Bearing preload adjustment device

Abstract

This application relates to a bearing preload adjustment device. The bearing preload adjustment device includes a pressure mechanism and a pressure detection mechanism. The output end of the pressure mechanism abuts against the outer ring end face of the bearing, thereby outputting pressure to the outer ring end face. The pressure detection mechanism is connected to at least one of the pressure mechanism and the bearing, and is used to detect the pressure signal of the pressure signal output by the pressure mechanism to the outer ring end face of the bearing. The pressure mechanism is communicatively connected to the pressure detection mechanism to acquire the pressure signal and adjust the output pressure value of the pressure signal output to the outer ring end face of the bearing according to the pressure signal. The pressure mechanism outputs pressure to the outer ring end face of the bearing and feeds back the pressure signal detected by the pressure detection mechanism to the pressure mechanism, realizing real-time adjustment of the bearing preload. This ensures that the rotor shaft maintains an appropriate preload, avoiding excessive or insufficient preload, thereby guaranteeing the bearing's stiffness, precision, and speed performance, reducing wear, and extending the bearing's service life.

Description

Technical Field

[0001] This application relates to the field of bearing preload adjustment technology, and in particular to bearing preload adjustment devices. Background Technology

[0002] Bearing preload can improve bearing stiffness, precision, and speed performance. A higher preload results in better bearing rigidity, higher precision, and also prevents vibration. However, excessive preload will generate a large amount of frictional heat, thus limiting bearing speed performance and accelerating wear on contact surfaces. To ensure bearing precision, lifespan, and speed performance, the preload should be moderate.

[0003] How to ensure that the bearing has an appropriate preload during use in order to maximize its performance is an urgent problem to be solved. Summary of the Invention

[0004] Based on this, a bearing preload adjustment device is provided, which enables the bearing to have an appropriate preload load.

[0005] Embodiments of this application disclose a bearing preload adjustment device, comprising:

[0006] A pressure mechanism, the output end of which is used to abut against the outer ring end face of the bearing, thereby outputting pressure to the outer ring end face of the bearing;

[0007] A pressure detection mechanism, which is connected to at least one of the pressure mechanism and the bearing, is used to detect a pressure signal that the pressure mechanism outputs pressure to the outer ring end face of the bearing.

[0008] The pressure mechanism is communicatively connected to the pressure detection mechanism to acquire the pressure signal and adjust the output pressure value of the pressure output to the outer ring end face of the bearing according to the pressure signal.

[0009] In one embodiment, the pressure mechanism includes:

[0010] A pressure element having an output portion, the output portion being used to form the output end;

[0011] A drive assembly, which is connected to the pressure element, is used to drive the output part of the pressure element to move axially along the bearing.

[0012] In one embodiment, a movable pressure plate is slidably connected inside the pressure member, and the movable pressure plate divides the inside of the pressure member into a first chamber and a second chamber;

[0013] The drive assembly includes a pressure source and a pressure transmission channel connecting the pressure source to the first chamber. The pressure source contains a pressure medium, and the pressure source and the first chamber communicate with each other through the pressure transmission channel.

[0014] In one embodiment, the bearing preload adjustment device further includes an oil reservoir for fixed connection with the rotor shaft, wherein the inner ring of the bearing is mounted on the rotor shaft;

[0015] The oil reservoir and the pressure component are slidably connected along the axial direction of the bearing.

[0016] In one embodiment, the pressure member is fixedly connected to a connecting frame, the oil reservoir is provided with an annular groove, the annular groove is arranged along the circumference of the bearing, and the connecting frame is slidably connected to the annular groove along the axial direction of the bearing.

[0017] In one embodiment, the oil storage chamber includes:

[0018] An oil inlet is provided for supplying cooling oil to the oil reservoir.

[0019] An oil outlet is provided, which is connected to the gap between the inner and outer rings of the bearing, for supplying cooling oil into the gap between the inner and outer rings of the bearing.

