Bearing spacer ring and electric spindle having the same

Abstract

The utility model provides a kind of bearing spacer ring and electric spindle with it. Among them, bearing spacer ring includes: spacer ring component, including first spacer ring and stop structure, first spacer ring has mounting recess, stop structure includes first stop portion, first stop portion movably set in mounting recess, to extrude pre-tightening bearing outer ring under the hydraulic oil of entering via mounting recess push;Second spacer ring is set in first spacer ring, and second spacer ring includes movably set second stop portion, and second stop portion extrudes pre-tightening bearing inner ring under the hydraulic oil of entering first spacer ring push.The utility model effectively solves the problem that the pre-tightening mode of spring loading or manual adjustment in prior art cannot realize synchronous, uniform pre-tightening of bearing inner and outer rings.

Description

Technical Field

[0001] This utility model relates to the field of electric spindle technology, and more specifically, to a bearing spacer and an electric spindle having the same. Background Technology

[0002] Currently, in high-precision mechanical systems, electric spindles are key components, and their design and maintenance significantly impact the overall performance and lifespan of the equipment. Specifically, electric spindles directly drive the spindle via a built-in motor, eliminating the gear, belt, or coupling transmissions of traditional spindles, thus reducing the transmission chain length to zero. They are widely used in high-end manufacturing in fields such as precision molds, automobiles, shipbuilding, and aerospace. Among these applications, the bearing preload of the electric spindle is crucial for ensuring its high precision and stable operation.

[0003] In the existing technology, the bearing preload of electric spindles is mainly achieved by spring loading or manual adjustment. However, the above preload methods lack precise control of the preload force, and cannot achieve synchronous and uniform preload on the inner and outer rings of the bearing. This leads to unstable preload effect and difficulty in accurately adjusting the preload force to adapt to the real-time changes of the inner and outer rings of the bearing. Utility Model Content

[0004] The main objective of this invention is to provide a bearing spacer and an electric spindle having the same, so as to solve the problem that the preload method using spring loading or manual adjustment in the prior art cannot achieve synchronous and uniform preload on the inner and outer rings of the bearing.

[0005] To achieve the above objectives, according to one aspect of the present invention, a bearing spacer is provided, comprising: a spacer assembly including a first spacer and a stop structure, the first spacer having a mounting recess, the stop structure including a first stop portion movably disposed within the mounting recess to press against a preloaded bearing outer ring under the pressure of hydraulic oil entering through the mounting recess; and a second spacer disposed within the first spacer, the second spacer including a movably disposed second stop portion, the second stop portion pressing against a preloaded bearing inner ring under the pressure of hydraulic oil entering the first spacer.

[0006] Furthermore, the bearing spacer also includes a first control valve for controlling the flow rate and / or velocity of the hydraulic oil entering the mounting recess to adjust the force applied by the first stop portion to the outer ring of the bearing; and / or, the bearing spacer also includes a second control valve for controlling the flow rate and / or velocity of the hydraulic oil entering the first spacer to adjust the force applied by the second stop portion to the inner ring of the bearing.

[0007] Furthermore, the first stop portion has a first mating inclined surface, and the stop structure also includes a push portion, which has a push surface and a second mating inclined surface. Hydraulic oil entering the mounting recess is used to push the push surface, and the push surface and the second mating inclined surface are set at an angle. The second mating inclined surface and the first mating inclined surface are set parallel to each other, so that when the hydraulic oil pushes the push surface, the second mating inclined surface pushes the first mating inclined surface to move toward the outer ring of the bearing.

[0008] Furthermore, there are two second mating inclined surfaces and two first stop portions, with the two first stop portions located on both sides of the pushing portion; wherein, the two first stop portions are arranged in a one-to-one correspondence with the two second mating inclined surfaces, and each first stop portion presses against the outer ring of the bearing of the corresponding bearing.

[0009] Furthermore, the included angle C between the two second mating inclined planes is greater than or equal to 45° and less than or equal to 60°.

[0010] Furthermore, the first spacer ring has a first mounting hole for mounting the shaft core, and the second spacer ring is disposed in the first mounting hole; the mounting recess includes a mounting groove, the pusher portion is movably disposed in the mounting groove, and the second mating inclined surface contacts the groove wall of the mounting groove; wherein, along the direction from the outer peripheral surface of the first spacer ring to the central axis of the first mounting hole, the groove width of the mounting groove gradually decreases.

[0011] Furthermore, the mounting recess also includes a second mounting hole communicating with the mounting groove, and the first stop is movably disposed in the second mounting hole. The second mounting hole is inclined relative to the first mounting hole. The angle D between the extension direction of the second mounting hole and the extension direction of the first mounting hole is greater than or equal to 45° and less than or equal to 60°.

[0012] Furthermore, the mounting recess also includes: a buffer hole for buffering hydraulic oil, and a second mounting hole communicating with the mounting groove through the buffer hole; wherein, the diameter of the second mounting hole is smaller than the diameter of the buffer hole, and there is a preset distance between the first stop and the wall of the buffer hole.

[0013] Furthermore, there is a first distance between the bottom of the mounting groove and the central axis of the first mounting hole, and a second distance between the wall of the buffer hole near the central axis of the first mounting hole and the central axis of the first mounting hole, wherein the first distance is less than the second distance.

[0014] Furthermore, the pushing part is annular or arc-shaped, and the cross-section of the pushing part is an inverted trapezoid or inverted triangle; and / or, the first stop part is annular or arc-shaped, and the cross-section of the first stop part is quadrilateral.

