodiments, along the axial direction of the first bearing group, 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 facing away from the second abutting portion abuts against the first bearing group, the end of the second abutting portion facing away from the first abutting portion abuts against the second spacer sleeve, the radial cross-sectional area of ​​the first abutting portion is greater than the radial cross-sectional area of ​​the second abutting portion, and the radial cross-sectional area of ​​the first middle portion decreases from the end facing away from the second abutting portion toward the other end. Along the axial direction of the second bearing group, 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 facing away from the fourth abutting portion abuts against the first spacer sleeve, the end of the fourth abutting portion facing away from the third abutting portion abuts against the second bearing group, the radial cross-sectional area of ​​the third abutting portion is less than the radial cross-sectional area of ​​the fourth abutting portion, and the radial cross-sectional area of ​​the second middle portion increases from the end facing away from the fourth abutting portion toward the other end.

[0008] In some embodiments, the first middle portion includes an inner side surface, and the inner side surface is disposed toward the second washer. The second middle portion includes an outer side surface, and the outer side surface is disposed toward the first washer. The inner side surface and the outer side surface are respectively disposed at an angle relative to the axial direction of the first bearing group, and a gap is provided between the inner side surface and the outer side surface.

[0009] In some embodiments, the sum of the lengths of the first bearing group, 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 group 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, A2 satisfy: L1 / A1=L2 / A2.

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

[0011] In order to solve the above technical problems, the present application also adopts another technical solution, providing a transmission device, which includes a main shaft and the above bearing mechanism, and the bearing mechanism is sleeved on the main shaft.

[0012] In some embodiments, the transmission device further comprises a housing, the housing is sleeved outside the bearing mechanism. The transmission device further comprises a seat ring, the seat ring is arranged in the housing, and the two ends of the seat ring abut against the housing and the second bearing group of the bearing mechanism respectively; and / or the transmission device further comprises a shaft sleeve, the shaft sleeve is sleeved on the main shaft, and one end of the shaft sleeve abuts against the fourth spacer sleeve of the bearing mechanism.

[0013] In order to solve the above technical problems, the present application also adopts another technical solution, providing a method for adjusting the error of the above bearing mechanism. The bearing mechanism includes a first bearing group and a second bearing group, the first bearing group includes the first bearing group, the first washer and the second spacer, and the second bearing group includes the first spacer, the second washer and the second bearing group. 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 cross-sectional area ratio of the cross-sectional area of ​​the first spacer to the cross-sectional area of ​​the second spacer. Calculating the length adjustment difference based on the theoretical deformation and the cross-sectional area ratio. Adjusting the length of the first washer and / or the length of the second washer so that the difference in length between the first load-bearing shaft group and the second load-bearing shaft group satisfies the length adjustment difference.

[0014] In some embodiments, the calculation formula of the theoretical deformation is:

[0015]

[0016] Among them, ΔL is the theoretical deformation, F is the preset load, l is the design length of the first spacer and / or the design length of the second spacer, E is the stiffness of the first spacer and / or the stiffness of the second spacer, and A is 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 length adjustment difference is calculated as follows:

[0018]

[0019] Wherein, A1 is the cross-sectional area of ​​the first spacer, A2 is the cross-sectional area of ​​the second spacer, Δl is the theoretical deformation, and l0 is the length adjustment difference.

[0020] The beneficial effect of the embodiment of the present application is that, different from the prior art, the embodiment of the present application provides a bearing mechanism, including a first bearing group, a first spacer, a second bearing group, a second spacer, a first washer and a second washer. The first bearing group is sleeved outside the first spacer. The second bearing group is spaced from the first bearing group in the axial direction. The second spacer is sleeved outside the second bearing group. The two ends of the first washer abut the first bearing group and the second spacer, respectively. The first washer is arranged outside the second washer, and the two ends of the second washer abut the first spacer and the second bearing group, respectively. When the first bearing group and the first spacer are subjected to an external force toward the second bearing group, the first bearing group transfers part of the external force to the second spacer through the first washer, and the first spacer transfers another part of the external force to the second bearing group through the second washer, so that the first bearing group and the second bearing group are subjected to uniform force. Through the above structure, the first bearing group and the second bearing group can share the load in the axial direction, reduce the impact on the operation of the bearing, so that the first bearing group and the second bearing group are subjected to uniform force, thereby extending the service life of the bearing mechanism. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings required for use in the embodiments of the present application will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on the drawings without paying creative work.