[0020] In one embodiment, multiple oil outlet holes are provided on the oil reservoir along the radial direction of the bearing;

[0021] The oil storage chamber is equipped with an oil baffle plate, which includes a fixed part, a telescopic part, and a shielding part. The fixed part and the shielding part are connected to both ends of the telescopic part in a radial direction along the bearing. When the oil storage chamber rotates with the rotor shaft, it generates centrifugal force. The shielding part responds to the centrifugal force by telescopically moving relative to the fixed part.

[0022] In one embodiment, the oil baffle further includes:

[0023] A first spring is connected between the fixed part and the telescopic part;

[0024] A second spring is connected between the blocking part and the telescopic part.

[0025] In one embodiment, the oil outlet includes a first circumferential oil outlet and a second axial oil outlet, the first circumferential oil outlet and the second circumferential oil outlet being arranged from the outside to the inside along the radial direction of the bearing, and the size of the first circumferential oil outlet being smaller than the size of the second circumferential oil outlet.

[0026] In one embodiment, the rotor shaft is provided with a main oil passage, which is connected to a branch oil passage arranged radially along the bearing, and the branch oil passage is connected to the oil inlet.

[0027] According to the bearing preload adjustment device of this application embodiment, the pressure mechanism outputs pressure to the outer ring end face of the bearing through the output end, and feeds back the pressure signal detected by the pressure detection mechanism to the pressure mechanism, thereby adjusting the output pressure value of the output end to realize real-time adjustment of the bearing preload, so that the rotor shaft can maintain an appropriate preload, avoiding excessive or insufficient preload of the bearing, thereby ensuring the rigidity, accuracy and speed performance of the bearing, reducing corresponding wear, and extending the service life of the bearing. Attached Figure Description

[0028] Figure 1 This is a schematic diagram of the bearing preload adjustment device according to an embodiment of this application.

[0029] Figure 2 This is a cross-sectional view of a bearing preload adjustment device according to an embodiment of this application.

[0030] Figure 3 This is a schematic diagram showing the structure of the oil baffle in a bearing preload adjustment device according to an embodiment of this application.

[0031] Figure 4 for Figure 3 A magnified view of a portion of point A in the middle.

[0032] Figure 5 This is a schematic diagram showing the structure of the oil hole in a bearing preload adjustment device according to an embodiment of this application.

[0033] Figure 6 This is a schematic diagram showing the structure of the oil baffle in a bearing preload adjustment device according to an embodiment of this application.

[0034] Figure 7 This is a cross-sectional view of the oil baffle plate in a bearing preload adjustment device according to an embodiment of this application.

[0035] Figure 8 This is a schematic diagram of the bearing preload adjustment device in a low-speed condition according to an embodiment of this application.

[0036] Figure 9 This is a schematic diagram of the bearing preload adjustment device under medium speed conditions according to an embodiment of this application.

[0037] Figure 10 This is a schematic diagram of the bearing preload adjustment device in a high-speed condition according to an embodiment of this application.

[0038] Figure label:

[0039] 1. Pressure mechanism;

[0040] 11. Pressure component; 111. Output end; 112. Moving pressure plate; 113. First chamber; 114. Second chamber; 115. Connecting frame; 1151. Sliding plate; 116. Inlet; 117. Sealing ring;

[0041] 12. Drive component; 121. Pressure source; 122. Pressure transmission channel;

[0042] 2. Bearing; 21. Outer ring; 22. Inner ring;

[0043] 3. Pressure testing agency;

[0044] 4. Oil reservoir; 41. Annular groove; 42. Oil inlet; 43. Oil outlet; 431. First circumferential oil hole; 432. Second circumferential oil hole; 44. Oil baffle; 441. Fixing part; 442. Telescopic part; 443. Blocking part; 444. First spring; 445. Second spring;

[0045] 5. Rotor shaft; 51. Main oil passage; 52. Branch oil passage. Detailed Implementation

[0046] To make the above-mentioned objectives, features, and advantages of this application more apparent and understandable, the specific embodiments of this application are described in detail below with reference to the accompanying drawings. Many specific details are set forth in the following description to provide a thorough understanding of this application. However, this application can be implemented in many other ways different from those described herein, and those skilled in the art can make similar modifications without departing from the spirit of this application. Therefore, this application is not limited to the specific embodiments disclosed below.