[0015] Furthermore, the second spacer ring has a third mounting hole for mounting the shaft core, and a second stop portion is disposed on at least a portion of the hole wall of the third mounting hole; wherein, the second stop portion is annular or arc-shaped, and the width W1 of the second stop portion is greater than or equal to 0.1 mm and less than or equal to 0.5 mm.

[0016] Furthermore, the width W2 of the push surface is greater than or equal to 0.1 mm and less than or equal to 0.5 mm; and / or, the distance L between the push surface and the central axis of the first mounting hole is greater than or equal to 0.1 mm and less than or equal to 0.5 mm.

[0017] Furthermore, the bearing spacer also includes: a first detection device for detecting the position of the bearing outer ring and / or the compressive force borne by the bearing outer ring, so as to adjust the flow rate and / or velocity of the hydraulic oil entering the mounting recess according to the detection result of the first detection device; and / or a second detection device for detecting the position of the bearing inner ring and / or the compressive force borne by the bearing inner ring, so as to adjust the flow rate and / or velocity of the hydraulic oil entering the first spacer according to the detection result of the second detection device.

[0018] According to another aspect of the present invention, an electric spindle is provided, comprising: a spindle core; a bearing housing; two bearings disposed within the bearing housing; a bearing spacer disposed between the two bearings for applying a compressive preload force to the outer ring and / or inner ring of at least one bearing; the spindle core passing through the bearing spacer and the two bearings; wherein the bearing spacer is the aforementioned bearing spacer.

[0019] Furthermore, the bearing housing has a first inlet channel for supplying hydraulic oil, the first inlet channel being connected to the mounting recess, the shaft core having a mounting port and a second inlet channel for supplying hydraulic oil, the second inlet channel being connected to the first mounting hole of the first spacer ring through the mounting port, and the second stop portion of the bearing spacer ring being movably disposed within the mounting port.

[0020] By applying the technical solution of this utility model, a mounting recess is provided in the first spacer ring. A first stop portion moves relative to the mounting recess under the push of hydraulic oil to compress the outer ring of the preload bearing. A second stop portion compresses the inner ring of the preload bearing under the push of hydraulic oil. That is, the first spacer ring compresses the outer ring of the preload bearing, and the second spacer ring compresses the inner ring of the preload bearing. The two spacers are used in combination, and the hydraulic oil evenly pushes the first and second spacers, thereby precisely controlling the preload force on the outer and inner rings of the bearing. This solves the problem that existing preload methods using spring loading or manual adjustment cannot achieve synchronous and uniform preload on the inner and outer rings of the bearing. Compared with traditional spring preload or manual adjustment methods, the bearing spacer ring in this application not only significantly improves the uniformity of the preload force and reduces bearing misalignment and vibration caused by uneven preload force, but also improves the overall operational stability of the electric spindle. Meanwhile, when hydraulic oil enters through the mounting recess and pushes the first stop, and when hydraulic oil enters the first spacer and pushes the second stop, the preload status of the bearing outer and inner rings can be monitored in real time by monitoring the pressure change of the hydraulic oil, so that the preload process can be monitored and adjusted in real time. Attached Figure Description

[0021] The accompanying drawings, which form part of this application, are used to provide a further understanding of the present invention. The illustrative embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an undue limitation of the present invention. In the drawings:

[0022] Figure 1 A partial cross-sectional view of an embodiment of the bearing spacer according to the present invention applied to an electric spindle is shown;

[0023] Figure 2 It shows Figure 1 Enlarged schematic diagram of point A on the bearing spacer ring;

[0024] Figure 3 It shows Figure 1 Exploded view of the electric spindle in the middle;

[0025] Figure 4 It shows Figure 1 A cross-sectional view of the spacer assembly of the bearing spacer;

[0026] Figure 5 It shows Figure 4 Enlarged schematic diagram of point B of the spacer ring assembly;

[0027] Figure 6 It shows Figure 5 A cross-sectional view of the first spacer ring of the spacer ring assembly;

[0028] Figure 7 It shows Figure 1 A cross-sectional view of the second spacer of the bearing spacer;

[0029] Figure 8 It shows Figure 1 A sectional view of the bearing housing.

[0030] The above figures include the following reference numerals:

[0031] 10. Spacer assembly; 11. First spacer; 111. Mounting recess; 1111. Mounting groove; 1112. Second mounting hole; 1113. Buffer hole; 112. First mounting hole; 12. Stop structure; 121. First stop part; 122. First mating slope; 123. Pushing part; 1231. Pushing surface; 1232. Second mating slope;

[0032] 20. Bearing; 21. Bearing outer ring; 22. Bearing inner ring;

[0033] 30. Second spacer ring; 31. Second stop; 32. Third mounting hole;

[0034] 40. Shaft core; 41. Mounting port; 42. Second liquid inlet channel;

[0035] 50. First detection device;

[0036] 60. Bearing housing; 61. First liquid inlet channel;

[0037] 70. Bearing spacer. Detailed Implementation

[0038] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0039] It should be noted that, unless otherwise specified, all technical and scientific terms used in this application have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains.

[0040] In this utility model, unless otherwise stated, directional terms such as "upper" and "lower" are generally used in relation to the direction shown in the accompanying drawings, or in relation to the vertical, perpendicular, or gravitational direction; similarly, for ease of understanding and description, "left" and "right" are generally used in relation to the left and right shown in the accompanying drawings; "inner" and "outer" refer to the inner and outer contours of each component itself, but the above directional terms are not used to limit this utility model.

[0041] To address the problem that existing technologies using spring loading or manual adjustment cannot achieve synchronous and uniform preload on the inner and outer rings of a bearing, this application provides a bearing spacer and an electric spindle having the same.