[0022] Figure 1 is a three-dimensional diagram of a bearing mechanism provided in one embodiment of the present application;

[0023] Figure 2 One embodiment of the present application provides Figure 1 A-side cross-sectional view;

[0024] Figure 3 One embodiment of the present application provides Figure 2 A magnified view of part B;

[0025] Figure 4 One embodiment of the present application provides Figure 2 Enlarged view of part C;

[0026] Figure 5 One embodiment of the present application provides Figure 2 A magnified view of the D portion;

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

[0028] The reference numerals are as follows:

[0029] Transmission 1000 Inside 1531 Bearing mechanism 100 Second gasket 160 First bearing group 110 The third contact portion 161 The third spacer 170 Fourth contact portion 162 First spacer 120 Second Central 163 Second bearing set 130 Outer side 1631 Fourth spacer 180 shell 200 Second spacer 140 Receiving cavity 210 First gasket 150 Limiting part 220 First contact portion 151 Seat 300 Second contact portion 152 Bushing 400 First Central 153 Spindle 500 DETAILED DESCRIPTION

[0030] In order to facilitate the understanding of the present application, the present application is described in more detail below in conjunction with the accompanying drawings and specific embodiments. It should be noted that when an element is described as "fixed to" another element, it can be directly on the other element, or there can be one or more centered elements therebetween. When an element is described as "connected to" another element, it can be directly connected to the other element, or there can be one or more centered elements therebetween. 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 those commonly understood by those skilled in the art to which this application belongs. The terms used in this specification and in the specification of this application are only for the purpose of describing specific embodiments and are not intended to limit this application. The term "and / or" used in this specification includes any and all combinations of one or more of the related listed items.

[0032] In the actual use of various transmission devices, when the transmission device is subjected to a large force in the axial direction, multiple sets of bearing groups are usually used to be sleeved on the main shaft, so that the axial force of the main shaft can be evenly distributed through multiple sets of bearing groups, so as to reduce the force borne by the main shaft and improve the operation stability of the main shaft. However, in this structure, the bearing group close to the source of the force will be subjected to a relatively large force, and the bearing group far away from the source of the force will be subjected to a relatively small force, which is easy to cause adverse conditions such as fatigue damage of some bearing groups, seriously affecting the transmission efficiency of the main shaft.

[0033] Based on this, this application adopts a technical solution, please refer to Figure 1 and Figure 2The present application provides a bearing mechanism 100, comprising a first bearing group 110, a first spacer sleeve 120, a second bearing group 130, a second spacer sleeve 140, a first washer 150 and a second washer 160. The first bearing group 110 is sleeved outside the first spacer sleeve 120. The second bearing group 130 is spaced apart from the first bearing group 110 in the axial direction. The second spacer sleeve 140 is sleeved outside the second bearing group 130. The two ends of the first washer 150 abut against the first bearing group 110 and the second spacer sleeve 140 respectively. The first washer 150 is arranged outside the second washer 160, and the two ends of the second washer 160 abut against the first spacer sleeve 120 and the second bearing group 130 respectively. When the first bearing group 110 and the first spacer sleeve 120 are subjected to an external force directed toward the second bearing group 130, the first bearing group 110 transfers part of the external force to the second spacer sleeve 140 through the first washer 150, and the first spacer sleeve 120 transfers another part of the external force to the second bearing group 130 through the second washer 160, so that the first bearing group 110 and the second bearing group 130 are subjected to uniform force.