[0047] In the description of this application, it should be understood that if terms such as "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential" appear, these terms indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0048] Furthermore, where the terms "first" and "second" appear, these terms are for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined with "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this application, where the term "multiple" appears, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0049] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise expressly limited. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0050] In this application, unless otherwise expressly specified and limited, the use of descriptions such as "above" or "below" the second feature indicates that the first and second features are in direct contact or indirect contact via an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. Similarly, "below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0051] It should be noted that if an element is referred to as being "fixed to" or "set on" another element, it can be directly on the other element or there may be an intervening element. If an element is considered to be "connected to" another element, it can be directly connected to the other element or there may be an intervening element. If so, the terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used in this application are for illustrative purposes only and do not represent the only possible implementation.

[0052] See Figure 1 and Figure 2The embodiments of this application propose a bearing 2 preload adjustment device, which includes a pressure mechanism 1 and a pressure detection mechanism 3. The output end 111 of the pressure mechanism 1 is used to abut against the end face of the outer ring 21 of the bearing 2, thereby outputting pressure to the end face of the outer ring 21 of the bearing 2. The pressure detection mechanism 3 is connected to at least one of the pressure mechanism 1 and the bearing 2, and is used to detect the pressure signal of the pressure signal output by the pressure mechanism 1 to the end face of the outer ring 21 of the bearing 2. The pressure mechanism 1 is communicatively connected to the pressure detection mechanism 3, and is used to acquire the pressure signal and adjust the output pressure value of the pressure output to the end face of the outer ring 21 of the bearing 2 according to the pressure signal.

[0053] According to the bearing 2 preload adjustment device of this application embodiment, the pressure mechanism 1 outputs pressure to the end face of the outer ring 21 of the bearing 2 through the output end 111, and feeds back the pressure signal detected by the pressure detection mechanism 3 to the pressure mechanism 1, thereby adjusting the output pressure value of the output end 111 to realize real-time adjustment of the preload of the bearing 2, so that the rotor shaft 5 can maintain an appropriate preload, avoiding the preload of the bearing 2 being too large or too small, thereby ensuring the rigidity, accuracy and speed performance of the bearing 2, reducing the corresponding wear, and extending the service life of the bearing 2.

[0054] See Figure 2 and Figure 3 In some embodiments, the pressure mechanism 1 includes a pressure element 11 and a drive assembly 12. The pressure element 11 has an output portion that forms an output end 111. The drive assembly 12 drives the pressure element 11 and drives the output portion of the pressure element 11 to move axially along the bearing 2.

[0055] In some embodiments, the pressure detection mechanism 3 includes a pressure sensor connected to the pressure element 11. The pressure sensor is capable of acquiring the pressure signal from the pressure element 11. Specifically, the pressure sensor acquires the pressure signal within the pressure element 11 via a circuit and feeds the pressure signal back to the pressure mechanism 1 via another circuit.

[0056] By directly contacting and pressing the pressure component 11 of the pressure mechanism 1 with the end face of the outer ring 21 of the bearing 2, and by receiving feedback from the pressure sensor on the pressure signal of the pressure component 11, the pressure adjustment can achieve real-time control of the preload of the bearing 2. This adapts to the preload requirements of the bearing 2 in different motor speed ranges, thereby ensuring the rigidity, accuracy, and speed performance of the bearing 2, reducing wear, and extending its service life.

[0057] In some embodiments, a movable pressure plate 112 is slidably connected inside the pressure member 11, dividing the interior of the pressure member 11 into a first chamber 113 and a second chamber 114. The drive assembly 12 includes a pressure source 121 and a pressure transmission channel 122 connecting the pressure source 121 to the first chamber 113. A pressure medium is disposed inside the pressure source 121, and the pressure source 121 and the first chamber 113 are interconnected through the pressure transmission channel 122.