[0042] like Figures 1 to 8As shown, the bearing spacer includes a spacer assembly 10 and a second spacer 30. The spacer assembly 10 includes a first spacer 11 and a stop structure 12. The first spacer 11 has a mounting recess 111, and the stop structure 12 includes a first stop portion 121, which is movably disposed within the mounting recess 111 to press against the preloaded bearing outer ring 21 under the pressure of hydraulic oil entering through the mounting recess 111. The second spacer 30 is disposed within the first spacer 11 and includes a movably disposed second stop portion 31, which press against the preloaded bearing inner ring 22 under the pressure of hydraulic oil entering the first spacer 11.

[0043] Applying the technical solution of this embodiment, the first spacer 11 has a mounting recess 111, and the first stop 121 moves relative to the mounting recess 111 under the push of hydraulic oil to push and compress the outer ring 21 of the preload bearing. The second stop 31 compresses the inner ring 22 of the preload bearing under the push of hydraulic oil. That is, the first spacer 11 is used to compress the outer ring 21 of the preload bearing, and the second spacer 30 is used to compress the inner ring 22 of the preload bearing. The two are used in combination and the first spacer 11 and the second spacer 30 are pushed evenly by hydraulic oil, thereby precisely controlling the preload force on the outer ring 21 and the inner ring 22 of the bearing. This solves the problem that the preload method using spring loading or manual adjustment in the prior art cannot achieve synchronous and uniform preload on the inner and outer rings of the bearing. Compared with the traditional spring preload or manual adjustment method, the bearing spacer in this embodiment not only significantly improves the uniformity of the preload force and reduces the bearing off-center load and vibration caused by uneven preload force, but also improves the overall operating stability of the electric spindle. Meanwhile, when hydraulic oil enters through the mounting recess 111 and pushes the first stop 121, and when hydraulic oil enters the first spacer 11 and pushes the second stop 31, the preload status of the bearing outer ring 21 and the bearing inner ring 22 can be understood in real time by monitoring the pressure change of the hydraulic oil, so that the preload process can be monitored and adjusted in real time.

[0044] In this embodiment, if the preload changes due to temperature or other reasons during the operation of the electric spindle, the preload can be corrected in real time by adjusting the supply of hydraulic oil, ensuring that the bearing 20 is always in the optimal preload state. This avoids performance degradation or equipment damage caused by changes in preload, extends the service life of the bearing 20, and enhances the operational reliability of the electric spindle.

[0045] Optionally, the bearing spacer also includes a first control valve for controlling the flow rate and / or velocity of hydraulic oil entering the mounting recess 111 to adjust the force applied by the first stop portion 121 to the outer ring 21 of the bearing; and / or, the bearing spacer also includes a second control valve for controlling the flow rate and / or velocity of hydraulic oil entering the first spacer 11 to adjust the force applied by the second stop portion to the inner ring 22 of the bearing.

[0046] like Figure 2 and Figure 5 As shown, the first stop portion 121 has a first mating inclined surface 122, and the stop structure 12 also includes a pushing portion 123. The pushing portion 123 has a pushing surface 1231 and a second mating inclined surface 1232. Hydraulic oil entering the mounting recess 111 is used to push the pushing surface 1231. The pushing surface 1231 and the second mating inclined surface 1232 are set at an angle. The second mating inclined surface 1232 is parallel to the first mating inclined surface 122, so that when the hydraulic oil pushes the pushing surface 1231, the second mating inclined surface 1232 pushes the first mating inclined surface 122 toward the outer ring 21 of the bearing. In this way, the parallel arrangement of the first mating inclined surface 122 of the first stop portion 121 and the second mating inclined surface 1232 of the pushing portion 123, as well as the design of the angle between the pushing surface 1231 and the second mating inclined surface 1232, can realize the amplification and uniform transmission of force by utilizing the principle of inclined surfaces. When the hydraulic oil pushes the push surface 1231, due to the inclined plane principle, the above-mentioned thrust will be converted into a larger thrust on the second mating inclined plane 1232. At the same time, through the guiding effect of the inclined plane, the thrust is evenly transmitted to the first mating inclined plane 122, and then acts on the outer ring 21 of the bearing.

[0047] In this embodiment, the pressure of hydraulic oil applied to the push surface 1231 enables rapid response and precise control of the preload. The aforementioned design of the push part 123 allows for rapid adjustment of the preload when hydraulic oil flow and pressure change, while the inclined surface further enhances the sensitivity of the adjustment. This allows for more rapid adaptation to changes in the electric spindle's operating state, maintaining the bearing in an ideal preload state, reducing performance fluctuations caused by untimely preload adjustment, and thus improving the electric spindle's operational stability and machining accuracy.

[0048] In this embodiment, a bearing spacer is disposed between two bearings 20. There are two second mating inclined surfaces 1232 and two first stop portions 121, located on opposite sides of the pushing portion 123. Each first stop portion 121 corresponds to one of the two second mating inclined surfaces 1232, with each first stop portion 121 pressing against the outer ring 21 of its corresponding bearing. By providing two first stop portions 121 and corresponding second mating inclined surfaces 1232 on both sides of the pushing portion 123, the bearing spacer achieves bidirectional symmetrical pre-tightening of the outer ring 21 between the two bearings 20. This ensures that regardless of which side of the bearing spacer is subjected to hydraulic pressure, the two first stop portions 121 are uniformly and simultaneously pushed towards the outer ring 21, generating a synchronous pre-tightening force. This effectively prevents the bearing from bearing asymmetrical forces, reduces off-center loading, and improves the bearing's load-bearing capacity and operational stability, which is crucial for ensuring the balanced operation of the electric spindle and extending its service life.