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

[0035] In some embodiments, see Figure 2 and Figure 3, and in combination with other drawings. Along the axial direction of the first bearing group 110, the first washer 150 includes a first abutting portion 151 and a second abutting portion 152 connected to each other, one end of the first abutting portion 151 away from the second abutting portion 152 abuts against the first bearing group 110, one end of the second abutting portion 152 away from the first abutting portion 151 abuts against the second spacer 140, and the radial cross-sectional area of ​​the first abutting portion 151 is greater than the radial cross-sectional area of ​​the second abutting portion 152; and / or along the axial direction of the second bearing group 130, the second washer 160 includes a third abutting portion 161 and a fourth abutting portion 162 connected to each other, one end of the third abutting portion 161 away from the fourth abutting portion 162 abuts against the first spacer 120, one end of the fourth abutting portion 162 away from the third abutting portion 161 abuts against the second bearing group 130, and 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 can be understood that the radial cross-sectional area of ​​the first abutting portion 151 is relatively large in order to abut against the first bearing group 110, thereby increasing the contact area to reduce stress concentration, and the radial cross-sectional area of ​​the second abutting portion 152 should be less than or equal to the radial cross-sectional area of ​​the second spacer sleeve 140, so that when the component force is transmitted to the second spacer sleeve 140, the force will not be transmitted to the second bearing group 130 adjacent to the second spacer sleeve 140, thereby reducing the influence of the component force on the transmission path of the first bearing group 110, the first washer 150 and the second spacer sleeve 140 on the bearing effect of the second bearing group 130, thereby improving the stability of the load distribution. As for the third abutting portion 161 and the fourth abutting portion 162, the radial cross-sectional area of ​​the fourth abutting portion 162 is relatively large in order to abut against the second bearing group 130, thereby increasing the contact area and reducing the stress concentration phenomenon, and the radial cross-sectional area of ​​the third abutting portion 161 should be less than or equal to the radial cross-sectional area of ​​the first spacer sleeve 120, so that when the component force is transmitted from the first spacer sleeve 120 to the second washer 160, the second washer 160 will not be subjected to the component force from the first bearing group 110, thereby reducing the influence of the component force on the transmission path of the first spacer sleeve 120, the second washer 160, and the second bearing group 130 on the bearing effect of the second washer 160 and the second bearing group 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 a plurality of gaskets with different radial cross-sectional areas, or a gasket with a stepped profile. That is, it is only necessary to make the radial cross-sectional area of ​​the first abutting portion 151 larger than the radial cross-sectional area of ​​the second abutting portion 152 , and the radial cross-sectional area of ​​the fourth abutting portion 162 larger than the radial cross-sectional area of ​​the third abutting portion 161 .

[0036] In other embodiments, see Figure 3 and Figure 4, and in combination with other drawings. Along the axial direction of the first bearing group 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, one end of the first abutting portion 151 away from the second abutting portion 152 abuts against the first bearing group 110, and one end of the second abutting portion 152 away from the first abutting portion 151 abuts against the second spacer 140, the radial cross-sectional area of ​​the first abutting portion 151 is greater 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 from one end away from the second abutting portion 152 toward the other end. Along the axial direction of the second bearing group 130, the second washer 160 includes a third abutting portion 161, a second middle portion 163 and a fourth abutting portion 162 connected in sequence, the end of the third abutting portion 161 away from the fourth abutting portion 162 abuts against the first spacer 120, the end of the fourth abutting portion 162 away from the third abutting portion 161 abuts against the second bearing group 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, and the radial cross-sectional area of ​​the second middle portion 163 increases from one end away from the fourth abutting portion 162 toward the other end. Different from the above embodiment, the first middle portion 153 is provided so that there is no transition with a large difference in cross-sectional area inside the first washer 150, thereby reducing the stress concentration phenomenon inside the first washer 150. The second middle portion 163 is provided so that there is no transition with a large difference in cross-sectional area inside the second washer 160, thereby reducing the stress concentration phenomenon inside the second washer 160.