[0058] Specifically, in some embodiments, the pressure source 121 is configured as a gas source, the pressure transmission channel 122 is configured as a gas pipe, and the pressure medium is configured as gas. In the pressure mechanism 1, the gas source delivers gas to the first chamber 113 of the pressure component 11 through the gas pipe. The delivered gas generates air pressure, which squeezes the moving pressure plate 112 towards the end face of the bearing 2. The pressure component 11 is squeezed, and its output end 111 is pressed tightly against the end face of the outer ring 21 of the bearing 2, so that the bearing 2 generates a preload. The pressure mechanism 1 controls the gas content in the pressure component 11 according to the pressure signal, so that the pressure in the pressure component 11 reaches the required pressure value, and changes the axial position of the output end 111 of the pressure component 11 in the bearing 2, thereby realizing real-time adjustment of the preload of the bearing 2.

[0059] Furthermore, an inlet 116 is provided on the wall of the first chamber 113 of the pressure component 11, and a sealing ring 117 is provided on the inner wall of the inlet 116. The sealing ring 117 is used to tightly abut against the outer wall of the air pipe to prevent air leakage.

[0060] The pressure component 11 of the pressure mechanism 1 is made to directly contact and press against the end face of the outer ring 21 of the bearing 2. The signal from the pressure sensor is fed back to the air intake device to adjust the pressure inside the pressure component 11 and adjust the preload of the bearing 2 in real time. This allows the rotor shaft 5 to maintain an appropriate preload of the bearing 2, avoiding excessive or insufficient preload of the bearing 2. This ensures the rigidity, accuracy, and speed performance of the bearing 2, reduces wear, and extends the service life of the bearing 2.

[0061] In some embodiments, the bearing 2 preload adjustment device further includes an oil reservoir 4, which is fixedly connected to the rotor shaft 5, and the inner ring 22 of the bearing 2 is mounted on the rotor shaft 5. The oil reservoir 4 and the pressure member 11 are slidably connected along the axial direction of the bearing 2. Specifically, the end face of the inner ring 22 of the oil reservoir 4 is interference-fitted with the rotor shaft 5.

[0062] See Figure 3 and Figure 4 In some embodiments, the pressure member 11 is fixedly connected to the connecting frame 115, the oil storage chamber 4 is provided with an annular groove 41, the annular groove 41 is arranged along the circumference of the bearing 2, and the connecting frame 115 is slidably connected to the annular groove 41 along the axial direction of the bearing 2.

[0063] Specifically, the connecting frame 115 can be integrally formed with the pressure component 11. The connecting frame 115 is provided with a T-shaped sliding plate 1151 extending towards the oil reservoir 4. The sliding plate 1151 can rotate circumferentially along the bearing 2 in the annular groove, or slide axially along the bearing 2 in the annular groove.

[0064] The pressure component 11 and the oil reservoir 4 are interconnected with the connecting frame 115 via an annular groove 41. This connection ensures that the oil reservoir 4 does not rotate with the rotor shaft 5, maintaining the stability of the preload control. The width of the annular groove 41 needs to be slightly larger than the mating width of the connecting frame 115. When the device is installed on the rotor shaft 5 to compress the bearing 2, the connecting frame 115 must be close to the non-oil-spraying side of the annular groove 41. This ensures that the preload compression of the bearing 2 outer ring 21 by the pressure component 11 is not affected by the connecting frame 115. The connecting frame 115 and the pressure component 11 are integral parts. The air inlet of the pressure component 11 is sealed by a sealing ring 117 to prevent gas leakage. The oil baffle 44 is installed close to the oil reservoir 4, with the shielding part 443 facing the oil outlet 43 of the oil reservoir 4. Simultaneously, the fixing part 441 has the same interference fit with the rotor shaft 5 as the oil reservoir 4, rotating with the shaft.

[0065] By designing the connecting frame 115, the pre-tightening and cooling bearing 2 of the device are integrated, while the pressure mechanism 1 and the oil injection mechanism move in layers. The oil injection mechanism moves with the rotor shaft 5 through interference fit, while the pressure mechanism 1 does not move with the rotor shaft 5, thereby avoiding the influence of the rotor shaft 5 movement on the air pressure pre-tightening force.