[0049] Specifically, two first stop portions 121 and two second mating inclined surfaces 1232 are provided, thereby enabling independent adjustment of the preload for each bearing outer ring 21 under different operating conditions. In practical applications, this allows the electric spindle to flexibly adjust the preload of each bearing 20 according to specific loads, temperature changes, or other external conditions to achieve optimal operating conditions.

[0050] Optionally, the included angle C between the two second mating inclined surfaces 1232 is greater than or equal to 45° and less than or equal to 60°. Thus, when the included angle C of the inclined surfaces is between 45° and 60°, the force perpendicular to the jacking surface 1231 can be effectively converted into a horizontal thrust along the inclined surfaces to both sides. Within this angle range, the conversion efficiency of the inclined surfaces is high, enabling the generation of a large preload output with a relatively small hydraulic oil pressure input. Simultaneously, the selection of the included angle C must also consider the stability and reliability of the structure. If the angle is too large (close to 60°), it will lead to poor contact between the inclined surfaces, uneven transmission of influence, and also increase the complexity of the structure and the potential failure rate; if the angle is too small (close to 45°), the force conversion efficiency will decrease, and under certain operating conditions, it may lead to uneven force distribution, affecting the preload effect.

[0051] In this embodiment, the included angle C between the two second mating inclined planes 1232 is 50°. This ensures that the included angle C is chosen to guarantee both effective force conversion and amplification, while maintaining the stability and reliability of the structure.

[0052] It should be noted that the included angle C between the two second mating inclined surfaces 1232 is not limited to this value and can be adjusted according to working conditions and usage requirements. Optionally, the included angle C between the two second mating inclined surfaces 1232 can be 48°, 52°, 55°, or 58°.

[0053] like Figure 1 and Figure 6As shown, the first spacer 11 has a first mounting hole 112 for mounting the shaft core 40, and the second spacer 30 is disposed within the first mounting hole 112. The mounting recess 111 includes a mounting groove 1111, and the pusher 123 is movably disposed within the mounting groove 1111. The second mating inclined surface 1232 contacts the groove wall of the mounting groove 1111. The width of the mounting groove 1111 gradually decreases along the direction from the outer circumference of the first spacer 11 to the central axis of the first mounting hole 112. This gradual decrease in the width of the mounting groove 1111 along the direction from the outer circumference of the first spacer 11 to the central axis of the first mounting hole 112 ensures that when the hydraulic oil pushes the pusher 123, the thrust is precisely guided along a predetermined path. As the groove width decreases, the inclined surface effect becomes more significant, allowing the thrust generated by the hydraulic oil to be evenly distributed onto the second mating inclined surface 1232. Through the interaction between the second mating inclined surface 1232 and the first mating inclined surface 122, the force is efficiently transmitted to the bearing outer ring 21. Meanwhile, the precise force guidance and distribution mentioned above helps to achieve uniform bearing preload, reduce potential off-center loads during bearing operation, and improve the operational stability and machining accuracy of the electric spindle.

[0054] In this embodiment, the aforementioned design of the mounting groove 1111 enables the system to self-regulate the flow path and rate of hydraulic oil to a certain extent, in order to cope with changes in preload requirements caused by factors such as temperature variations and load fluctuations during actual operation. When the bearing preload status needs adjustment, changes in hydraulic oil pressure and flow rate will automatically adjust the position of the jacking part 123 through the guiding effect of the mounting groove 1111, achieving rapid fine-tuning of the preload force without complex external intervention. Simultaneously, the gradual width design of the groove enhances the structural strength of the mounting groove 1111, improves the smoothness and stability of the jacking part 123's movement, reduces preload failures caused by structural deformation or jamming, and improves the reliability and durability of the entire preload system.

[0055] like Figure 6As shown, the mounting recess 111 also includes a second mounting hole 1112 communicating with the mounting groove 1111. The first stop 121 is movably disposed within the second mounting hole 1112. The second mounting hole 1112 is inclined relative to the first mounting hole 112. The angle D between the extension direction of the second mounting hole 1112 and the extension direction of the first mounting hole 112 is greater than or equal to 45° and less than or equal to 60°. In this way, the inclined arrangement of the second mounting hole 1112 and the angle D between it and the first mounting hole 112 being set within the range of 45° to 60° can efficiently convert the vertical thrust transmitted by the hydraulic oil via the pusher 123 into a preload force along the outer ring 21 of the bearing by utilizing the principle of inclined plane torque. Meanwhile, the selection of the aforementioned angle range ensures the efficiency of force conversion and the uniformity of force distribution, enabling sufficient and uniform preload even with a small input force. By precisely controlling the included angle D, the magnitude of the preload can be finely adjusted to meet the preload requirements of the electric spindle under different operating conditions, thereby improving the preload accuracy and control flexibility of the system.

[0056] In this embodiment, the extension direction of the second mounting hole 1112 forms an angle D of 50° with the extension direction of the first mounting hole 112. This angle D helps optimize the internal spatial layout of the electric spindle, achieving a compact and lightweight structure. Within a limited installation space, by tilting the second mounting hole 1112, not only are the space limitations that might be encountered when pre-tightening the bearing directly in the axial or radial direction avoided, but the three-dimensional space is also fully utilized, reducing the volume occupied by the pre-tightening assembly.

[0057] It should be noted that the angle D between the extension direction of the second mounting hole 1112 and the extension direction of the first mounting hole 112 is not limited to this value and can be adjusted according to working conditions and usage requirements. Optionally, the angle D between the extension direction of the second mounting hole 1112 and the extension direction of the first mounting hole 112 can be 48°, 52°, 55°, or 58°.