[0037] For further information, see Figure 4 , and in combination with other drawings. The first middle portion 153 includes an inner side surface 1531, and the inner side surface 1531 is arranged toward the second washer 160. The second middle portion 163 includes an outer side surface 1631, and the outer side surface 1631 is arranged toward the first washer 150. The inner side surface 1531 and the outer side surface 1631 are respectively arranged at an angle relative to the axial direction of the first bearing group 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 group 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 group 130, so that the first bearing group 110 and the second bearing group 130 bear the force together, and each bears the force independently, thereby optimizing the load distribution inside the bearing mechanism 100. Optionally, the inner side surface 1531 and the outer side surface 1631 may be surfaces parallel to each other, and the surfaces are curved surfaces.

[0038] In some embodiments, the sum of the lengths of the first bearing group 110, the first washer 150 and the second spacer 140 is L1, the sum of the lengths of the first spacer 120, the second washer 160 and the second bearing group 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, A2 satisfy: L1 / A1=L2 / A2. It is understandable that in the actual design, manufacturing and assembly process, errors are prone to occur between the various parts, thereby affecting 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 improving the force bearing capacity.

[0039] In some embodiments, see Figure 3 and Figure 4 , and in combination with other drawings. The bearing mechanism 100 further includes a third spacer 170, which is sleeved outside the first bearing group 110; and / or the bearing mechanism 100 further includes a fourth spacer 180, and the second bearing group 130 is sleeved outside the fourth spacer 180. By providing the third spacer 170, the third spacer 170 can separate the first bearing group 110 from other structures on the side of the first bearing group 110 away from the first spacer 120, thereby reducing friction resistance and improving transmission efficiency; by providing the fourth spacer 180, the fourth spacer 180 can separate the second bearing group 130 from other structures on the side of the second bearing group 130 away from the second spacer 140, thereby reducing friction resistance and improving transmission efficiency.

[0040] Based on the above bearing mechanism 100, please refer to Figure 1 and Figure 5 , and in combination with other drawings, in combination with the aforementioned transmission device 1000. The transmission device 1000 also includes a main shaft 500. The bearing mechanism 100 is sleeved on the main shaft 500, so that by setting the above-mentioned bearing mechanism 100, when the main shaft 500 is subjected to an external force in its axial direction, the above-mentioned bearing mechanism 100 can be fully utilized to evenly distribute the load, thereby improving the force bearing capacity of the main shaft 500 in the axial direction.

[0041] For the transmission 1000 described above, see Figure 1 and Figure 5, and in combination with other drawings, the transmission device 1000 also includes a housing 200, a seat ring 300 and a sleeve 400, and the housing 200 is sleeved outside the bearing mechanism 100. The transmission device 1000 also includes a seat ring 300, which is arranged in the housing 200, and the two ends of the seat ring 300 respectively abut the housing 200 and the second bearing group 130 of the bearing mechanism 100; and / or the transmission device 1000 also includes a sleeve 400, which is sleeved on the main shaft 500, and one end of the sleeve 400 abuts the fourth spacer 180 of the bearing mechanism 100. It is still necessary to explain that the housing 200 is provided with a receiving chamber 210, and the receiving chamber 210 is used to receive the above-mentioned main shaft 500 and the bearing mechanism 100. It can be understood that there is an avoidance space between the third spacer 170 and the housing 200, and another avoidance space is provided between the second spacer 140 and the housing 200. The first spacer 120 is at least partially concave toward the axial direction of the main shaft 500 to form an escape space, thereby reducing the contact area between the first spacer 120 and the housing 200, thereby reducing the circumferential friction resistance between the first spacer 120 and the housing 200, and reducing the wear on the first spacer 120 or the housing 200. Correspondingly, the second spacer 140 is at least partially concave toward the direction of the housing 200 to form an escape space, thereby reducing the contact area between the second spacer 140 and the main shaft 500, thereby reducing the friction resistance between the second spacer 140 and the main shaft 500, and reducing the wear on the second spacer 140 or the main shaft 500. It can be understood that lubricating oil, lubricant, etc. can also be added into the escape 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 understandable that there is also an escape space between the first spacer 120 and the main shaft 500, and between the fourth spacer 180 and the main shaft 500, which functions similarly to the above-mentioned escape space and will not be described one by one here. The seat ring 300 is arranged in the housing 200, and the two ends of the seat ring 300 abut the housing 200 and the second bearing group 130 of the bearing mechanism 100 respectively. By setting the seat ring 300, the bearing mechanism 100 is installed on the main shaft 500. Optionally, the housing 200 is also provided with a limiting portion 220, which is arranged on the side of the seat ring 300 away from the second bearing group 130 of the second bearing group 130, and further bears the force through the seat ring 300. The transmission device 1000 also includes a sleeve 400, which is sleeved on the main shaft 500, and one end of the sleeve 400 abuts against the fourth spacer 180 of the bearing mechanism 100, so that the bearing mechanism 100 is installed on the main shaft 500.