[0066] See Figure 2 and Figure 3 In some embodiments, the oil reservoir 4 includes an oil inlet 42 and an oil outlet 43. The oil inlet 42 is used to supply cooling oil to the oil reservoir 4. The oil outlet 43 is connected to the gap between the inner ring 22 and the outer ring 21 of the bearing 2, and is used to supply cooling oil to the gap between the inner ring 22 and the outer ring 21 of the bearing 2.

[0067] See Figure 2 and Figure 5 In some embodiments, multiple oil outlet holes 43 are provided on the oil storage chamber 4 along the radial direction of the bearing 2. The oil storage chamber 4 is provided with an oil baffle plate 44, which includes a fixed part 441, a telescopic part 442, and a blocking part 443. The fixed part 441 and the blocking part 443 are connected to both ends of the telescopic part 442 along the radial direction of the bearing 2. When the oil storage chamber 4 rotates with the rotor shaft 5, centrifugal force is generated, and the blocking part 443 responds to the centrifugal force by telescopically moving relative to the fixed part 441.

[0068] See Figure 6Specifically, the fixing part 441 is fixed with the rotor shaft 5 by an interference fit and rotates synchronously with the rotor shaft 5. The telescopic part 442 can elastically extend and retract. Under different speed conditions, it can extend or shorten in the circumferential direction of the bearing 2 under the action of centrifugal force, so that the blocking part 443 blocks the oil outlet 43 on the oil storage chamber 4 to different degrees. At the same time, due to the elastic effect, it can return to the initial position when the motor finally stops rotating.

[0069] With the above configuration, the oil outlet 43 of the oil storage chamber 4 is combined with the oil baffle 44 to form an oil injection mechanism. The oil baffle 44 is designed as an elastic telescopic structure, which can achieve various degrees of telescopic extension and contraction due to centrifugal force in different speed ranges. This allows for various combinations of oil hole blocking in different speed ranges, achieving different cooling effects for the bearing 2.

[0070] See Figure 7 In some embodiments, the oil baffle 44 further includes a first spring 444 and a second spring 445, the first spring 444 being connected between the fixed part 441 and the telescopic part 442, and the second spring 445 being connected between the blocking part 443 and the telescopic part 442.

[0071] Specifically, the elastic expansion and contraction effect of the oil baffle 44 is achieved through the structure of the first spring 444 and the second spring 445. The fixed part 441 of the oil baffle 44 is fixedly connected to one side of the first spring 444, the inner end of the telescopic part 442 is fixedly connected to the other side of the first spring 444, the outer end of the telescopic part 442 is fixedly connected to one side of the second spring 445, and the blocking part 443 is fixedly connected to the other side of the second spring 445. The elastic expansion and contraction effect of the oil baffle 44 is achieved through the elastic connection of the fixed part 441, the telescopic part 442, and the blocking part 443 of the oil baffle 44 by the first spring 444 and the second spring 445. It is understood that the telescopic part 442 can be appropriately provided with a slotted structure to prevent it from blocking the oil outlet 43.

[0072] See Figure 5 In some embodiments, the oil outlet 43 includes a first circumferential oil outlet 431 and a second axial oil outlet. The first circumferential oil outlet 431 and the second circumferential oil outlet 432 are arranged radially from the outside to the inside of the bearing 2, and the size of the first circumferential oil outlet 431 is smaller than the size of the second circumferential oil outlet 432. The first circumferential oil outlet 431 is located on the outside of the oil reservoir 4, and the second circumferential oil outlet 432 is located on the inside of the oil reservoir 4. In some embodiments, in a set of oil outlets 43, there are four first circumferential oil outlets 431 and four second circumferential oil outlets 432, and their positions are evenly distributed inside and outside. The diameter, number, and positional distribution of this part of the oil outlet 43 are not fixed and can be determined in conjunction with the design of the oil baffle 44 and according to the specific actual situation.