[0058] like Figure 6As shown, the mounting recess 111 also includes a buffer hole 1113, which is used to buffer hydraulic oil. The second mounting hole 1112 communicates with the mounting groove 1111 through the buffer hole 1113. The diameter of the second mounting hole 1112 is smaller than the diameter of the buffer hole 1113, and there is a preset distance between the first stop portion 121 and the wall of the buffer hole 1113. Thus, the buffer hole 1113 stabilizes the hydraulic oil pressure. During the pre-tightening process, the hydraulic oil is transferred from the push portion 123 through the mounting groove 1111 and then through the second mounting hole 1112 to the first stop portion 121. During this process, the hydraulic oil is buffered within the buffer hole 1113, preventing pressure fluctuations caused by rapid flow. This stable oil pressure environment helps improve the control accuracy of the pre-tightening force, ensuring a smooth and accurate pre-tightening process. The buffer hole 1113 plays a crucial role, especially in scenarios requiring fine adjustment of the pre-tightening force.

[0059] In this embodiment, by differentiating the diameters of the second mounting hole 1112 and the buffer hole 1113, and by setting a preset distance between the first stop portion 121 and the wall of the buffer hole 1113, the hydrodynamic characteristics of the hydraulic oil during transmission can be optimized. A smaller diameter of the second mounting hole 1112 increases the resistance to oil flow, while a larger diameter of the buffer hole 1113 helps reduce the resistance of the oil during the buffering stage, forming a "throttling-buffering" fluid control mechanism. This reduces energy loss of the hydraulic oil during transmission, improves the overall efficiency of the hydraulic system, and plays a positive role in reducing the energy consumption of the electric spindle and improving its operational economy. Simultaneously, the buffer hole 1113 and its connection to the second mounting hole 1112 allow the system to respond more quickly to changes in hydraulic oil pressure when adjusting the preload. When it is necessary to increase or decrease the preload, the hydraulic oil can quickly adjust its state within the buffer hole 1113, thereby rapidly affecting the movement of the first stop part 121, improving the response speed of the preload system. The preset distance setting avoids direct contact between the first stop part 121 and the hole wall of the buffer hole 1113, reducing friction and wear between moving parts, and improving the operational reliability and durability of the entire system.

[0060] In this embodiment, there is a first distance between the bottom of the mounting groove 1111 and the central axis of the first mounting hole 112, and a second distance between the wall of the buffer hole 1113 near the central axis of the first mounting hole 112 and the central axis of the first mounting hole 112. The first distance is smaller than the second distance. Thus, because the first distance between the bottom of the mounting groove 1111 and the central axis of the first mounting hole 112 is smaller than the second distance between the wall of the buffer hole 1113 and the central axis, the pushing part 123 can reach the initial position required for bearing preload more quickly under the action of hydraulic oil. When hydraulic oil enters the mounting groove 1111 from the pushing part 123, the smaller first distance means that the hydraulic oil pressure can be quickly converted into a thrust on the first stop part 121, thereby preloading the outer ring 21 of the bearing. At the same time, the larger second distance of the buffer hole 1113 provides a buffer space, which helps to stabilize the hydraulic oil pressure, reduce the impact of pressure fluctuations on the preload control accuracy, and ensure precise control of the preload.

[0061] Specifically, during the pre-tightening process, the design of a smaller first distance than the second distance effectively reduces the impact on the structural stability of the bearing and the first spacer 11 caused by sudden changes in pre-tightening force. When the first stop 121 begins its pre-tightening action, the smaller first distance concentrates the force, reducing the risk of deformation of the first spacer 11 due to excessive torque. Simultaneously, the larger second distance of the buffer hole 1113 provides a buffer space for the hydraulic oil, helping to absorb and disperse the mechanical impact generated by pre-tightening force adjustment, protecting the bearing and the first spacer 11 from damage, and extending the service life of the equipment.

[0062] Optionally, the pusher portion 123 is annular or arc-shaped, and its cross-section is an inverted trapezoid or inverted triangle; and / or, the first stop portion 121 is annular or arc-shaped, and its cross-section is quadrilateral. In this way, the pusher portion 123 adopts an inverted trapezoidal or inverted triangular cross-section design, gradually reducing its contact area with the hydraulic oil. This helps to evenly distribute the hydraulic oil pressure across the entire contact surface of the pusher portion 123, avoiding excessive local pressure and ensuring uniform force transmission. In particular, the annular or arc-shaped pusher portion 123 can more evenly apply preload to the bearing outer ring 21, reducing bearing misalignment caused by uneven force distribution and enhancing the stability and reliability of the preload process. Simultaneously, the quadrilateral cross-section of the first stop portion 121 provides a larger contact area, helping to disperse the reaction force applied to the bearing outer ring 21 during the preload process, reducing local stress concentration on the first spacer ring 11, and improving the mechanical strength and structural stability of the first spacer ring 11. The annular or arc-shaped first stop 121 can match the contact surface of the bearing outer ring 21, further improving the uniform distribution of force and ensuring the consistency of bearing preload effect.

[0063] In this embodiment, the pusher portion 123 is annular, and its cross-section is an inverted triangle. The first stop portion 121 is annular, and its cross-section is rectangular. This design of the pusher portion 123 and the first stop portion 121 allows for better adaptation to the internal spatial layout of the electric spindle, optimizes the space utilization efficiency of the bearing spacer, reduces the structural volume, and contributes to the lightweight and miniaturized design of the electric spindle. Simultaneously, the inverted triangular design of the pusher portion 123 enables it to move smoothly along a preset track under hydraulic pressure, avoiding potential movement jamming due to structural complexity, optimizing the motion performance of the pretensioning components, and thus improving the operational convenience and ease of maintenance of the entire pretensioning system.