[0042] In combination with the housing 200 and the seat ring 300, please refer to Figure 5, and in combination with other drawings, the above force transmission path is further explained. The first bearing group 110, the first washer 150, and the second spacer 140 are connected to form a first load-bearing shaft group, so that the first load-bearing shaft group can share a part of the external force. Specifically, when the end of the first bearing group 110 away from the second bearing group 130 is subjected to an external force, a part of the force is transmitted to the housing 200 through the first bearing group 110, the first washer 150, and the second spacer 140. The first spacer 120, the second washer 160, and the second bearing group 130 are connected to form a second load-bearing shaft group, so that the second load-bearing shaft group can share another part of the external force. Specifically, another part of the force is transmitted to the housing 200 through the first spacer 120, the second washer 160, the second bearing group 130, and the seat ring 300; thereby optimizing the load distribution of the transmission device 1000.

[0043] As mentioned above, the bearing mechanism 100 will inevitably produce axial errors during the actual manufacturing and installation process. Therefore, the present application also provides an error adjustment method for the bearing mechanism 100, which is used to calculate the above-mentioned bearing mechanism 100. The bearing mechanism 100 includes the above-mentioned first load-bearing shaft group and the second load-bearing shaft group, wherein the first load-bearing shaft group includes the first bearing group 110, the first washer 150 and the second spacer sleeve 140, and the second load-bearing shaft group includes the first spacer sleeve 120, the second washer 2+0 and the second bearing group 130. For the specific calculation method, please refer to the following and Figure 6 , and combined with other accompanying drawings.

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

[0045] S02: measuring the cross-sectional area of ​​the first spacer 120 and the cross-sectional area of ​​the second spacer 140, and calculating the cross-sectional area ratio of the cross-sectional area of ​​the first spacer 120 to the cross-sectional area of ​​the second spacer 140;

[0046] S03: Calculate the length adjustment difference based on the theoretical deformation and the cross-sectional area ratio;

[0047] S04: Adjust the length of the first washer 150 and / or the length of the second washer 160 so that the difference between the lengths of the first load-bearing shaft group and the second load-bearing shaft group satisfies the length adjustment difference.

[0048] In some embodiments, the calculation formula of the theoretical deformation amount of the first spacer 120 and / or the second spacer 140 is:

[0049]

[0050] Among them, Δl is the theoretical deformation, F is the preset load, 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] In order to ensure that the first bearing group 110 and the second bearing group 130 are subjected to uniform force, when designing the bearing mechanism 100, it is designed that the preset load borne by the first bearing shaft group is equal to the preset load borne by the second bearing shaft group, the design length borne by the first bearing shaft group is equal to the design length borne by the second bearing shaft group, and the design length of the first spacer 120 is equal to the design length of the second spacer 140, the stiffness of the first spacer 120 is equal to the stiffness of the second spacer 140, and the design cross-sectional area of ​​the first spacer 120 is equal to the design cross-sectional area of ​​the second spacer 140. Therefore, the theoretical deformation of the first spacer 120 is equal to the theoretical deformation of the second spacer 140.

[0052] In actual applications, the actual load borne by the first load-bearing shaft group is F1, the actual load borne by the second load-bearing shaft group 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, the deformation of the first spacer 120 when subjected to force is Δl1, and the actual deformation of the second spacer 140 when subjected to force is Δl2.