[0073] By designing the diameter of the oil outlet 43 of the oil storage chamber 4 in a gradient from large to small from the inside to the outside, combined with the effect of the oil baffle 44 extending outward under the action of centrifugal force, the flow rate of the cooling oil in the bearing 2 can be matched at different speeds of the rotor shaft 5. For example, as the speed of the rotor shaft 5 gradually increases, the diameter of the oil holes blocked by the oil baffle 44 becomes smaller and the number decreases, and the flow rate of the cooling oil gradually increases.

[0074] By employing a flexible and retractable oil baffle 44 combined with different oil injection hole designs (diameter, number, and position), different oil injection effects are achieved under the action of centrifugal force, thereby matching the required flow rate of cooling oil for bearings 2 in different speed ranges (high speed, medium speed, and low speed).

[0075] Specifically, in some embodiments, the design of the oil baffle 44 and the oil outlet 43 has the following effects at different speeds:

[0076] See Figure 8 At low speed, the centrifugal force is small, the telescopic part 442 of the oil baffle 44 does not extend outward, the blocking part 443 completely blocks the second circumferential oil hole 432, and the oil storage chamber 4 cools the bearing 2 through the first circumferential oil hole 431. At this time, the flow rate is small.

[0077] See Figure 9 At medium speed, the centrifugal force is moderate. The telescopic part 442 of the oil baffle 44 extends outward, and the blocking part 443 completely blocks the first circumferential oil hole 431. The oil storage chamber 4 cools the bearing 2 through the second circumferential oil hole 432. Since the diameter of the second circumferential oil hole 432 is larger than that of the first circumferential oil hole 431, the flow rate is increased compared with the low speed condition. At this time, the flow rate is moderate.

[0078] See Figure 10 At high speeds, the centrifugal force is large, and the telescopic part 442 of the oil baffle plate 44 extends outward to the end face of the inner ring 22 of the pressure member 11. The shielding part 443 does not shield the first circumferential oil hole 431 and the second circumferential oil hole 432. The oil storage chamber 4 cools the bearing 2 through the first circumferential oil hole 431 and the second circumferential oil hole 432. At this time, the flow rate is the maximum.

[0079] See Figure 2 In some embodiments, the rotor shaft 5 is provided with a main oil passage 51, which is connected to a branch oil passage 52 arranged radially along the bearing 2. The branch oil passage 52 is connected to the oil inlet 42. In order to reduce the internal space occupancy of the motor, the main oil passage 51 of the cooling oil circuit is built inside the rotor shaft 5, so that the cooling oil is delivered to the oil injection mechanism during the rotation of the motor, thereby realizing internal oil circulation.

[0080] With the above configuration, the oil storage chamber 4 has an oil inlet, and the rotor shaft 5 has an oil distribution channel 52, so that the oil inlet hole 42 and the oil distribution channel 52 are aligned and installed. The main oil channel 51 inside the rotor shaft 5 is used to cool the bearing 2. The cooling oil flows into the oil storage chamber 4 through the oil distribution channel 52 and the oil inlet hole 42, and finally acts on the bearing 2 through the first circumferential oil hole 431 and the second circumferential oil hole 432 on the side end face of the oil storage chamber 4 near the bearing 2 for cooling.

[0081] The bearing 2 preload adjustment device of this application can be applied to the preload load control of rotor bearing 2. Addressing the current problem of poor cooling in rotor bearing 2, it integrates oil spray cooling, enabling simultaneous preload load control and cooling of bearing 2. Preload load control is achieved by adjusting the pressure mechanism 1 to cause the pressure element 11 to press against the outer ring 21 of bearing 2. Oil spray cooling is achieved through the design of the oil outlet 43, combined with the change in the position of the oil baffle 44 at different speeds to achieve different oil flow rates, matching the cooling requirements of bearing 2 at different motor speed ranges. This allows for heat dissipation of bearing 2 when the rotor shaft 5 rotates and generates heat at different speeds, preventing premature bearing 2 failure due to friction and heat, and extending the service life of bearing 2.

[0082] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0083] The embodiments described above are merely illustrative of several implementation methods of this application, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the patent application. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of this application, and these all fall within the protection scope of this application. Therefore, the protection scope of this patent application should be determined by the appended claims.