[0064] like Figure 7 As shown, the second spacer 30 has a third mounting hole 32 for mounting the shaft core 40, and a second stop 31 is disposed on at least a portion of the hole wall of the third mounting hole 32; wherein, the second stop 31 is annular or arc-shaped, and the width W1 of the second stop 31 is greater than or equal to 0.1 mm and less than or equal to 0.5 mm. Thus, setting the width W1 of the second stop 31 between 0.1 mm and 0.5 mm ensures a more uniform distribution of contact force between the second stop 31 and the bearing inner ring 22 during the rotation of the shaft core 40. The selection of the width W1 not only provides sufficient friction to achieve preload, but also avoids uneven force distribution or poor contact problems that may be caused by the stop being too wide or too narrow. At the same time, the annular or arc-shaped second stop 31 can well match the shape of the bearing inner ring 22, ensuring a uniform distribution of preload force in the circumferential direction of the bearing inner ring 22, which helps reduce the radial runout of the bearing.

[0065] Specifically, the width W1 of the second stop 31 is set within the aforementioned range, which helps reduce mechanical wear between the second spacer 30 and the shaft core 40, and the bearing inner ring 22. If the width W1 is too narrow, it may increase contact pressure, leading to rapid wear of the contact surfaces; while if it is too wide, it may increase unnecessary frictional resistance, affecting the bearing's operating efficiency and stability. Meanwhile, a width W1 of 0.1 mm to 0.5 mm is an ideal range that balances contact pressure and frictional resistance, ensuring effective preload while minimizing wear between moving parts, thereby improving the overall operational reliability of the electric spindle and extending the equipment's service life. Furthermore, the annular or arc-shaped design of the second stop 31 can reduce stress damage that may be caused by localized force concentration, further enhancing the durability of the bearing preload system.

[0066] In this embodiment, the second stop portion 31 is annular, and the width W1 of the second stop portion 31 is 0.25mm.

[0067] It should be noted that the width W1 of the second stop portion 31 is not limited to this value and can be adjusted according to working conditions and usage requirements. Optionally, the width W1 of the second stop portion 31 is 0.15mm, or 0.18mm, or 0.22mm, or 0.28mm, or 0.30mm, or 0.35mm, or 0.38mm, or 0.40mm, or 0.45mm, or 0.48mm.

[0068] Optionally, the width W2 of the push surface 1231 is greater than or equal to 0.1 mm and less than or equal to 0.5 mm; and / or, the distance L between the push surface 1231 and the central axis of the first mounting hole 112 is greater than or equal to 0.1 mm and less than or equal to 0.5 mm. This precise control of the width W2 of the push surface 1231 helps ensure more uniform and stable force transmission. Setting the width W2 between 0.1 mm and 0.5 mm ensures that the contact area between the push surface and the outer ring 21 of the bearing is appropriate, providing sufficient contact surface to ensure stable force transmission while avoiding uneven force distribution or insufficient contact caused by excessive width or narrowness. Simultaneously, the above settings allow for precise control of the hydraulic oil pressure and flow rate, enabling very fine adjustment of the preload of the inner and outer rings of the bearing, ensuring precise matching of the preload force.

[0069] In this embodiment, the width W2 of the push surface 1231 is 0.25 mm, and the distance L between the push surface 1231 and the central axis of the first mounting hole 112 is 0.25 mm. By setting the distance L between the push surface 1231 and the central axis of the first mounting hole 112 to 0.25 mm, the mechanical clearance between the push part 123 and the first spacer ring 11 is reduced, which helps to improve the structural compactness of the entire pretensioning system. A smaller distance L means that the stroke of the push part 123 is shorter when responding to changes in hydraulic oil pressure, resulting in a faster response speed and improved dynamic performance of the pretensioning system.

[0070] like Figure 1As shown, the bearing spacer also includes a first detection device 50, which is used to detect the position of the bearing outer ring 21 and / or the compressive force borne by the bearing outer ring 21, so as to adjust the flow rate and / or velocity of the hydraulic oil entering the mounting recess 111 according to the detection result of the first detection device 50; and / or, the bearing spacer also includes a second detection device, which is used to detect the position of the bearing inner ring 22 and / or the compressive force borne by the bearing inner ring 22, so as to adjust the flow rate and / or velocity of the hydraulic oil entering the first spacer 11 according to the detection result of the second detection device. In this way, through the real-time monitoring of the first detection device 50 and the second detection device, the flow rate and velocity of the hydraulic oil can be dynamically adjusted according to the actual position changes and compressive force borne by the bearing outer ring 21 and bearing inner ring 22 during the operation of the electric spindle. The preload can be finely adjusted in real time according to factors such as actual load and temperature changes during the operation of the electric spindle, ensuring that the preload is always in the most suitable state, avoiding premature wear or performance degradation of the bearing due to improper preload, and significantly improving the operating efficiency and service life of the bearing. Meanwhile, the aforementioned configuration of the detection device enables the bearing spacer to have self-adjusting capabilities, automatically adjusting the preload based on the detection data without manual intervention.

[0071] In this embodiment, the bearing spacer also includes a first detection device 50 and a second detection device. The first detection device 50 is used to detect the position of the bearing outer ring 21 and / or the compressive force borne by the bearing outer ring 21, so as to adjust the flow rate and / or flow velocity of the hydraulic oil entering the mounting recess 111 according to the detection result of the first detection device 50. The second detection device is used to detect the position of the bearing inner ring 22 and / or the compressive force borne by the bearing inner ring 22, so as to adjust the flow rate and / or flow velocity of the hydraulic oil entering the first spacer 11 according to the detection result of the second detection device.