[0053] If it is to ensure that the force on the first bearing group 110 and the second bearing group 130 is uniform, the actual load borne by the first load-bearing shaft group and the actual load borne by the second load-bearing shaft group shall be equal (F1=F2), that is, the deformation of the first spacer sleeve 120 when subjected to force is equal to the actual deformation of the second spacer sleeve 140 when subjected to force (Δl1=Δl2). Since the actual stiffness E1 of the first spacer sleeve 120 and the actual stiffness E2 of the second sleeve 140 are equal (E1=E2), it is actually necessary to satisfy that the ratio of the actual length of the first spacer sleeve 120 to the actual cross-sectional area of ​​the first spacer sleeve 120 is equal to the ratio of the actual length of the second spacer sleeve 140 to the actual cross-sectional area of ​​the second spacer sleeve 140 (l1 / A1=l2 / A2).

[0054] During the production process, due to processing errors, the actual cross-sectional area A1 of the first spacer 120 and the actual cross-sectional area A2 of the second spacer 140 are not equal, and the actual length l1 of the first spacer 120 and the actual length l2 of the second spacer are not equal. In addition, due to assembly errors, the actual total length of the first load-bearing shaft group and the actual total length of the second load-bearing shaft group are also not equal, which results in the inability to ensure that the first load-bearing shaft group and the second load-bearing shaft group are subjected to uniform force when the bearing mechanism is subjected to load. Therefore, the length of the first washer 150 and / or the length of the second washer 160 can be adjusted, and then the actual total length of the first load-bearing shaft group and / or the actual total length of the second load-bearing shaft group can be adjusted, thereby compensating for the uneven force caused by processing errors.

[0055] When designing the bearing mechanism 100, the preset total load borne by the bearing mechanism 100 is Nt, and the preset load borne by the first load-bearing shaft group and the preset load borne by the second load-bearing shaft group are respectively The deformation of the first bearing axis group and the second bearing axis group is equal and both are Δl, then the force of the first bearing axis group or the second bearing axis group for every 1μm deformation is

[0056] In the case of actual errors, assuming that the total length L1 of the first load-bearing shaft group is 10 μm longer than the total length L2 of the second load-bearing shaft group, that is, when L1-L2=10 μm, the first load-bearing shaft group will be loaded first. At this time, the second load-bearing shaft group is not subjected to load.

[0057] In the axial direction of the bearing mechanism 100, when the first load-bearing shaft group is compressed until the first bearing group 110 and the second spacer 140 are flush, the first load-bearing shaft group and the second load-bearing bearing are subjected to force at the same time. At this time, the magnitude of the force on the first load-bearing shaft group is The force on the second bearing shaft group is half of the total load. That is, the first load-bearing shaft group and the second load-bearing shaft group deform synchronously, and the deformation amounts are consistent. Then the following relationship is obtained:

[0058]

[0059] Further deduction yields:

[0060]

[0061] Finally we get:

[0062]

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

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

[0065] Design calculation for the bearing mechanism 100: The bearing mechanism 100 needs to bear a total load of 8T. The first load-bearing shaft group and the second load-bearing shaft group are evenly distributed with a total load in a ratio of 1:1, and each bears a component force of 4T. At this time, 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 421mm 2 , so that the theoretical deformation of the first spacer 120 is 52μm; accordingly, the total design length of the second spacer 140 is 0.115m, the material stiffness of the second spacer 140 is 210GPa, and the cross-sectional area of ​​the second spacer 140 is 421mm 2 , thus obtaining a theoretical deformation amount of the second spacer 140 of 52 μm.