Claims

1. A bearing preload adjustment device, characterized in that, include: A pressure mechanism, the output end of which is used to abut against the outer ring end face of a bearing, thereby outputting pressure to the outer ring end face of the bearing; the pressure mechanism includes a pressure element, the pressure element having an output portion, the output portion being used to form the output end. A pressure detection mechanism, which is connected to at least one of the pressure mechanism and the bearing, is used to detect a pressure signal that the pressure mechanism outputs pressure to the outer ring end face of the bearing. The pressure mechanism is communicatively connected to the pressure detection mechanism to acquire the pressure signal and adjust the output pressure value of the pressure output to the outer ring end face of the bearing according to the pressure signal. An oil reservoir is provided, which is fixedly connected to the rotor shaft, and the inner ring of the bearing is mounted on the rotor shaft. The oil reservoir and the pressure component are slidably connected along the axial direction of the bearing. The oil reservoir includes an oil outlet hole, which is connected to the gap between the inner and outer rings of the bearing, for supplying cooling oil to the gap between the inner and outer rings of the bearing. Multiple oil outlet holes are provided on the oil reservoir along the radial direction of the bearing. The oil reservoir is provided with an oil baffle plate, which includes a fixed part, a telescopic part, and a blocking part. The fixed part and the blocking part are telescopically connected to both ends of the telescopic part along the radial direction of the bearing. When the oil reservoir rotates with the rotor shaft, it generates centrifugal force, and the blocking part responds to the centrifugal force by telescopically moving relative to the fixed part. The oil outlet of the oil reservoir is combined with the oil baffle to form an oil spraying mechanism. The oil baffle is designed as an elastic telescopic structure, which can expand and contract to various degrees due to centrifugal force within different speed ranges. This allows for various combinations of oil hole blocking at different speed ranges, achieving different bearing cooling effects.

2. The bearing preload adjustment device according to claim 1, characterized in that, The pressure mechanism also includes: A drive assembly, which is connected to the pressure element, is used to drive the output part of the pressure element to move axially along the bearing.

3. The bearing preload adjustment device according to claim 2, characterized in that, The pressure component is internally slidably connected to a movable pressure plate, which divides the interior of the pressure component into a first chamber and a second chamber. The drive assembly includes a pressure source and a pressure transmission channel connecting the pressure source to the first chamber. The pressure source contains a pressure medium, and the pressure source and the first chamber communicate with each other through the pressure transmission channel.

4. The bearing preload adjustment device according to claim 1, characterized in that, The fixing part is fixed to the rotor shaft with an interference fit and rotates synchronously with the rotor shaft. The telescopic part can elastically expand and contract.

5. The bearing preload adjustment device according to claim 1, characterized in that, The pressure component is fixedly connected to a connecting frame, and the oil storage chamber is provided with an annular groove. The annular groove is arranged along the circumference of the bearing, and the connecting frame is slidably connected to the annular groove along the axial direction of the bearing.

6. The bearing preload adjustment device according to claim 1, characterized in that, The oil storage chamber includes: An oil inlet is provided for supplying cooling oil to the oil reservoir.

7. The bearing preload adjustment device according to claim 6, characterized in that, The oil baffle also includes: A first spring is connected between the fixed part and the telescopic part.

8. The bearing preload adjustment device according to claim 7, characterized in that, The oil baffle also includes: A second spring is connected between the blocking part and the telescopic part.

9. The bearing preload adjustment device according to claim 7, characterized in that, The oil outlet includes a first circumferential oil outlet and a second circumferential oil outlet. The first circumferential oil outlet and the second circumferential oil outlet are arranged from the outside to the inside along the radial direction of the bearing. The size of the first circumferential oil outlet is smaller than the size of the second circumferential oil outlet.

10. The bearing preload adjustment device according to claim 6, characterized in that, The rotor shaft is provided with a main oil passage, which is connected to a branch oil passage arranged radially along the bearing, and the branch oil passage is connected to the oil inlet hole.

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