[0072] like Figure 1 As shown, this application also provides an electric spindle, including a spindle core 40, a bearing housing 60, two bearings 20, and a bearing spacer 70. The two bearings 20 are disposed within the bearing housing 60, and the bearing spacer 70 is disposed between the two bearings 20 to apply a compressive preload force to the outer ring 21 and / or inner ring 22 of at least one bearing 20; the spindle core 40 passes through the bearing spacer 70 and the two bearings 20. The bearing spacer 70 is the aforementioned bearing spacer 70.

[0073] Specifically, by placing the bearing spacer 70 between the two bearings 20 and directly applying preload to the outer ring 21 and inner ring 22 of the bearings, the preload is ensured to be directly and uniformly transmitted to the bearings, avoiding uneven force transmission and poor preload effect that may occur in traditional preload methods. The bearing spacer 70 can independently adjust the preload on the inner and outer rings of the bearings as needed, thereby ensuring that the bearings maintain the optimal preload state under different working conditions, improving the operating accuracy and stability of the electric spindle. At the same time, designing the bearing spacer 70 as a component integrating the preload function, rather than a separate preload device, simplifies and compacts the internal structure of the electric spindle. On the one hand, the presence of the bearing spacer 70 reduces the need for additional preload components, making the assembly of the electric spindle simpler, reducing weight and size, and improving the flexibility and portability of the equipment. On the other hand, the tight fit between the bearing spacer 70 and the shaft core 40, and the direct control of the preload on the inner and outer rings of the bearings, reduces energy loss caused by mechanical backlash or long force transmission paths, improving the response speed and operating efficiency of the electric spindle.

[0074] like Figure 1 and Figure 8 As shown, the bearing housing 60 has a first inlet channel 61 for hydraulic oil to enter, which communicates with the mounting recess 111. The shaft core 40 has a mounting port 41 and a second inlet channel 42 for hydraulic oil to enter. The second inlet channel 42 communicates with the first mounting hole 112 of the first spacer 11 through the mounting port 41. The second stop portion 31 of the bearing spacer 70 is movably disposed within the mounting port 41. This arrangement of the first inlet channel 61 and the second inlet channel 42 allows hydraulic oil to flow directly and effectively into the critical parts of the bearing spacer 70, namely the mounting recess 111 and the first mounting hole 112, to preload the inner and outer rings of the bearing via the second stop portion 31, ensuring immediate response of the preload force and minimal energy loss. Simultaneously, the movable arrangement of the second stop portion 31 allows the preload force to vary with the flow rate and velocity of the hydraulic oil, thereby enabling precise adjustment of the preload amount of the inner and outer rings according to real-time operating conditions.

[0075] In this embodiment, the system monitors the flow rate and velocity of the hydraulic oil, as well as the displacement and stress on the inner and outer rings of the bearing, using a detection device. Based on the monitoring results, the system can react promptly and dynamically adjust the preload. This self-monitoring and feedback mechanism significantly improves the intelligence level of the preload system, enabling it to proactively respond to various external environmental changes (such as temperature fluctuations and load changes), ensuring that the preload is always maintained at the optimal level. This prevents premature bearing failure due to improper preload and extends the service life of the electric spindle.

[0076] As can be seen from the above description, the embodiments of this utility model achieve the following technical effects:

[0077] The first spacer ring has a mounting recess. A first stop, driven by hydraulic oil, moves relative to the mounting recess to press and compress the outer ring of the preload bearing. A second stop, also driven by hydraulic oil, compresses the inner ring of the preload bearing. In other words, the first spacer ring compresses the outer ring of the preload bearing, and the second spacer ring compresses the inner ring. The combined use of these two spacers, with hydraulic oil evenly pushing both rings, precisely controls the preload force on the outer and inner rings of the bearing. This solves the problem in existing technologies where spring loading or manual adjustment methods cannot achieve synchronous and uniform preload on the inner and outer rings of the bearing. Compared to traditional spring preload or manual adjustment methods, the bearing spacer rings in this application not only significantly improve the uniformity of the preload force and reduce bearing misalignment and vibration caused by uneven preload force, but also enhance the overall operational stability of the electric spindle. Meanwhile, when hydraulic oil enters through the mounting recess and pushes the first stop, and when hydraulic oil enters the first spacer and pushes the second stop, the preload status of the bearing outer and inner rings can be monitored in real time by monitoring the pressure change of the hydraulic oil, so that the preload process can be monitored and adjusted in real time.

[0078] Obviously, the embodiments described above are only some embodiments of this utility model, and not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort should fall within the protection scope of this utility model.

[0079] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0080] It should be noted that the terms "first," "second," etc., used in the specification, claims, and accompanying drawings of this application are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate so that the embodiments of this application described herein can be implemented in sequences other than those illustrated or described herein.

[0081] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A bearing spacer, characterized in that, include: The spacer assembly (10) includes a first spacer (11) and a stop structure (12), the first spacer (11) having a mounting recess (111) and the stop structure (12) including a first stop portion (121) movably disposed within the mounting recess (111) to press against the preload bearing outer ring (21) under the pressure of hydraulic oil entering through the mounting recess (111). The second spacer (30) is disposed inside the first spacer (11). The second spacer (30) includes a movable second stop (31). The second stop (31) is pushed by hydraulic oil entering the first spacer (11) to squeeze the preload bearing inner ring (22).

2. The bearing spacer according to claim 1, characterized in that, The bearing spacer also includes a first control valve, which controls the flow rate and / or velocity of the hydraulic oil entering the mounting recess (111) to adjust the force exerted by the first stop (121) on the outer ring (21) of the bearing; and / or, The bearing spacer also includes a second control valve, which is used to control the flow rate and / or velocity of the hydraulic oil entering the first spacer (11) to adjust the force applied by the second stop to the inner ring (22) of the bearing.