[0066] When there is actually a processing error in this exemplary embodiment, the cross-sectional area of ​​the first spacer 120 and the cross-sectional area of ​​the second spacer 140 are: When the first spacer 120 and the second spacer 140 need to be adjusted, the length difference between them needs to be calculated so that the first spacer 120 and the second spacer 140 evenly share the total load of 8T. Substitute the above Can get Thus, l0=1.3 μm is obtained, that is, 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] The embodiment of the present application is intended to provide a bearing mechanism 100, comprising a first bearing group 110, a first spacer sleeve 120, a second bearing group 130, a second spacer sleeve 140, a first washer 150 and a second washer 160. The first bearing group 110 is sleeved outside the first spacer sleeve 120. The second bearing group 130 is spaced apart from the first bearing group 110 in the axial direction. The second spacer sleeve 140 is sleeved outside the second bearing group 130. The two ends of the first washer 150 abut against the first bearing group 110 and the second spacer sleeve 140 respectively. The first washer 150 is arranged outside the second washer 160, and the two ends of the second washer 160 abut against the first spacer sleeve 120 and the second bearing group 130 respectively. When the first bearing group 110 and the first spacer 120 are subjected to an external force directed toward the second bearing group 130, the first bearing group 110 transmits part of the external force to the second spacer 140 through the first washer 150, and the first spacer 120 transmits the other part of the external force to the second bearing group 130 through the second washer 160, so that the first bearing group 110 and the second bearing group 130 are subjected to uniform force. Through the above structure, the first bearing group 110 and the second bearing group 130 can share the axial load, reducing the impact on the operation of the bearings.

[0068] Based on the same inventive concept, the present application also provides a transmission device 1000, which includes a bearing mechanism 100 and a main shaft 500. The structures and functions of the bearing mechanism 100 and the main shaft 500 can be found in the above embodiments, which will not be described in detail here.

[0069] Based on the same inventive concept, the present application also provides an error adjustment method for a transmission device 1000, which is applied to the above-mentioned bearing mechanism 100 and the main shaft. For the error adjustment method, reference may be made to the above-mentioned embodiments, which will not be described one by one here.

[0070] It should be noted that the preferred embodiments of the present application are given in the specification and drawings of the present application. However, the present application can be implemented in many different forms and is not limited to the embodiments described in the specification. These embodiments are not used as additional limitations on the content of the present application. The purpose of providing these embodiments is to make the understanding of the disclosure of the present application more thorough and comprehensive. In addition, the above-mentioned technical features continue to be combined with each other to form various embodiments not listed above, which are all regarded as the scope of the description of the present application; further, for ordinary technicians in this field, they can be improved or transformed according to the above description, and all these improvements and transformations should belong to the scope of protection of the claims attached to the present application.

Claims

1. A bearing mechanism, characterized in that: include: The first bearing group; a first spacer sleeve, wherein the first bearing assembly is arranged outside the first spacer sleeve; a second bearing group, the second bearing group being spaced apart from the first bearing group in the axial direction; A second spacer sleeve, the second spacer sleeve is sleeved outside the second bearing group; a first washer, two ends of which respectively abut against the first bearing set and the second spacer sleeve; a second washer, wherein the first washer is disposed outside the second washer, and two ends of the second washer respectively abut against the first spacer sleeve and the second bearing group; When the first bearing group and the first spacer sleeve are subjected to an external force directed toward the second bearing group, the first bearing group transfers part of the external force to the second spacer sleeve through the first washer, and the first spacer sleeve transfers another part of the external force to the second bearing group through the second washer, so that the first bearing group and the second bearing group are subjected to uniform force.

2. The bearing mechanism according to claim 1, characterized in that: Along the axial direction of the first bearing group, the first washer includes a first abutting portion and a second abutting portion connected to each other, an end of the first abutting portion facing away from the second abutting portion abuts against the first bearing group, an end of the second abutting portion facing away from the first abutting portion abuts against the second spacer sleeve, and a radial cross-sectional area of ​​the first abutting portion is greater than a radial cross-sectional area of ​​the second abutting portion; and / or Along the axial direction of the second bearing group, the second washer includes a third abutment portion and a fourth abutment portion that are connected to each other, the end of the third abutment portion facing away from the fourth abutment portion abuts against the first spacer sleeve, the end of the fourth abutment portion facing away from the third abutment portion abuts against the second bearing group, and the radial cross-sectional area of ​​the third abutment portion is smaller than the radial cross-sectional area of ​​the fourth abutment portion.