3. The bearing spacer according to claim 1, characterized in that, The first stop portion (121) has a first mating inclined surface (122), and the stop structure (12) further includes: The pusher (123) has a pusher surface (1231) and a second mating inclined surface (1232). Hydraulic oil entering the mounting recess (111) is used to push the pusher surface (1231). The pusher surface (1231) and the second mating inclined surface (1232) are set at an angle. The second mating inclined surface (1232) is arranged parallel to the first mating inclined surface (122) so that when the hydraulic oil pushes the push surface (1231), the second mating inclined surface (1232) pushes the first mating inclined surface (122) toward the outer ring (21) of the bearing.

4. The bearing spacer according to claim 3, characterized in that, There are two second mating inclined surfaces (1232) and two first stop portions (121). The two first stop portions (121) are located on both sides of the push portion (123). The two first stop portions (121) are arranged in a one-to-one correspondence with the two second mating inclined surfaces (1232), and each first stop portion (121) presses against the outer ring (21) of the bearing corresponding to it.

5. The bearing spacer according to claim 4, characterized in that, The included angle C between the two second mating inclined planes (1232) is greater than or equal to 45° and less than or equal to 60°.

6. The bearing spacer according to claim 3, characterized in that, The first spacer (11) has a first mounting hole (112) for mounting the shaft core (40), and the second spacer (30) is disposed in the first mounting hole (112); the mounting recess (111) includes a mounting groove (1111), the pusher (123) is movably disposed in the mounting groove (1111), and the second mating inclined surface (1232) contacts the groove wall of the mounting groove (1111); wherein, along the direction from the outer peripheral surface of the first spacer (11) to the central axis of the first mounting hole (112), the groove width of the mounting groove (1111) gradually decreases.

7. The bearing spacer according to claim 6, characterized in that, The mounting recess (111) further includes a second mounting hole (1112) communicating with the mounting groove (1111). The first stop (121) is movably disposed in the second mounting hole (1112). The second mounting hole (1112) is inclined relative to the first mounting hole (112). The extension direction of the second mounting hole (1112) forms an angle D greater than or equal to 45° and less than or equal to 60° with the extension direction of the first mounting hole (112).

8. The bearing spacer according to claim 7, characterized in that, The mounting recess (111) also includes: A buffer hole (1113) is used to buffer hydraulic oil, and the second mounting hole (1112) is connected to the mounting groove (1111) through the buffer hole (1113); The diameter of the second mounting hole (1112) is smaller than that of the buffer hole (1113), and there is a preset distance between the first stop (121) and the hole wall of the buffer hole (1113).

9. The bearing spacer according to claim 8, characterized in that, The bottom of the mounting groove (1111) has a first distance from the central axis of the first mounting hole (112), and the wall of the buffer hole (1113) near the central axis of the first mounting hole (112) has a second distance from the central axis of the first mounting hole (112), wherein the first distance is less than the second distance.

10. The bearing spacer according to claim 3, characterized in that, The pushing part (123) is annular or arc-shaped, and the cross-section of the pushing part (123) is an inverted trapezoid or inverted triangle; and / or, the first stop part (121) is annular or arc-shaped, and the cross-section of the first stop part (121) is quadrilateral.

11. The bearing spacer according to claim 1, characterized in that, The second spacer (30) has a third mounting hole (32) for mounting the shaft core (40), and the second stop (31) is disposed on at least a portion of the hole wall of the third mounting hole (32); wherein the second stop (31) is annular or arc-shaped, and the width W1 of the second stop (31) is greater than or equal to 0.1 mm and less than or equal to 0.5 mm.

12. The bearing spacer according to claim 6, characterized in that, The width W2 of the push surface (1231) is greater than or equal to 0.1 mm and less than or equal to 0.5 mm; and / or the distance L between the push surface (1231) and the central axis of the first mounting hole (112) is greater than or equal to 0.1 mm and less than or equal to 0.5 mm.

13. The bearing spacer according to claim 1, characterized in that, The bearing spacer also includes: A first detection device (50) is used to detect the position of the bearing outer ring (21) and / or the compressive force borne by the bearing outer ring (21), so as to adjust the flow rate and / or velocity of the hydraulic oil entering the mounting recess (111) according to the detection result of the first detection device (50); and / or, The second detection device is used to detect the position of the bearing inner ring (22) and / or the compressive force borne by the bearing inner ring (22), so as to adjust the flow rate and / or velocity of the hydraulic oil entering the first spacer (11) according to the detection result of the second detection device.

14. An electric spindle, characterized in that, include: Shaft core (40); Bearing housing (60); Two bearings (20) are disposed within the bearing housing (60); A bearing spacer (70) is disposed between two of the bearings (20) for applying a compressive preload to the outer ring (21) and / or inner ring (22) of at least one of the bearings (20); the shaft (40) passes through the bearing spacer (70) and the two bearings (20); wherein the bearing spacer (70) is the bearing spacer (70) according to any one of claims 1 to 13.

15. The electric spindle according to claim 14, characterized in that, The bearing housing (60) has a first inlet channel (61) for hydraulic oil to enter, the first inlet channel (61) is connected to the mounting recess (111), the shaft core (40) has a mounting port (41) and a second inlet channel (42) for hydraulic oil to enter, the second inlet channel (42) is connected to the first mounting hole (112) of the first spacer (11) through the mounting port (41), and the second stop (31) of the bearing spacer (70) is movably disposed in the mounting port (41).

Images