3. The bearing mechanism according to claim 1, characterized in that: Along the axial direction of the first bearing group, the first washer includes a first abutting portion, a first middle portion and a second abutting portion connected in sequence, one end of the first abutting portion facing away from the second abutting portion abuts against the first bearing group, one end of the second abutting portion facing away from the first abutting portion abuts against the second spacer sleeve, a radial cross-sectional area of ​​the first abutting portion is greater than a radial cross-sectional area of ​​the second abutting portion, and a radial cross-sectional area of ​​the first middle portion decreases in sequence from one end facing away from the second abutting portion toward the other end; Along the axial direction of the second bearing group, the second washer includes a third abutment portion, a second middle portion and a fourth abutment portion connected in sequence, the end of the third abutment portion facing away from the fourth abutment portion abuts against the first spacer sleeve, the end of the fourth abutment portion facing away from the third abutment portion abuts against the second bearing group, the radial cross-sectional area of ​​the third abutment portion is smaller than the radial cross-sectional area of ​​the fourth abutment portion, and the radial cross-sectional area of ​​the second middle portion increases sequentially from the end facing away from the fourth abutment portion toward the other end.

4. The bearing mechanism according to claim 3, characterized in that: The first middle portion includes an inner side surface, and the inner side surface is disposed toward the second gasket; The second middle portion includes an outer side surface, and the outer side surface is disposed toward the first gasket; The inner side surface and the outer side surface are respectively arranged at an angle relative to the axial direction of the first bearing group, and a gap is provided between the inner side surface and the outer side surface.

5. The bearing mechanism according to any one of claims 1 to 4, characterized in that: The sum of the lengths of the first bearing group, 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 group 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, A2 satisfy: L1 / A1=L2 / A2.

6. The bearing mechanism according to any one of claims 1 to 4, characterized in that: The bearing mechanism further comprises a third spacer sleeve, wherein the third spacer sleeve is sleeved outside the first bearing assembly; and / or The bearing mechanism further comprises a fourth spacer sleeve, and the second bearing assembly is sleeved outside the fourth spacer sleeve.

7. A transmission device, characterized in that: include: Spindle; A bearing mechanism according to any one of claims 1 to 5, wherein the bearing mechanism is sleeved on the main shaft.

8. The transmission device according to claim 7, characterized in that: The transmission device further comprises a housing, wherein the housing is sleeved outside the bearing mechanism; The transmission device further comprises a seat ring, which is arranged in the housing, and two ends of the seat ring abut against the housing and the second bearing group of the bearing mechanism respectively; and / or The transmission device further comprises a shaft sleeve, which is sleeved on the main shaft, and one end of the shaft sleeve abuts against a fourth spacer sleeve of the bearing mechanism.

9. A method for adjusting the error of a bearing mechanism, characterized in that: Used to adjust the bearing mechanism according to any one of claims 1 to 8, the bearing mechanism comprising a first load-bearing shaft group and a second load-bearing shaft group, the first load-bearing shaft group comprising the first bearing group, the first washer and the second spacer, the second load-bearing shaft group comprising the first spacer, the second washer and the second bearing group; the method comprising: Calculating and obtaining a 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 cross-sectional area ratio of the cross-sectional area of ​​the first spacer to the cross-sectional area of ​​the second spacer; Calculate the length adjustment difference according to the theoretical deformation and the cross-sectional area ratio; The length of the first washer and / or the length of the second washer is adjusted so that the difference between the lengths of the first load-bearing shaft group and the second load-bearing shaft group satisfies the length adjustment difference.

10. The method according to claim 9, characterized in that The calculation formula of the theoretical deformation is: Among them, Δl is the theoretical deformation, F is the preset load, l is the design length of the first spacer and / or the design length of the second spacer, E is the stiffness of the first spacer and / or the stiffness of the second spacer, and A is the design cross-sectional area of ​​the first spacer and / or the design cross-sectional area of ​​the second spacer.

11. The method according to claim 9, characterized in that The calculation formula of the length adjustment difference is: Wherein, A1 is the actual cross-sectional area of ​​the first spacer, A2 is the actual cross-sectional area of ​​the second spacer, Δl is the theoretical deformation, and l0 is the length adjustment difference.

Images